CN110494712B - Air cooling type industrial steam condensing device of microtube - Google Patents
Air cooling type industrial steam condensing device of microtube Download PDFInfo
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- CN110494712B CN110494712B CN201780051189.9A CN201780051189A CN110494712B CN 110494712 B CN110494712 B CN 110494712B CN 201780051189 A CN201780051189 A CN 201780051189A CN 110494712 B CN110494712 B CN 110494712B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
- F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
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Abstract
A large field erected air cooled industrial steam condensing unit, each unit having 10 heat exchanger tube bundles arranged in five pairs in a V-shape, each heat exchanger tube bundle having four primary heat exchangers and four secondary heat exchangers, wherein each secondary heat exchanger is paired with a single primary heat exchanger. The four primary condensing units are arranged with the tubes horizontal and the inlet steam manifold at one end of the tubes is perpendicular to the primary condensing unit tubes, i.e. parallel to the transverse axis of the tube bundle. Steam enters a small inlet steam manifold from below. The tube has a cross-sectional dimension of 200mm width, a cross-sectional height of less than 10mm, a fin height of 10mm, and is arranged with 9 to 12 fins per inch.
Description
Technical Field
The invention relates to an air-cooled industrial steam condensing device erected on a large-scale site.
Background
The finned tubes currently used in most large field-mounted air-cooled industrial steam condensing units ("ACC") are flat tubes with a length of about 11m, a width (also referred to as the "air stroke length") of 200mm, semicircular leading and trailing edges, and an external height (perpendicular to the air stroke length) of 18.7 mm. The thickness of the tube wall is 1.35 mm. Fins are brazed to both flat sides of each tube. The fin height is typically 18.5mm with 11 fins per inch. The fin surfaces are in a wave pattern to enhance heat transfer and to aid in the stiffness of the fins. The standard spacing between tubes, center to center, was 57.2 mm. The tube itself constitutes about one third of the cross-sectional area (perpendicular to the air flow direction); while the fins constitute approximately two-thirds of the cross-sectional area. There was a small gap of 1.5mm between adjacent fin tips. For summer ambient conditions, the maximum steam velocity through the tubes can typically be as high as 28mps, more typically 23 to 25 mps. The individual a-frames formed by these tube and fin combination designs have been optimized based on tube length, fin spacing, fin height and shape, and air stroke length. The finned tubes are assembled to form heat exchanger tube bundles, typically 39 tubes per heat exchanger tube bundle, and 10-14 tube bundles are arranged in two tube bundles, each fan having a single a-frame collectively formed by the two tube bundles. A fan is typically located below the a-frame for forcing air through the tube bundle. The overall design of the tubes and fins and the combined air pressure drop of the tubes and fins are also optimized to match the air transfer capacity of large (36 foot diameter) fans operating at 200 to 250 horsepower. Since the introduction of the concept of a single row of oval tubes over 20 years ago, this optimized arrangement has remained relatively unchanged in many different manufacturers to date.
The typical a-frame ACC described above includes a first stage or "primary" condensing plant tube bundle and a second stage or "secondary" tube bundle. About 80% to 90% of the heat exchanger tube bundles belong to the first stage or primary condensing unit tube bundle (bundle). The steam enters the top of the primary condensing unit tube bundle, while the condensate and some of the steam exits the bottom. The first stage configuration is thermally efficient; however, it does not provide a method for removing non-condensable gases. To sweep the non-condensable gases through the first stage tube bundle, 10% to 20% of the heat exchanger tube bundles are configured as a second stage or secondary condensing device, typically interspersed in the primary condensing device, for drawing steam from the lower condensate manifold. In this arrangement, as the steam and non-condensable gases are drawn into the bottom of the secondary condensing device, the steam and non-condensable gases pass through the primary condensing device. As the gas mixture travels upward through the secondary condensing device, the remaining steam condensate, condenses into non-condensable gases. The top of the secondary condensing device is connected to a vacuum manifold for removing non-condensable gases in the system.
Variants on standard prior art ACC devices have been disclosed, for example in documents US2015/0204611 and US 2015/0330709. These applications show identical but substantially shortened finned tubes which are then arranged into a series of small a-frames, typically 5 a-frames for each fan. Part of the logic is to reduce the steam pressure drop, which has little effect on the total capacity in summer conditions, but more for winter conditions. It is also logical to weld the overhead steam manifold piping to each tube bundle at the factory and transport them together, thus saving expensive field welding work. The net effect of this arrangement of connecting the steam manifolds at the factory and transporting them with the tube bundle is to reduce the length of the tubes in order to accommodate the manifolds in a standard height cubic shipping container. The total amount of surface area is reduced due to the shortened tubes, which is about 3% reduction in relative capacity for a standard single a-frame design of similar overall dimensions under summer conditions.
Disclosure of Invention
The invention proposed herein is: 1) novel tube designs for heat exchanger systems, including but not limited to large field-erected air-cooled industrial steam condensing units; and 2) new design of air cooled industrial steam condensing units for large field installations of power plants and the like; both are capable of reducing the materials used in certain configurations while significantly increasing the thermal capacity of the ACC. Various aspects and/or embodiments of the invention are described below:
according to a preferred embodiment of the tube design invention, the cross-sectional dimension of the tube is 200mm wide (air stroke length), similar to the prior art, but the cross-sectional height (perpendicular to the air stroke length) is less than 10mm, preferably 4-10mm, more preferably 5.0-9mm, even more preferably 5.2-7mm, most preferably 6.0mm, (also the outer tube width), and the height of the fins is 8-12mm, the height of the fins is more preferably 10mm, 8 to 12 fins, preferably 11 fins, are arranged per inch. According to another preferred embodiment, the actual fins may be 16-22mm, preferably 18.5mm in height, and span the space between two adjacent tubes, effectively allowing 8-11mm fins to be used for each tube on each side.
The current view prevailing in the art is that tubes with as large a cross section as possible should be manufactured to accommodate the large quantities of steam output by large power plants, and just as the cost is reduced due to the larger tubes, the manufacture of tubes with smaller cross sections (same air stroke length but significantly smaller height) is directly contrary to the current view prevailing in the art. Although the cost of this arrangement is significantly higher than the prior art tube arrangement, the inventors have surprisingly found that the increase in efficiency of the lower height tube (in the most preferred embodiment, the efficiency is increased by more than 30% compared to the prior art tube) exceeds the offset cost increase compared to the prior art tube. This novel tube design can be used in large field-mounted air-cooled industrial steam condensing units of the prior art (e.g., as described in the background section), or it can be used in conjunction with the new ACC design described below.
For large field-erected air-cooled industrial steam condensing unit new designs, one of the main features of the present invention is to arrange multiple primary and secondary condensing units in the new design to reduce the cost of the steam manifold while significantly increasing the heat capacity to allow easy container shipping and minimal field welding.
According to one embodiment of the invention, the design is characterized in that the 10 heat exchanger tube bundles of each unit are arranged in five pairs of "V's" (inverted configuration compared to standard prior art ACC devices). According to alternative embodiments, the tube bundles may be arranged in an a-frame arrangement, but such embodiments require additional piping and therefore increase costs.
In a preferred arrangement, each heat exchanger tube bundle has four primary heat exchangers and four secondary heat exchangers, with each secondary heat exchanger paired with a single primary heat exchanger. According to an alternative embodiment, only one secondary heat exchanger is provided per heat exchanger core; however, matching each secondary heat exchanger with a single primary heat exchanger has the advantage of minimizing condensing unit piping/headers. According to further alternative embodiments, three or even two or five or more heat exchangers may be provided per heat exchanger core, with subsequent capacity and cost tradeoffs.
According to a preferred embodiment, the four primary condensing units are arranged such that the tubes are horizontal, while the inlet steam manifold at one end of the tubes is aligned parallel to the transverse axis of the tube bundle. This arrangement allows steam to enter the small inlet steam manifold from below. According to an alternative embodiment, the steam may be introduced from above, but this embodiment requires more piping.
According to a preferred embodiment, each tube bundle has a vertical width of 91 inches (2.3m) to 101 inches (2.57 m).
The preferred tube bundle length is 41 feet to 43 feet, but various other shorter lengths may be provided, including 38 feet. According to one embodiment, two small secondary condensing units can be attached to the primary condensing unit on site, resulting in very low additional on-site welding costs. This embodiment is particularly useful in cases where the core length required is longer than the shipping container length.
According to a preferred embodiment, each horizontal tube bundle length has a tube length of 2.2m to 2.8m for a tube bundle having four primary condensation devices. For a tube bundle with five primary condensing units per tube bundle, each horizontal tube bundle length has a tube length of 1.75 to 2.25m, and preferably 2.0 m. The steam manifold and the outlet manifold have a preferred width (perpendicular to the vertical length of the manifold) of 0.065m to 0.10m, preferably 0.075 m. Each primary condensing unit is preferably directly connected to a secondary condensing unit having finned tubes with longitudinal axes aligned parallel to the transverse axis of the tube bundle, configured to receive steam from the bottom, and preferably dimensioned to have a surface area of 10% to 20% of the surface area of its respective primary condensing unit, and for example 0.20m to 0.45m wide, preferably 0.31m wide, in the case of primary condensing units of size 2.3m x 2.4 m.
According to a preferred embodiment, the heat exchanger tube bundle consists, from one end to the other, of: a small secondary condensing device (10-20% of the surface area of the corresponding primary coil) with tubes aligned parallel to the transverse axis of the tube bundle, followed by a full-size primary condensing device with horizontal tubes (aligned parallel to the longitudinal axis of the tube bundle) with a condensate header between the primary and secondary condensing device connected along its sides to the outlets of the primary condensing device tubes and at its bottom to the inlets of the secondary condensing device for delivering the remaining steam and non-condensable gases directly into the secondary condensing device. A vapor inlet manifold is located distal to the first primary condensing unit. The second primary and secondary condensing units are mirrored from the first condensing unit to complete the first half of the heat exchanger tube bundle. The rear half of the heat exchanger is mirrored from the front half.
The tube bundles are then mated, preferably in a V-frame. This brings two sets of four steam inlets to two separate small areas. These four inlets can be connected to a single steam standpipe from the underlying large steam line and connected together by a one-to-four adapter, eliminating the need to weld the steam manifold over the length of the tube bundle. As noted above, an a-frame may be used, but is less cost effective because the conventional a-frame ACC configuration requires that the steam pipes be placed above the coil/bundle rather than below.
The steam is conveyed to the heat exchanger tube bundle through a steam pipe. The riser pipe conveys steam from the steam conduit to the heat exchanger inlet and then to the steam inlet manifold. The steam inlet manifold delivers steam to the horizontal guide tubes of the primary condensing unit. As the vapor traverses the tubes of the primary condensing device, most of the vapor condenses into liquid water. The tubes of the primary condensing unit terminate in a condensate header that receives the condensate and the remaining steam (including non-condensable gases). The bottom of the condensate header has a "foot" portion that extends from and opens into the bottom of the secondary condensing unit. Condensate collects at the bottom of the condensate header where it is transported to the condensate collection pipe. Simultaneously, the remaining steam, including non-condensable gases, is drawn upwardly from the condensate header by the secondary condensing means. As the remaining steam condenses, the condensate flows back down the bottom of the condensate header through the secondary condensing device and into the condensate collection pipe. The non-condensable gases leave the secondary condensing unit through a non-condensable collecting pipe.
As discussed, this new ACC design can be used with tubes having the cross-sectional configuration and area of the prior art (200mm x 18.7mm), in which case the increase in efficiency is about 5%. Alternatively, this new ACC design may be used with tubes having the new design described herein (200mm x less than 10mm), with an efficiency improvement of about 22% over prior art a-frames having standard tube construction.
According to another alternative embodiment, the new ACC design of the present invention may be used with 100mm x 5mm to 100mm x 7mm tubes with offset fins. This example produced a 17.5% increase in total capacity, about a 40% reduction in tube and fin cost, while reducing the support tube bundle weight compared to a standard ACC configuration with standard tubes. The weight of the tube bundle according to this embodiment will also be about 60% of the prior art tube bundle and therefore more easily supported within the new ACC structure.
According to another embodiment, the new ACC design of the present invention may be used with 200mm x 5mm to 200mm x 7mm tubes having "arrow" type fins with 9.8 fins per inch. This embodiment yields a total capacity increase of over 30% compared to a standard ACC configuration with standard tubing.
According to another embodiment, the new ACC design of the present invention may be used with 120mm x 5mm to 120mm x 7mm tubes having "arrow" type fins with 9.8 fins per inch. This embodiment yields a total capacity increase of over 17% compared to a standard ACC configuration with standard tubing. According to another embodiment, the new ACC design of the present invention may be used with 140mm x 5mm to 140mm x 7mm tubes having "arrow" type fins with 9.8 fins per inch. This embodiment yields a total capacity increase of over 23% compared to a standard ACC configuration with standard tubing. Although the capacity increase for the 120mm and 140mm configurations is not as great as for the 200mm configuration, the 120mm and 140mm configurations reduce material and weight compared to the 200mm design.
For the disclosure of the arrow-type fin structure discussed above, the disclosure of U.S. application No.15/425,454 filed on 6.2.2017 is incorporated herein in its entirety.
According to yet another embodiment, the new ACC design of the present invention may be used with tubes having "louvered" fins, which have approximately the same performance as offset fins, and which are easier to acquire and manufacture.
With the prior art, the heat exchanger fins and tubes are brazed together, one tube at a time. According to the present invention, with these smaller tube bundles and smaller tubes, it is possible to braze multiple finned tubes into a single assembly, thereby reducing manufacturing costs, eliminating air gaps between finned tubes that affect performance, and providing a robust structure between adjacent tube walls to prevent them from collapsing under vacuum. Furthermore, for the fins and tubes with the arrangement of the invention, a significant surface area is obtained, in particular because the total area for heat transfer is limited by the size of the transport container door. This arrangement provides a more efficient heat exchange area per transport vessel size unit than any other design, since the tube length or tube bundle width is not reduced by the steam manifolds required by the other design.
In summary, the overall gain in vapor condensation capacity and cost reduction of the present invention is up to 33% compared to equivalent size devices of the prior art, with a constant fan power per fan. For a multi-unit ACC, the number of fans can be reduced, since each unit has a higher capacity and less units are needed to perform the steam condensation work, the total fan power can be reduced by more than 25%.
In addition, the ACC design of the present invention may be easier to set up, requiring less overall space within the power plant.
There is thus provided, in accordance with an embodiment of the present invention, a large field-mounted air-cooled industrial steam condensing unit for connection to an industrial steam production facility, including: a plurality of pairs of heat exchanger tube bundles, each pair of heat exchanger tube bundles arranged in a V-shaped configuration and each heat exchanger tube bundle having a longitudinal axis and a transverse axis perpendicular to the longitudinal axis, each heat exchanger tube bundle comprising a plurality of steam inlet manifolds, a plurality of primary condensing device portions, a plurality of outlet condensate headers, and at least one secondary condensing device portion; each primary condensing unit comprises a plurality of finned tubes, the longitudinal axis of each finned tube being parallel to the longitudinal axis of the corresponding heat exchanger tube bundle; each secondary condensing unit comprises a plurality of finned tubes, the longitudinal axis of each finned tube being parallel to the transverse axis of the respective heat exchanger; a longitudinal axis of each of the steam inlet manifolds is parallel to a transverse axis of the respective heat exchanger, each steam inlet manifold is configured to receive steam from a steam distribution manifold located below the heat exchange tube bundle and distribute the steam to first ends of the plurality of finned tubes in the respective primary condensing unit; a longitudinal axis of each of the outlet condensate headers is parallel to a transverse axis of the respective heat exchanger and is connected on a first side to the second ends of the plurality of finned tubes of the respective primary condensing device for collecting condensate, uncondensed steam and uncondensable gases therefrom, each of the outlet condensate headers being connected at a bottom end to a bottom end of the at least one secondary condensing device portion, each of the outlet condensate headers also being connected at a bottom end to a condensate collecting pipe and each of the secondary condenser portions being connected at a top end to an uncondensable collecting pipe.
There is also provided in accordance with an embodiment of the present invention a large field erected air cooled industrial steam condensing unit including an equal number of primary condensing units and secondary condensing units, each paired with a single primary condensing unit.
There is also provided in accordance with an embodiment of the present invention a large field erected air cooled industrial steam condensing unit wherein each heat exchanger tube bundle includes four primary condensing units and four secondary condensing units, wherein each primary condensing unit/secondary condensing unit pair is oppositely directed from left to right with respect to adjacent primary condensing unit/secondary condensing unit pairs such that a first pair of the steam inlet manifolds in a heat exchanger tube bundle are directly adjacent to each other and a second pair of the steam inlet manifolds in the same heat exchanger tube bundle are directly adjacent to each other.
There is also provided in accordance with an embodiment of the present invention a large field erected air cooled industrial steam condensing unit wherein the bottom end of the steam inlet manifold of a first heat exchanger tube bank is adjacent to the bottom end of the steam inlet manifold of a second heat exchanger tube bank in a pair of heat exchanger tube banks.
There is also provided in accordance with an embodiment of the present invention a large field erected air cooled industrial steam condensing unit wherein the bottom ends of the two adjacent steam inlet manifolds of a first heat exchange tube bank and the bottom ends of the two adjacent steam inlet manifolds of a second heat exchange tube bank of a pair of heat exchange tube banks are connected to a first end of a quad type steam manifold adapter and wherein the second end of the quad type steam manifold adapter is connected to a steam supply manifold.
There is also provided in accordance with an embodiment of the present invention a large field erected air cooled industrial steam condensing unit wherein the plurality of finned tubes in the primary condensing unit are 2.0 to 2.8m in length, 200mm in cross sectional width and 4-10mm in cross sectional height.
There is also provided in accordance with an embodiment of the present invention a large field erected air cooled industrial steam condensing unit wherein the cross sectional height of the tubes in the primary condensing unit is 5.2-7 mm.
There is also provided, in accordance with an embodiment of the present invention, a large field erected air cooled industrial steam condensing unit wherein the cross sectional height of the tubes in the primary condensing unit is 5.9 mm.
There is also provided in accordance with an embodiment of the present invention a large field erected air cooled industrial steam condensing unit wherein the plurality of finned tubes in the primary condensing unit have fins attached to the flat sides of the tubes, the fins having a height of 10mm with 9 to 12 fins disposed at intervals per inch.
There is also provided in accordance with an embodiment of the present invention a large field erected air cooled industrial steam condensing unit wherein the plurality of finned tubes in the primary condensing unit have fins attached to the flat sides of the tubes, the fins having a height of 18mm to 20mm, spanning the space between and contacting adjacent tubes, with 9 to 12 fins per inch spacing.
There is also provided, in accordance with an embodiment of the present invention, a large field-erected air-cooled industrial steam condensing unit, wherein the surface area of all secondary condensing units in a heat exchange tube bundle is 10-20% of the surface area of all primary condensing units in the same heat exchange tube bundle.
There is also provided in accordance with an embodiment of the present invention a large field erected air cooled industrial steam condensing unit wherein two primary/secondary condensing unit pairs are adjacent to each other and the secondary condensing units of the two pairs are adjacent to each other, the two secondary condensing units being combined into a single secondary condensing unit.
Drawings
FIG. 1A is a perspective view of the heat exchange portion of a large field erected air cooled industrial steam condensing unit of the prior art;
FIG. 1B is a partially exploded close-up view of the heat exchange portion of a large field erected air cooled industrial steam condensing unit of the prior art, showing the orientation of the tubes relative to the steam distribution manifold;
FIG. 2A is a perspective view of the heat exchange portion of a large field-mounted air-cooled industrial steam condensing unit ("ACC") according to a first embodiment of the present invention;
FIG. 2B is a partially exploded close-up view of the apparatus shown in FIG. 2A, showing the orientation of the tubes in the primary condensing unit;
FIG. 3 is a side view of the heat exchange portion of the ACC according to a preferred embodiment of the present invention;
FIG. 4 is a close-up side view of the connection between the steam risers and the corresponding steam headers at the bottom of the heat exchange portion of the ACC, according to one embodiment of the invention;
FIG. 5 is an end view of a steam riser/transition element/steam manifold assembly for an ACC according to an embodiment of the present invention;
FIG. 6 is a cross-sectional perspective view of a prior art ACC tube and fin;
figure 7 is a perspective view of a first embodiment of a microtube and fin according to the invention;
FIG. 8 is a side view of a large field erected air cooled industrial steam condensing unit according to one embodiment of the present invention with a V-shaped heat exchange tube bundle pair having a primary condensing unit and a secondary condensing unit arrangement as shown in FIG. 2A;
FIG. 9 is an end view of the large field erected air cooled industrial steam condensing unit shown in FIG. 8;
FIG. 10 is a top plan view of the large field erected air cooled industrial steam condensing unit shown in FIG. 8;
FIG. 11 is a perspective view of a primary condensing unit finned tube bundle in accordance with an embodiment of the present invention;
fig. 12 is a photograph of a perspective view of the primary condensing unit finned tube bundle presented in fig. 11.
Detailed Description
V-shaped ACC with horizontal primary condensing device and vertical secondary condensing device
Referring to fig. 2A, 2B and 3, a bundle pair 2 may be constructed by connecting two bundles 4 in a V configuration. Each tube bundle 4 is made up of four primary condensing units 6 and four secondary condensing units 8, each secondary condensing unit 8 being paired with a single primary condensing unit 6. The tubes 10 in the primary condensing unit 6 are arranged with the tubes 10 horizontal, while the inlet steam manifold 12 at one end of the tubes is aligned parallel to the transverse axis of the tube bundle. This arrangement allows steam to enter the small inlet steam manifold 12 from below. The tubes 14 in the secondary condensing device 8 are also aligned parallel to the transverse axis of the tube bundle. The preferred vertical height of each tube bundle is 91 inches (2.3 meters) to 101 inches (2.57 meters), with a preferred tube bundle length of 38 feet to 45 feet.
According to a preferred embodiment, each primary condensation unit 6 occupies 2.6m of the length, measured along the length of the tube bundle; each steam manifold 12 and condensate outlet header 16 occupies 0.3 meter in length, and each secondary tube bundle 8 occupies 0.4 meter in length. In any event, each secondary tube bundle 8 will occupy 10% to 20% of the finned tube surface area of the entire heat exchanger tube bundle.
With continued reference to fig. 2A and 3, a preferred heat exchanger tube bundle according to the present invention is comprised of, from one end to the other: a secondary condensing unit 8 having tubes 14 with the longitudinal axes of the tubes 14 oriented parallel to the transverse axis of the tube bundle, followed by an outlet condensate header 16 (about 3 inches) adjacent the secondary condensing unit 8 and communicating steam from the primary condensing unit 6 directly into the secondary condensing unit 8, followed by a full-scale primary condensing unit 6 having horizontal tubes 10.
According to a preferred embodiment, each condensate header 16 has a foot 28 at its bottom, which foot 28 extends below and opens into its respective secondary condensation device 8. A steam inlet manifold 12 (about 0.20 to 0.25m per side) is located at the distal end of the first primary condensing unit 6. The second set of primary and secondary condensing means is obtained from the mirror image of the first set, thus completing the first half of the heat exchanger. The rear half of the heat exchanger is mirrored from the front half. Adjacent secondary condensing devices as shown in the center of fig. 2A and 3 may be combined into a single secondary condensing device. The condensate collected at the bottom of the condensate header 16 flows into the condensate collection pipe 30. Non-condensable gases are drawn from the top of the secondary condensation device 8 into the non-condensable collecting tubes 32.
The tube bundles are then paired together, preferably in a V-frame. As shown in fig. 2A and 3, this arrangement brings two sets of four steam inlets 18 to two single small areas. These four inlets may be connected to a single steam riser 20 and connected together by a one-to-four adapter 24, wherein the single steam riser 20 originates from a large steam pipe 22, see fig. 4 and 5. There is no need to weld the steam manifold over the length of the tube bundle. An a-frame may be used, but is less cost effective.
Fig. 8-10 illustrate a representative large field-erected air-cooled industrial steam condensing unit having a V-shaped pair of heat exchange tube bundles with a primary condensing unit and a secondary condensing unit arrangement as shown in fig. 2A, according to one embodiment of the invention. The plant shown in fig. 8-10 is a 36 unit (6 units by 6 units) ACC with the most preferred embodiment having five tube bundle pairs or "streets" per unit, but the present invention can be used with ACCs of any size and with any number of tube bundle pairs or streets per unit.
The above-described embodiments of the present invention have increased heat capacity by 13% compared to the designs disclosed in U.S. published patent application No. us2013/0312932, U.S. published patent application No.2015/0204611, and U.S. published patent application No. 2015/0330709.
The above-described embodiment of the present invention, which uses primary tubes of standard cross-sectional shape and area (200mm x 18.7mm, see, e.g., fig. 6 (except for tube length)), increases heat capacity by 5% over the existing standard a-frame technology and greatly reduces installation costs by a similar degree.
According to a most preferred embodiment, the above described new ACC design may be used in conjunction with a primary condenser tube having a cross-sectional dimension of 200mm width (air stroke length), a cross-sectional height (perpendicular to the air stroke length) of less than 10mm, preferably 4-10mm, more preferably 5.0-9mm, even more preferably 5.2-7mm, and most preferably 6.0mm height (tube thickness of 0.8 mm, tube inner diameter of 4.4 mm), a fin height of 8-12mm, preferably 10mm, with 8-12 fins, preferably 11 fins per inch (fig. 7). Fig. 11 and 12 illustrate a plurality of primary condensing unit tubes and fins assembled into a primary condensing unit tube bundle according to one embodiment of the present invention. According to the preferred embodiment, an additional 17% capacity increase is made for a single unit operating at constant fan power, resulting in a total capacity increase of 30% compared to the prior art a-frame design with standard tubes.
According to another preferred embodiment, the actual fins may be 16-22mm in height, preferably 18.5mm in height, and span the space between two adjacent tubes, effectively allowing 8-11mm fins to be used per tube on each side.
The above description of fin types and sizes is not intended to limit the present invention. The inventive tubes described herein may be used with any type of fin without departing from the scope of the invention.
Claims (12)
1. A large field erected air cooled industrial steam condensing unit connected to an industrial steam production facility, comprising:
a plurality of pairs of heat exchanger tube bundles, each pair of heat exchanger tube bundles arranged in a V-shaped configuration and each heat exchanger tube bundle having a longitudinal axis and a transverse axis perpendicular to the longitudinal axis,
each heat exchanger tube bundle comprising a plurality of steam inlet manifolds, a plurality of primary condensing units, a plurality of outlet condensate headers, and at least one secondary condensing unit;
each primary condensing unit comprises a plurality of finned tubes, the longitudinal axis of each finned tube being parallel to the longitudinal axis of each heat exchanger tube bundle;
each secondary condensing unit comprises a plurality of finned tubes, the longitudinal axis of each finned tube being parallel to the transverse axis of each heat exchanger tube bundle;
a longitudinal axis of each of the steam inlet manifolds is parallel to a transverse axis of each of the heat exchanger tube bundles, each steam inlet manifold is configured to receive steam from a steam distribution manifold located below the heat exchanger tube bundles and distribute the steam to first ends of the plurality of finned tubes in the respective primary condensing unit;
a longitudinal axis of each said outlet condensate header being parallel to a transverse axis of said each heat exchanger tube bundle and connected on a first side to second ends of said plurality of finned tubes of a respective primary condensing device to collect condensate, uncondensed steam and non-condensable gases therefrom,
each of said outlet condensate headers being connected at a bottom end to a bottom end of said at least one secondary condensing device, each of said outlet condensate headers also being connected at a bottom end to a condensate collecting pipe, an
Each of said secondary condensing means is connected at a top end to a non-condensable collecting tube.
2. A large field erected air cooled industrial steam condensing unit according to claim 1, comprising the same number of primary and secondary condensing units, each paired with a single primary condensing unit.
3. A large field erected air cooled industrial steam condensing unit according to claim 2 wherein each heat exchanger tube bundle comprises four primary condensing units and four secondary condensing units, wherein the direction from left to right of each primary condensing unit/secondary condensing unit pair is reversed with respect to the adjacent primary condensing unit/secondary condensing unit pair, such that a first pair of said steam inlet manifolds in a heat exchanger tube bundle are directly adjacent to each other and a second pair of said steam inlet manifolds in the same heat exchanger tube bundle are directly adjacent to each other.
4. The large field erected air cooled industrial steam condensing unit according to claim 3, wherein the bottom end of said steam inlet manifold of a first heat exchanger tube bank is adjacent to the bottom end of the steam inlet manifold of a second heat exchanger tube bank in a pair of heat exchanger tube banks.
5. The large field erected air cooled industrial steam condensing apparatus according to claim 4, wherein the bottom ends of two adjacent steam inlet manifolds of a first heat exchanger tube bank and the bottom ends of two adjacent steam inlet manifolds of a second heat exchanger tube bank of a pair of heat exchanger tube banks are connected to a first end of a quad type steam manifold adapter and wherein the second end of said quad type steam manifold adapter is connected to a steam supply manifold.
6. A large field erected air cooled industrial steam condensing unit according to claim 1 wherein said plurality of finned tubes in said primary condensing unit are 2.0 to 2.8m in length, 200mm in cross sectional width and 4-10mm in cross sectional height.
7. A large field erected air cooled industrial steam condensing unit according to claim 6 wherein the cross sectional height of said plurality of finned tubes is 5.2-7 mm.
8. A large field erected air cooled industrial steam condensing unit according to claim 7 wherein the cross sectional height of said plurality of finned tubes is 6 mm.
9. A large field erected air cooled industrial steam condensing unit according to claim 1 wherein said plurality of finned tubes in said primary condensing unit have fins attached to the flat sides of said plurality of finned tubes, said fins having a height of 10mm with 9 to 12 fins disposed per inch of spacing.
10. A large field erected air cooled industrial steam condensing unit according to claim 1 wherein said plurality of finned tubes in said primary condensing unit have fins attached to the flat sides of said plurality of finned tubes, said fins having a height of 18mm to 20mm, spanning the space between and contacting adjacent tubes, with 9 to 12 fins per inch spacing.
11. A large field erected air cooled industrial steam condensing unit according to claim 1 wherein the surface area of all secondary condensing units in a heat exchanger tube bundle is 10-20% of the surface area of all primary condensing units in the same heat exchanger tube bundle.
12. A large field erected air cooled industrial steam condensing unit according to claim 4 wherein two primary/secondary condensing unit pairs are adjacent to each other and the secondary condensing units of both pairs are adjacent to each other, said two secondary condensing units being combined into a single secondary condensing unit.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110173115.0A CN112923745A (en) | 2016-12-22 | 2017-07-28 | Air cooling type industrial steam condensing device of microtube |
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| Application Number | Priority Date | Filing Date | Title |
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| US201662438142P | 2016-12-22 | 2016-12-22 | |
| US62/438,142 | 2016-12-22 | ||
| US15/624,587 | 2017-06-15 | ||
| US15/624,587 US10024600B2 (en) | 2016-06-21 | 2017-06-15 | Mini-tube air cooled industrial steam condenser |
| PCT/US2017/038430 WO2017223139A1 (en) | 2016-06-21 | 2017-06-21 | Mini-tube air cooled industrial steam condenser |
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| CN112923745A (en) | 2021-06-08 |
| CN110494712A (en) | 2019-11-22 |
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