WO2018126694A1 - 一种强力冷却的直接空冷凝汽器散热单元及空冷岛 - Google Patents

一种强力冷却的直接空冷凝汽器散热单元及空冷岛 Download PDF

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Publication number
WO2018126694A1
WO2018126694A1 PCT/CN2017/097691 CN2017097691W WO2018126694A1 WO 2018126694 A1 WO2018126694 A1 WO 2018126694A1 CN 2017097691 W CN2017097691 W CN 2017097691W WO 2018126694 A1 WO2018126694 A1 WO 2018126694A1
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WIPO (PCT)
Prior art keywords
air
air supply
flow guiding
heat dissipating
supply ring
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PCT/CN2017/097691
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English (en)
French (fr)
Inventor
程友良
张宁
程伟良
施宏波
周玉
李卫华
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华北电力大学
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Priority to US16/463,966 priority Critical patent/US11175096B2/en
Publication of WO2018126694A1 publication Critical patent/WO2018126694A1/zh

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • 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
    • F28B2001/065—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 with secondary condenser, e.g. reflux condenser or dephlegmator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B7/00—Combinations of two or more condensers, e.g. provision of reserve condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/10—Particular layout, e.g. for uniform temperature distribution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/08—Fluid driving means, e.g. pumps, fans

Definitions

  • the invention relates to a heat-dissipating cooling device for a thermal power plant, in particular to a heat-cooling unit for a direct-cooling condenser with strong cooling.
  • Air cooling has become the main cooling method.
  • the use of air cooling is the air cooling island composed of several air condenser cooling units as the main heat sink for the steam exhaust of the power plant.
  • the air condenser heat dissipating unit known to the inventors has a problem that the air flow rate is low.
  • Another object of the present invention is to provide an air-cooled island having the above-described strongly cooled direct air condenser heat sink unit.
  • a powerfully cooled direct air condenser heat dissipating unit comprises a cooling wall having a shape of a rotating body having a longitudinal axis, a blowing device and a guiding device, the guiding device is located in the cooling wall, and the air blowing device
  • the utility model comprises a unit air supply passage, a supply air ring and a wind collecting chamber, wherein the air supply ring is located at a lower part of the cooling wall, the air supply ring is a ring-shaped annular body, and a ring slit air outlet is arranged at a lower part of the air supply ring;
  • the wind collecting chamber is in a pot, and the upper part of the collecting air chamber is connected with the air supply ring;
  • the unit air supply passage is provided with a partition plate, and the partition plate divides the unit air supply passage into two upper and lower air passages, and is located at the upper part.
  • the air duct is connected to the cavity of the air supply ring, and the air duct at
  • the further flow guiding device is composed of a circular arc guiding surface, a spiral guiding surface and a rounding table guiding surface which are arranged from the bottom to the top, and the lower part of the circular guiding surface is penetrated into the air blowing ring, and the spiral guiding surface is outside.
  • the profile is a rounded table shape, distributed in the outer circumference of the rounded table shape Spiral groove.
  • the further cooling wall is provided with a heat exchange tube and a heat dissipating fin, a steam distribution pipe is arranged at the top of the cooling wall, and a condensed water recovery pipe is arranged at the bottom of the cooling wall, and the upper part of the air supply ring is connected with the condensed water recovery pipe, and the diversion table is arranged
  • the top of the arc is closedly connected with the steam distribution pipe, and the top of the circular flow guiding surface is closed to the bottom of the spiral flow guiding surface, and the top of the spiral flow guiding surface is closedly connected with the bottom of the flow guiding surface of the round table.
  • the height of the further arc-conducting surface is 0.2-0.3 times the height of the stave, and the height of the spiral-conducting surface is 0.4-0.5 times the height of the stave.
  • the conical angle a of the further spiral flow guiding surface is 30-60°
  • the inclination angle c of the tangential line of the spiral groove with respect to the axis is 20-50°
  • the cone angle b of the flow guiding surface of the round table is 70-120°.
  • the cross section of the further air supply ring is of a water drop type, and the air outlet is disposed at the inner side wall of the air supply ring.
  • the center of the further flow guiding device, the center of the cooling wall, the center of the air supply ring, and the center of the collecting chamber are collinear.
  • Further contours of the stave are in the shape of a truncated cone, a hyperboloid or an arc.
  • a further unit air supply passage is connected to the main air duct, and a fan is arranged in the main air duct.
  • the flow guiding device is in the form of a rotating body having a longitudinal axis, and the flow guiding device comprises a second heat exchange tube, a second heat dissipating fin, a second steam distribution tube and a second condensed water recovery tube; the second steam distribution tube is located at the Two condensed water recovery pipes are above; two ends of the plurality of second heat exchange tubes are respectively connected with the second steam distribution pipe and the second condensed water recovery pipe; and a plurality of second heat dissipation are connected between the adjacent second heat exchange tubes Fin.
  • the distance between the second heat exchange tube and the longitudinal axis of the flow guiding device is gradually reduced along the direction from the second steam distribution pipe to the second condensate recovery pipe.
  • each of the second heat exchange tubes is evenly arranged around the longitudinal axis of the flow guiding device.
  • the flow guiding device further includes a lower guiding portion connected to the second condensed water collecting pipe; the lower guiding portion protrudes downward into the air blowing ring with respect to the second condensed water collecting pipe, and the protruding portion has an arc shape External outline.
  • Air-cooled islands including main air ducts, fans, and any of the above-mentioned powerfully cooled direct air condenser heat sink units;
  • the fan is disposed in the main air duct; each unit air supply passage is connected to the main air duct.
  • main air duct extends along a spiral trajectory.
  • the embodiment of the invention provides a powerfully cooled direct air condenser heat dissipating unit, and the partition partitions the inside of the unit air supply passage into two upper and lower air passages, so that a part of the air in the unit air supply passage enters the wind collection chamber, and the other part Enter the air supply ring and blow it out at high speed from the air outlet.
  • the high-speed air blown out by the air outlet drives the air in the wind collecting chamber upward to the cooling wall, increasing the flow rate of the air blown to the cooling wall, improving the utilization rate of the air, and improving the heat dissipation efficiency.
  • the air-cooling island provided by the embodiment of the present invention has the above-mentioned powerfully cooled direct air condenser heat dissipating unit. Therefore, the heat dissipation efficiency of the air-cooled island is also improved.
  • the flow rate of air blown to the stave is increased, thereby reducing the performance, quantity and power consumption requirements of the fan in the main duct.
  • the air-cooled islands provided by the embodiments of the present invention can achieve higher heat dissipation efficiency without increasing the performance of the fan, increasing the number of fans and power consumption.
  • FIG. 1 is a schematic diagram showing the external structure of a powerfully cooled direct air condenser heat dissipating unit according to Embodiment 1 of the present invention
  • FIG. 2 is a schematic diagram showing the internal structure of a heat-cooling direct air condenser heat dissipating unit according to Embodiment 1 of the present invention
  • Figure 3 is an enlarged view of the portion III of Figure 2;
  • FIG. 4 is a schematic diagram showing the internal structure of a heat-cooling direct air-cooling condenser heat dissipation unit according to Embodiment 2 of the present invention.
  • FIG. 5 is a schematic structural view of a heat-cooling unit of a direct-cooling direct air condenser according to Embodiment 3 of the present invention.
  • FIG. 6 is a schematic structural diagram of an air-cooled island according to Embodiment 4 of the present invention.
  • FIG. 1 is a schematic diagram showing the external structure of a powerfully cooled direct air condenser heat sink unit 010 according to the embodiment
  • FIG. 2 is a powerfully cooled direct air condenser heat sink unit provided in the embodiment.
  • the strongly cooled direct air condenser heat sink unit 010 includes a stave 100 and a blower 300.
  • the outer shape of the stave 100 is a revolving shape having a longitudinal axis, and the stave 100 defines a cooling space 100a.
  • the stave 100 is in the shape of a truncated cone whose diameter gradually increases from the top to the bottom. It can be understood that in other embodiments, the stave 100 can also be a hyperboloid or curved surface (the bus bar is an arc).
  • the stave 100 includes a first heat exchange tube 110, a first steam distribution tube 130, and a first condensed water recovery tube 140.
  • the first steam distribution pipe 130 and the first condensate recovery pipe 140 are both annular.
  • the first steam distribution pipe 130 and the first condensate recovery pipe 140 are coaxial.
  • the outer diameter of the first steam distribution pipe 130 is smaller than the outer diameter of the first condensate recovery pipe 140.
  • the first steam distribution pipe 130 is located above the first condensate recovery pipe 140.
  • the plurality of first heat exchange tubes 110 are evenly arranged around the axis of the first steam distribution tube 130.
  • One end of the first heat exchange tube 110 is in communication with the first steam distribution tube 130, and the other end of the first heat exchange tube 110 is first condensed.
  • the water recovery pipe 140 is in communication.
  • the steam is sent to the first steam distribution pipe 130 and then flows along the first heat exchange pipe 110. During the flow of the steam along the first heat exchange tube 110, heat is exchanged with the outside air through the first heat exchange tube 110 to condense the steam.
  • the stave 100 further includes a first heat dissipating fin 120.
  • a plurality of first heat dissipating fins 120 are disposed between adjacent first heat exchange tubes 110. Both ends of the first heat dissipating fin 120 are respectively connected to the adjacent two first heat exchange tubes 110.
  • the air blowing device 300 includes a blower ring 310, a collecting chamber 320, and a unit air supply passage 330.
  • the air supply ring 310 is annular, and the inner circumferential surface of the air supply ring 310 defines a first air inlet space 310a.
  • the air supply ring 310 is located below the first condensed water recovery pipe 140 and is connected to the first condensed water recovery pipe 140. Referring to FIG. 3 in combination, FIG. 3 is an enlarged view of FIG. 2, showing the cross-sectional structure of the air supply ring 310.
  • the cross section of the air supply ring 310 includes a first annular surface 311, a second annular surface 312, and a third annular surface 313.
  • the third annular surface 310b is enclosed by the third toroidal surface 313.
  • the first annular surface 311 is located outside the second annular surface 312, and the upper ends of the first annular surface 311 and the second annular surface 312 are connected to each other, and the outer circumferential edge of the third annular surface 313 is connected to the lower end of the first annular surface 311.
  • the inner circumference of the third annular surface 313 is spaced apart from the second annular surface 312 to form an annular slit-shaped air outlet 310c.
  • the second air inlet space 310b communicates with the first air inlet space 310a through the air outlet 310c.
  • the plenum 320 includes a bottom plate 321 and an annular shroud 322 extending along the edge of the bottom plate 321 .
  • the bottom plate 321 and the shroud 322 together define an upper open plenum space 320a.
  • the upper end of the louver 322 is connected to the lower end of the first annular surface 311 such that the plenum space 320a communicates with the first air inlet space 310a.
  • a partition plate 331 is disposed in the unit air supply passage 330.
  • the partition plate 331 partitions the unit air supply passage 330 into upper and lower air passages, which are an upper air passage 330a and a lower air passage 330b, respectively.
  • the upper air passage 330a communicates with the second air inlet space 310b
  • the lower air passage 330b communicates with the air collection space 320a.
  • the air in the unit air supply passage 330 enters the air collection space 320a through the lower air passage 330b
  • the other portion enters the second air inlet space 310b through the upper air passage 330a and is blown out by the air outlet 310c at a high speed to enter the first air inlet space 310a.
  • the high-speed air in the first air inlet space 310a drives the air in the air collecting space 320a to flow into the cooling space 100a at a high speed. In this way, the flow rate of the air blown toward the stave 100 is increased.
  • the high-speed air in the first air inlet space 310a drives the air in the air collecting space 320a to flow into the cooling space 100a at a high speed
  • a partial negative pressure is generated in the air collecting space 320a, so that more air in the lower air channel 330b enters the set.
  • the wind space 320a balances the air pressure, thereby increasing the amount of air entering the cooling space 100a, improving the cooling efficiency.
  • the distance between the second annular surface 312 and the first annular surface 311 along the axial direction of the air supply ring 310 is gradually increased, along the radial direction of the air supply ring 310.
  • the inner circumference of the three-ring surface 313 is located inside the lower end of the second annular surface 312, and the third annular surface 313 has an arc shape that protrudes downward.
  • the air entering the second air inlet space 310b can be blown to the third annular surface 313 from the top to the top at a high speed, and then blown upward by the air outlet 310c under the reflection of the third annular surface 313, thereby driving the air collecting space 320a.
  • the air inside flows into the cooling space 100a at a high speed, so that the air can efficiently enter the cooling space 100a, reducing the power loss in the air flow, and further improving the air utilization rate and heat dissipation efficiency.
  • the strongly cooled direct air condenser heat sink unit 010 further includes a first The flow guiding device 200 in the air inlet space 310a.
  • the flow guiding device 200 is for guiding the air so that the air can be blown to various parts of the cooling wall 100.
  • the flow guiding device 200 in this embodiment adopts the following structure.
  • the flow guiding device 200 as a whole has a substantially rounded table shape (i.e., the diameter of the flow guiding device 200 gradually decreases from top to bottom).
  • the air entering the cooling space 100a can be diffused radially outward and obliquely upward under the guidance of the outer peripheral surface of the flow guiding device 200, so that the air entering the first air inlet space 310a can be blown toward the cooling wall 100.
  • the air flow rate is gradually decreased, and the flow guiding device 200 as a whole has a substantially rounded table shape, so that the distance between the cooling wall 100 and the flow guiding device 200 gradually increases in the downward direction. Reduced.
  • the lower air will flow a long distance to reach the cooling wall 100, and the upper air only needs to flow a short distance to reach the cooling wall 100, which makes the air flow rate to the various parts of the cooling wall 100 substantially the same. Furthermore, uniform heat dissipation to various parts of the cooling wall 100 is achieved, and the layout of the air flow field and the temperature field is more reasonable.
  • the upper end of the flow guiding device 200 is sealingly connected with the first steam distribution pipe 130 to prevent air from flowing out from the upper end of the cooling wall 100, so that more air can be used for dissipating heat to the cooling wall 100, thereby improving air utilization. rate.
  • the outer surface of the flow guiding device 200 includes a circular arc guiding surface 210, a spiral guiding surface 220, and a rounding table guiding surface 230 arranged in order from bottom to top.
  • the arc-shaped flow guiding surface 210 is a circular arc surface convex downward from the lower end of the flow guiding device 200 (corresponding to the circular arc guiding surface 210 being a teardrop shape), and the circular arc guiding surface 210 penetrates into the first inlet air space 310a Inside.
  • the air flowing to the cooling space 100a is diverted by the circular arc guiding surface 210 such that a part of the air flows directly to the lower portion of the cooling wall 100, and the other portion goes up along the spiral flow guiding surface 220.
  • the air flow resistance is reduced, and on the other hand, part of the air can be directed to the lower portion of the cooling wall 100, and the heat dissipation efficiency of the lower portion of the cooling wall 100.
  • the spiral flow guiding surface 220 is provided with a spiral guiding groove 220a, and part of the air is blown in the tangential direction of the guiding groove 220a toward the middle portion and the middle portion of the cooling wall 100 under the guidance of the guiding groove 220a, and then The middle and upper portions of the stave 100 are effectively cooled. The remaining air continues to ascend and flows to the upper portion of the stave 100 under the action of the round table diversion surface 230, thereby effectively cooling the upper middle portion of the stave 100. In this way, the air is sufficiently blown to each portion of the stave 100 to maximize the use of air to dissipate heat.
  • the height of the arc-shaped flow guiding surface 210 is 0.2-0.3 times the height of the cooling wall 100, and the spiral guiding surface 220 is The height is 0.4-0.5 times the height of the stave 100.
  • the taper angle a of the spiral flow guiding surface 220 is 30-60°, the inclination angle c of the guiding groove 220a with respect to the axis of the flow guiding device 200 is 20-50°, and the taper angle b of the rounding table guiding surface 230 is 70- 120°.
  • the cooling wall 100, the flow guiding device 200, the air supply ring 310, and the collecting chamber 320 are coaxial.
  • FIG. 4 is a schematic diagram showing the internal structure of the strongly cooled direct air condenser heat sink unit 010 according to the embodiment.
  • This embodiment is basically the same as Embodiment 1, except that different flow guiding devices are employed.
  • the flow guiding device 500 includes a second heat exchange tube 510, a second steam distribution tube 530, and a second condensed water recovery tube 540.
  • the flow guiding device 500 as a whole has a substantially rounded table shape (i.e., the diameter of the flow guiding device 200 gradually decreases from top to bottom).
  • the second steam distribution pipe 530 is located above the second condensate recovery pipe 540, the second steam distribution pipe 530 is disposed coaxially with the second condensate recovery pipe 540, and the outer diameter of the second steam distribution pipe 530 is larger than the second condensate recovery pipe.
  • the plurality of second heat exchange tubes 510 are evenly arranged around the axis of the second steam distribution tube 530, one end of the second heat exchange tube 510 is in communication with the second steam distribution tube 530, and the other end of the second heat exchange tube 510 is condensed with the second
  • the water recovery pipe 540 is in communication. The steam is sent to the second steam distribution pipe 530 and then along the second heat exchange pipe 510. flow.
  • the flow guiding device 500 acts on the air to enable air to be blown to various parts of the cooling wall 100.
  • the air guiding device 500 also cools the steam in the flow guiding device 500 during the diversion of the air. In this way, the presence of the flow guiding device 500 greatly improves the heat dissipation area of the strongly cooled direct air condenser heat dissipating unit 010, thereby greatly improving the heat dissipation efficiency.
  • the flow guiding device 500 further includes a second heat dissipation fin 520 .
  • a plurality of second heat dissipating fins 520 are disposed between adjacent second heat exchange tubes 510. Both ends of the second heat dissipating fin 520 are respectively connected to the adjacent two second heat exchange tubes 510.
  • the second heat radiating fins 520 can increase the heat radiating area of the flow guiding device 500 and further improve the cooling efficiency of the steam in the second heat exchange tubes 510.
  • the flow guiding device 500 further includes a lower flow guiding portion 550 connected to the second condensed water recovery pipe 540.
  • the lower flow guiding portion 550 protrudes downward into the first air inlet space 310a with respect to the second condensed water recovery pipe 540.
  • the convex portion has an arcuate outer contour.
  • the embodiment provides a powerfully cooled direct air condenser heat sink unit 020.
  • the strongly cooled direct air condenser heat sink unit 020 further includes a main air duct 400 and a fan 410 disposed in the main air duct 400 on the basis of the first embodiment and the second embodiment.
  • the main air duct 400 is in communication with the unit air supply passage 330.
  • the fan 410 operates to introduce external air into the unit air supply passage 330 through the main air passage 400. Since the powerfully cooled direct air condenser heat dissipating unit 020 provided by the embodiment has high air utilization rate and heat dissipation efficiency, it can obtain higher performance without increasing the performance of the fan 410 and increasing the number of fans 410 and power consumption. The heat dissipation efficiency achieves the effect of energy saving and consumption reduction.
  • the embodiment provides an air cooling island 030.
  • the air cooling island 030 includes a plurality of strongly cooled direct air condenser heat dissipating units 010 described in Embodiment 1 or Embodiment 2, and further includes a main air duct 400, and a fan 410 disposed in the main air duct 400.
  • Each unit air supply passage 330 is in communication with the main air passage 400. Due to the high air utilization rate and high heat dissipation efficiency of the powerfully cooled direct air condenser heat dissipating unit 010, higher heat dissipation efficiency can be achieved without increasing the performance of the fan 410 and increasing the number of fans 410 and power consumption. The effect of energy saving and consumption reduction.
  • the main air duct 400 can also extend along a spiral trajectory, so that the same amount of powerful cooling is provided. Under the condition of the direct air condenser heat sink unit 010, the space of the air-cooled island 030 is more concentrated, which facilitates the arrangement of the air-cooled island 030.
  • the powerfully cooled direct air condenser heat dissipating unit provided by the embodiment of the invention increases the flow rate of the air blown to the cooling wall, improves the utilization rate of the air, and improves the heat dissipation efficiency.
  • the air-cooling island provided by the embodiment of the present invention has the above-mentioned powerfully cooled direct air condenser heat dissipating unit, so that the heat dissipation efficiency of the air-cooled island is also improved.
  • the flow rate of air blown to the stave is increased, thereby reducing the performance, quantity and power consumption requirements of the fan in the main duct.
  • the air-cooled islands provided by the embodiments of the present invention can achieve higher heat dissipation efficiency without increasing the performance of the fan, increasing the number of fans and power consumption.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

一种强力冷却的直接空冷凝汽器散热单元（010，020）及空冷岛（030），包括冷却壁面（100）、送风装置（300）和导流装置（200），导流装置（200）位于冷却壁面（100）内，送风装置（300）包括单元送风通道（330）、送风环（310）和集风腔（320），送风环（310）位于冷却壁面（100）下部，送风环（310）为空腔的环形体，在送风环（310）的下部设有环形狭缝出风口（310c）；集风腔（320）上部与送风环（310）连通；单元送风通道（330）内设有隔板（331），隔板（331）将单元送风通道（330）分为上下两个风道，位于上部的风道（330a）连通送风环（310）的空腔，位于下部的风道（330b）连通集风腔（320）。在同等分机功率的条件下可以增加空气流量和流速，达到换热效率高的目的。

Description

一种强力冷却的直接空冷凝汽器散热单元及空冷岛
相关申请的交叉引用
本申请要求于2017年01月5日提交中国专利局的申请号为201710006117.4、名称为“一种强力冷却的直接空冷凝汽器散热单元”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及一种火力电厂散热冷却装置，具体涉及一种强力冷却的直接空冷凝汽器散热单元。
背景技术
目前火力发电行业很多冷凝汽器散热单元采用空冷的方式，特别建在富煤缺水地区的火力发电厂，空冷成为主要的冷却方式。采用空冷是将数个空冷凝汽器散热单元组成的空冷岛作为电厂汽轮机排汽的主要散热设备。发明人已知的空冷凝汽器散热单元存在空气流速低的问题。
发明内容
本发明的目的在于提供一种强力冷却的直接空冷凝汽器散热单元，以改善现有的空冷凝汽器散热单元存在的空气流速低的问题。
本发明的另一个目的在于提供一种空冷岛，该空冷岛具备上述的强力冷却的直接空冷凝汽器散热单元。
本发明的实施例通过以下技术方案实现：
一种强力冷却的直接空冷凝汽器散热单元，包括冷却壁，冷却壁的外形为具有纵向轴线的回转体形，还包括送风装置和导流装置，导流装置位于冷却壁内，送风装置包括单元送风通道、送风环和集风腔，送风环位于冷却壁下部，送风环为空腔的环形体，在送风环的下部设有环形狭缝出风口；集风腔位于送风环下部，集风腔呈盆装，集风腔上部与送风环连通；单元送风通道内设有隔板，隔板将单元送风通道分为上下两个风道，位于上部的风道连通送风环的空腔，位于下部的风道连通集风腔。
进一步的导流装置由自下而上设置的圆弧导流面、螺旋导流面、倒圆台导流面构成，圆弧导流面的下部探入送风环内，螺旋导流面的外廓为倒圆台形，在倒圆台形的外周分布 螺旋沟槽。
进一步的冷却壁设有换热管和散热翅片，冷却壁顶部设有蒸汽分配管，冷却壁的底部设有凝结水回收管，送风环上部与凝结水回收管连接，倒圆台导流面的顶部与蒸汽分配管封闭连接,圆弧导流面的顶部与螺旋导流面的底部封闭对接，螺旋导流面的顶部与倒圆台导流面的底部封闭连接。
进一步的圆弧导流面的高度为冷却壁高度的0.2-0.3倍，螺旋导流面的高度为冷却壁高度的0.4-0.5倍。
进一步的螺旋导流面的圆锥角a为30-60°，螺旋沟槽的切线相对轴线的倾角c为20-50°，倒圆台导流面的圆锥角b为70-120°。
进一步的送风环的截面呈水滴型，出风口设置在送风环的内侧壁处。
进一步的导流装置的中心、冷却壁的中心、送风环的中心、集风腔的中心共线。
进一步的冷却壁的外廓形状为圆台形、双曲面形或弧形。
进一步的单元送风通道连通主风道，主风道内设有风机。
进一步的，导流装置为具有纵向轴线的回转体形，导流装置包括第二换热管、第二散热翅片、第二蒸汽分配管和第二凝结水回收管；第二蒸汽分配管位于第二凝结水回收管上方；多个第二换热管的两端分别与第二蒸汽分配管和第二凝结水回收管连通；相邻的第二换热管之间连接有多个第二散热翅片。
进一步的，沿第二蒸汽分配管至第二凝结水回收管的方向，第二换热管与导流装置的纵向轴线之间的距离逐渐减小。
进一步的，各个第二换热管围绕导流装置的纵向轴线均匀布置。
进一步的，导流装置还包括与第二凝结水回收管连接的下导流部；下导流部相对于第二凝结水回收管向下凸出至送风环内，凸出部分具备弧形的外部轮廓。
空冷岛，包括主风道、风机以及上述任意一种强力冷却的直接空冷凝汽器散热单元；
风机设置在主风道内；各个单元送风通道均与主风道连通。
进一步的，主风道沿螺旋轨迹延伸。
本发明的技术方案至少具备以下优点和有益效果：
本发明的实施例提供的强力冷却的直接空冷凝汽器散热单元，隔板将单元送风通道内部分隔为上下两个风道，使得单元送风通道内的空气一部分进入集风腔，另一部分进入送风环并由出风口高速吹出。由出风口吹出的高速空气带动集风腔内的空气向上吹向冷却壁，增加了吹向冷却壁的空气的流速，提高了空气的利用率，提高了散热效率。
本发明的实施例提供的空冷岛，由于具备上述的强力冷却的直接空冷凝汽器散热单元， 因此空冷岛的散热效率也得到提高。另外，由于强力冷却的直接空冷凝汽器散热单元在工作过程中，吹向冷却壁的空气的流速提高，因此也降低了对主风道内风机的性能、数量和功耗的要求。与发明人已知的空冷岛相比，本发明的实施例提供的空冷岛在不提升风机性能、不增加风机数量和功耗的条件下能够获得更高的散热效率。
附图说明
为了更清楚的说明本发明实施例的技术方案，下面对实施例中需要使用的附图作简单介绍。应当理解，以下附图仅示出了本发明的某些实施方式，不应被看作是对本发明范围的限制。对于本领域技术人员而言，在不付出创造性劳动的情况下，能够根据这些附图获得其他附图。
图1是本发明实施例1提供的的强力冷却的直接空冷凝汽器散热单元外部结构示意图；
图2为本发明实施例1提供的的强力冷却的直接空冷凝汽器散热单元内部结构示意图；
图3为图2的III处放大图；
图4为本发明实施例2提供的的强力冷却的直接空冷凝汽器散热单元内部结构示意图；
图5为本发明实施例3提供的强力冷却的直接空冷凝汽器散热单元结构示意图；
图6为本发明实施例4提供的空冷岛的结构示意图。
图中：010-强力冷却的直接空冷凝汽器散热单元；020-强力冷却的直接空冷凝汽器散热单元；030-空冷岛；100-冷却壁；100a-冷却空间；110-第一换热管；120-第一散热翅片；130-第一蒸汽分配管；140-第一凝结水回收管；200-导流装置；210-圆弧导流面；220-螺旋导流面；220a-导流槽；230-倒圆台导流面；300-送风装置；310-送风环；310a-第一进风空间；310b-第二进风空间；310c-出风口；311-第一环面；312-第二环面；313-第三环面；320-集风腔；320a-集风空间；321-底板；322-围板；330-单元送风通道；330a-上风道；330b-下风道；331-隔板；400-主风道；410-风机；500-导流装置；510-第二换热管；520-第二散热翅片；530-第二蒸汽分配管；540-第二凝结水回收管；550-下导流部。
具体实施方式
为使本发明实施例的目的、技术方案和优点更加清楚，下面将结合附图，对本发明实施例中的技术方案进行清楚、完整的描述。显然，所描述的实施例是本发明的一部分实施例，而不是全部的实施例。
因此，以下对本发明的实施例的详细描述并非旨在限制要求保护的本发明的范围，而是仅仅表示本发明的部分实施例。基于本发明中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。
需要说明的是，在不冲突的情况下，本发明中的实施例及实施例中的特征和技术方案可以相互组合。
应注意到：相似的标号和字母在下面的附图中表示类似项，因此，一旦某一项在一个附图中被定义，则在随后的附图中不需要对其进行进一步定义和解释。
在本发明的描述中，需要说明的是，术语“第一”、“第二”等仅用于区分描述，而不能理解为指示或暗示相对重要性。
实施例1：
请参照图1和图2，图1为本实施例提供的强力冷却的直接空冷凝汽器散热单元010的外部结构示意图，图2为本实施例提供的强力冷却的直接空冷凝汽器散热单元010的内部结构示意图。从图1和图2中可以看出，强力冷却的直接空冷凝汽器散热单元010包括冷却壁100和送风装置300。
请继续参照图1和图2，冷却壁100的外形为具有纵向轴线的回转体形，冷却壁100限定冷却空间100a。在本实施例中，冷却壁100为从上至下直径逐渐增大的圆台形。可以理解的，在其他实施方式中，冷却壁100也可以为双曲面形或弧形面(母线为弧线)。进一步的，在本实施例中，冷却壁100包括第一换热管110、第一蒸汽分配管130和第一凝结水回收管140。第一蒸汽分配管130和第一凝结水回收管140均为环形。第一蒸汽分配管130和第一凝结水回收管140同轴。第一蒸汽分配管130的外径小于第一凝结水回收管140的外径。第一蒸汽分配管130位于第一凝结水回收管140的上方。多个第一换热管110围绕第一蒸汽分配管130的轴线均匀布置，第一换热管110的一端与第一蒸汽分配管130连通，第一换热管110的另一端与第一凝结水回收管140连通。蒸汽被送入第一蒸汽分配管130，然后沿着第一换热管110流动。蒸汽在沿着第一换热管110流动过程中，通过第一换热管110与外部的空气产生热交换，使蒸汽冷凝。冷凝得到的凝结水进入第一凝结水回收管140后被排出。为了提高冷却壁100的散热效率，在本实施例中，冷却壁100还包括第一散热翅片120。多个第一散热翅片120设置在相邻的第一换热管110之间。第一散热翅片120的两端分别与相邻的两个第一换热管110连接。通过第一散热翅片120，能够提高冷却壁100的散热面积，进而提高第一换热管110内蒸汽的冷却效率。
请继续参照图1和图2，在本实施例中，送风装置300包括送风环310、集风腔320和单元送风通道330。送风环310为环状，送风环310的内周面限定第一进风空间310a。送风环310位于第一凝结水回收管140的下方，并与第一凝结水回收管140连接。请结合参照图3，图3为图2的III处放大图，示出了送风环310的截面结构。送风环310的截面包括第一环面311、第二环面312和第三环面313。第一环面311、第二环面312 和第三环面313共同围成环状的第二进风空间310b。其中第一环面311位于第二环面312外侧，第一环面311和第二环面312的上端相互连接，第三环面313的外周缘与第一环面311的下端连接。第三环面313的内周缘与第二环面312之间间隔设置，形成环形狭缝状的出风口310c。第二进风空间310b通过出风口310c与第一进风空间310a连通。集风腔320包括底板321以及沿底板321边缘延伸的环形的围板322。底板321与围板322共同限定上方开放的集风空间320a。围板322的上端与第一环面311的下端连接，使得集风空间320a与第一进风空间310a连通。单元送风通道330内设置有隔板331，隔板331将单元送风通道330内分隔为上下两个风道，分别为上风道330a和下风道330b。上风道330a与第二进风空间310b连通，下风道330b与集风空间320a连通。这样，单元送风通道330内的空气，部分通过下风道330b进入集风空间320a，另一部分通过上风道330a进入第二进风空间310b并由出风口310c高速吹出，进入第一进风空间310a中。第一进风空间310a中的高速空气，带动集风空间320a内的空气高速流入冷却空间100a。这样，增加了吹向冷却壁100的空气的流速。另外，第一进风空间310a中的高速空气带动集风空间320a内的空气高速流入冷却空间100a时，会在集风空间320a内产生局部负压，使得下风道330b中的更多空气进入集风空间320a以平衡气压，进而增加了进入冷却空间100a的空气的量，提高了冷却效率。
进一步的，请继续参照图3，在本实施例中，沿送风环310的轴线方向第二环面312与第一环面311的距离逐渐增大，沿送风环310的径向方向第三环面313的内周缘位于第二环面312下端内侧，并且第三环面313呈向下凸出的弧形。这样，进入第二进风空间310b的空气能够首先自上而上高速吹向第三环面313，然后在第三环面313的反射下由出风口310c高速向上吹出，进而带动集风空间320a内的空气高速向上流入冷却空间100a，使得空气能够高效率地进入冷却空间100a，降低了空气流动中的动力损耗，进一步提高了空气的利用率和散热效率。
请继续参照图2，为了使进入第一进风空间310a的空气能够吹向冷却壁100的各个部位，在本实施例中，强力冷却的直接空冷凝汽器散热单元010还包括设置在第一进风空间310a内的导流装置200。导流装置200用于对空气起导流作用，使得空气能够吹向冷却壁100的各个部位。进一步的，本实施例中的导流装置200采用如下结构。导流装置200整体大致呈倒圆台形状(即导流装置200的直径从上至下大致呈逐渐减小的趋势)。这样，进入冷却空间100a的空气在导流装置200外周面的引导下，能够沿径向向外且倾斜向上的方式扩散，进而使得进入第一进风空间310a的空气能够吹向冷却壁100的各个部位。空气至下而上的流动过程中，空气流速是逐渐降低的，导流装置200整体大致呈倒圆台形状，使得沿至下而上的方向，冷却壁100与导流装置200之间的间距逐渐减小。这样 一来，下方的空气会进行流动较长距离才能到达冷却壁100，而上方的空气只需要流动较短的距离即可到达冷却壁100，这使得流向冷却壁100各个部位的空气流速大致相同，进而实现了对冷却壁100各个部位的均匀散热，使空气流场和温度场的布局更加合理。在本实施例中，导流装置200的上端与第一蒸汽分配管130密封连接，避免空气从冷却壁100上端流出，使更多的空气能够用于对冷却壁100散热，提高了空气的利用率。
进一步的，请继续参照图2，在本实施例中，导流装置200的外表面包括从下至上依次布置的圆弧导流面210、螺旋导流面220和倒圆台导流面230。圆弧导流面210为由导流装置200的下端向下凸出的圆弧面(相当于圆弧导流面210为水滴形)，圆弧导流面210探入第一进风空间310a内。这样，向冷却空间100a流动的空气被圆弧导流面210导流，使得一部分空气直接流向冷却壁100的下部，另一部分沿螺旋导流面220上行。如此，一方面降低了空气流动阻力，另一方面使得部分空气能够定向流向冷却壁100的下部，冷却壁100下部的散热效率。进一步的，螺旋导流面220上设置有螺旋形的导流槽220a，部分空气在导流槽220a的引导下沿导流槽220a的切线方向吹向冷却壁100的中部和中上部，进而对冷却壁100的中部和中上部进行有效冷却。其余空气继续上行，并在倒圆台导流面230的作用下流向冷却壁100的上部，进而对冷却壁100的中上部进行有效冷却。这样，使空气充分吹向冷却壁100的每个部位，最大限度的利用空气散热。
请继续参照图2，为了使空气流场和温度场的分布更加合理，在本实施例中，圆弧导流面210的高度为冷却壁100高度的0.2-0.3倍，螺旋导流面220的高度为冷却壁100高度的0.4-0.5倍。螺旋导流面220的圆锥角a为30-60°，导流槽220a的切线相对导流装置200的轴线的倾角c为20-50°，倒圆台导流面230的圆锥角b为70-120°。
请继续参照图2，为了进一步提高散热的均匀性，在本实施例中，冷却壁100、导流装置200、送风环310和集风腔320同轴。
实施例2：
请参照图4，图4为本实施例提供的强力冷却的直接空冷凝汽器散热单元010的内部结构示意图。本实施例与实施例1基本相同，不同之处在于采用了不同的导流装置。在本实施例中，导流装置500包括第二换热管510、第二蒸汽分配管530和第二凝结水回收管540。导流装置500整体大致呈倒圆台形状(即导流装置200的直径从上至下大致呈逐渐减小的趋势)。第二蒸汽分配管530位于第二凝结水回收管540上方，第二蒸汽分配管530与第二凝结水回收管540同轴设置，第二蒸汽分配管530的外径大于第二凝结水回收管540的外径。多个第二换热管510围绕第二蒸汽分配管530的轴线均匀布置，第二换热管510的一端与第二蒸汽分配管530连通，第二换热管510的另一端与第二凝结水回收管540连通。蒸汽被送入第二蒸汽分配管530，然后沿着第二换热管510 流动。蒸汽在沿着第二换热管510流动过程中，通过第二换热管510与外部的空气产生热交换，使蒸汽冷凝。冷凝得到的凝结水进入第二凝结水回收管540后被排出。导流装置500对空气起导流作用，使得空气能够吹向冷却壁100的各个部位。导流装置500在对空气起导流过程中，空气还会对导流装置500中的蒸汽进行冷却。这样一来，导流装置500的存在，大大提高了强力冷却的直接空冷凝汽器散热单元010的散热面积，进而大大提高了散热效率。
请继续参照图4，在本实施例中，为了进一步提高散热效率，在本实施例中，导流装置500还包括第二散热翅片520。多个第二散热翅片520设置在相邻的第二换热管510之间。第二散热翅片520的两端分别与相邻的两个第二换热管510连接。通过第二散热翅片520，能够提高导流装置500的散热面积，进而提高第二换热管510内蒸汽的冷却效率。
请继续参照图4，在本实施例中，导流装置500还包括与第二凝结水回收管540连接的下导流部550。下导流部550相对于第二凝结水回收管540向下凸出至第一进风空间310a中。凸出部分具备弧形的外部轮廓。这样，向冷却空间100a流动的空气被下导流部550导流，使得一部分空气直接流向冷却壁100的下部，另一部分上行。如此，一方面降低了空气流动阻力，另一方面使得部分空气能够定向流向冷却壁100的下部，冷却壁100下部的散热效率。
实施例3：
请参照图5，本实施例提供一种强力冷却的直接空冷凝汽器散热单元020.。强力冷却的直接空冷凝汽器散热单元020在实施例1和实施例2的基础上，还包括主风道400，以及设置在主风道400中的风机410。主风道400与单元送风通道330连通。风机410工作，从而将外部的空气通过主风道400引入单元送风通道330。由于本实施例提供的强力冷却的直接空冷凝汽器散热单元020空气的利用率和散热效率高，因此在不提升风机410性能、不增加风机410数量和功耗的条件下能够获得更高的散热效率，实现了节能降耗的效果。
实施例4：
请参照图6，本实施例提供一种空冷岛030。空冷岛030包括多个实施例1或实施例2中记载的强力冷却的直接空冷凝汽器散热单元010，还包括.主风道400，以及设置在主风道400中的风机410。各个单元送风通道330均与所述主风道400连通。由于强力冷却的直接空冷凝汽器散热单元010空气的利用率和散热效率高，因此在不提升风机410性能、不增加风机410数量和功耗的条件下能够获得更高的散热效率，实现了节能降耗的效果。
在本实施例中，.主风道400也可以沿螺旋轨迹延伸，这样在具备相同数量的强力冷却 的直接空冷凝汽器散热单元010的条件下，空冷岛030的占地面积更加集中，便于空冷岛030的布置。
显然，本发明的上述实施例仅仅是为了清楚说明本发明所作的举例，而并非是对本发明的实施方式的限定。对于所属领域的普通技术人员来说，在上述说明的基础上还可以做出其它不同形式的变化或变动。这里无需也无法对所有的实施方式予以穷举。凡在本发明的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本发明权利要求的保护范围之内。
工业实用性
本发明的实施例提供的强力冷却的直接空冷凝汽器散热单元，增加了吹向冷却壁的空气的流速，提高了空气的利用率，提高了散热效率。
本发明的实施例提供的空冷岛，由于具备上述的强力冷却的直接空冷凝汽器散热单元，因此空冷岛的散热效率也得到提高。另外，由于强力冷却的直接空冷凝汽器散热单元在工作过程中，吹向冷却壁的空气的流速提高，因此也降低了对主风道内风机的性能、数量和功耗的要求。与发明人已知的空冷岛相比，本发明的实施例提供的空冷岛在不提升风机性能、不增加风机数量和功耗的条件下能够获得更高的散热效率。

Claims (15)

  1. 一种强力冷却的直接空冷凝汽器散热单元，包括冷却壁，冷却壁的外形为具有纵向轴线的回转体形，其特征在于：所述强力冷却的直接空冷凝汽器散热单元还包括送风装置和导流装置，所述导流装置位于所述冷却壁内，所述送风装置包括单元送风通道、送风环和集风腔，所述送风环位于所述冷却壁下部，所述送风环为空腔的环形体，在所述送风环的下部设有环形狭缝出风口；所述集风腔位于所述送风环下部，所述集风腔呈盆装，所述集风腔上部与所述送风环连通；所述单元送风通道内设有隔板，所述隔板将所述单元送风通道分为上下两个风道，位于上部的所述风道连通所述送风环的空腔，位于下部的所述风道连通所述集风腔。
  2. 根据权利要求1所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：所述导流装置由自下而上设置的圆弧导流面、螺旋导流面、倒圆台导流面构成，所述圆弧导流面的下部探入所述送风环内，所述螺旋导流面的外廓为倒圆台形，在所述螺旋导流面的外周分布螺旋沟槽。
  3. 根据权利要求2所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：所述冷却壁设有第一换热管和第一散热翅片，所述冷却壁顶部设有第一蒸汽分配管，所述冷却壁的底部设有第一凝结水回收管，所述送风环上部与所述第一凝结水回收管连接，所述倒圆台导流面的顶部与所述第一蒸汽分配管封闭连接，所述圆弧导流面的顶部与所述螺旋导流面的底部封闭对接，所述螺旋导流面的顶部与所述倒圆台导流面的底部封闭连接。
  4. 根据权利要求3所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：所述圆弧导流面的高度为所述冷却壁高度的0.2-0.3倍，所述螺旋导流面的高度为所述冷却壁高度的0.4-0.5倍。
  5. 根据权利要求4所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：所述螺旋导流面的圆锥角a为30-60°，所述螺旋沟槽的切线相对所述螺旋导流面的轴线的倾角c为20-50°，所述倒圆台导流面的圆锥角b为70-120°。
  6. 根据权利要求5所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：所述送风环的截面呈水滴型，所述出风口设置在所述送风环的内侧壁处。
  7. 根据权利要求6所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：所述导流装置的中心、所述冷却壁的中心、所述送风环的中心、所述集风腔的中心共线。
  8. 根据权利要求7所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：所述冷却壁的外廓形状为圆台形、双曲面形或弧形。
  9. 根据权利要求8所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：所述 单元送风通道连通主风道，所述主风道内设有风机。
  10. 根据权利要求1所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：所述导流装置为具有纵向轴线的回转体形，所述导流装置包括第二换热管、第二散热翅片、第二蒸汽分配管和第二凝结水回收管；所述第二蒸汽分配管位于所述第二凝结水回收管上方；多个所述第二换热管的两端分别与所述第二蒸汽分配管和所述第二凝结水回收管连通；相邻的所述第二换热管之间连接有多个所述第二散热翅片。
  11. 根据权利要求10所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：沿所述第二蒸汽分配管至所述第二凝结水回收管的方向，所述第二换热管与所述导流装置的纵向轴线之间的距离逐渐减小。
  12. 根据权利要求11所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：
    各个所述第二换热管围绕所述导流装置的纵向轴线均匀布置。
  13. 根据权利要求10所述的强力冷却的直接空冷凝汽器散热单元，其特征在于：所述导流装置还包括与所述第二凝结水回收管连接的下导流部；所述下导流部相对于所述第二凝结水回收管向下凸出至所述送风环内，凸出部分具备弧形的外部轮廓。
  14. 空冷岛，其特征在于，所述空冷岛包括主风道、风机以及多个权利要求1-8、10-13中任意一项所述的强力冷却的直接空冷凝汽器散热单元；
    所述风机设置在所述主风道内；各个所述单元送风通道均与所述主风道连通。
  15. 根据权利要求13所述的空冷岛，其特征在于：
    所述主风道沿螺旋轨迹延伸。
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