• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Heat exchanger (3) for cooling a gas, which heat exchanger comprises first tubes (5) mounted in a tube plate (6), characterized in that the heat exchanger (3) comprises a screen structure (11), the screen structure being a screen (12) mounted at a distance from the tube plate (6), the screen (12) being provided with holes (15) to allow the passage of the gas exiting the first tubes (5) , the screen structure (11) further comprising second tubes (13) connected to the holes (15), the second tubes (13) extending from the screen (12) into the first tubes (5), and a have an external diameter (Do), which is less than the internal diameter (Di) of the first tubes (5), to form a space (17) between the second tubes (13) and the first tubes (5).
    公开号:BE1023641B1
    申请号:E2015/5773
    申请日:2015-11-27
    公开日:2017-05-30
    发明作者:Stephan GEERTS；Henrik Öhman
    申请人:Atlas Copco Airpower, Naamloze Vennootschap；
    IPC主号:
    专利说明:

    Heat exchanger and method for separating a liquid from a gas.
    The present invention relates to a heat exchanger and to a method for separating a liquid from a gas. This liquid will typically, but not necessarily, be a liquid condensate that is formed when the gas is cooled.
    In particular, the present invention relates to a heat exchanger and a method therefor wherein the gas is compressed air and water vapor condenses in this air in the heat exchanger.
    Such heat exchangers are typically used in compressor installations for cooling compressed air and they are used as intermediate coolers between two consecutive compression stages of a multi-stage compressor installation or as an aftercooler downstream of the last compression stage before the compressed air is delivered to a network for use by users. .
    Due to its compression, compressed air often contains more water than the saturation pressure at a given temperature. This water must be removed because it can damage downstream components, mainly due to corrosion and increasing wear of moving parts.
    For this reason, water separators are used after a cooling step to remove water. These water separators can be relatively large and must be pressure-resistant, so that these water separators entail considerable costs.
    Condensate is formed by cooling the compressed air, which can then be separated from the air. Two types of condensed water may be present, more particularly fine droplets that move relatively easily with the air stream, as well as free water mass, which is essentially formed by such droplets deposited on walls or coalesced to form larger amounts of water. , which are only influenced to a limited extent by the air flow.
    For both types of liquid water, there are various optimal ways of removing them from an air stream, in particular with regard to the air flow regimes in the separator. For this reason, individual separators usually do not have a good removal efficiency for both types of liquid water at the same time.
    As a result, complicated and large separators must be used or a low water removal efficiency must be accepted, with the aforementioned disadvantages.
    Furthermore, any component of a device, such as a water separator, which causes a flow disruption, at the same time reduces the energy efficiency of the supply of compressed air to the users and, for that reason alone, the use thereof must be limited or avoided,
    The same considerations apply in other technological areas where liquid, in particular liquid condensate, must be separated from a gas.
    It is an object of the invention to provide a solution to one or more of the aforementioned and other disadvantages by providing a heat exchanger for cooling a gas, which heat exchanger comprises first tubes mounted in or on a tube plate, characterized in that the heat exchanger comprises a screen structure for separating liquid, the screen structure comprising a screen mounted at a distance from the tube plate on the gas side of the tube plate, the screen being provided with holes for the passage of gas coming from the first tubes, the screen structure further comprising second tubes connected to the holes so that gas can flow from the second tubes through the holes, the second tubes extending from the screen into the first tubes, and have an outer diameter, at least away from their end of the screen, which is smaller than the inner diameter of the first tubes, to form a space between the second tubes and the first tubes.
    The first tubes are heat exchange tubes for gas flow therethrough. The heat exchanger will therefore typically be of the known shell and tube type (shell-tube bundle type). The tube plate in this case forms the separation between the gas and a cooling medium in the jacket.
    The screen structure is mounted in the heat exchanger housing between the tube plate and a common gas outlet.
    Such a heat exchanger allows the easy separation of liquid mass, but not necessarily fine entrained condensate mist. which is already in the heat exchanger, but before the gas reaches the liquid clarifier, so that the separator can be designed and built smaller and cheaper than would otherwise be the case and / or the liquid separation efficiency can be improved and / or the pressure drop in the system is reduced can become.
    In a preferred embodiment, the placement and shape of the first and second tubes are such that an annular space is formed between the second tubes and the first tubes. This makes a better removal of the liquid mass possible.
    In another preferred embodiment, the second tubes have a central axis that is straight and that forms a right angle with respect to the tube plate. This results in a lower pressure drop of the gas phase.
    In yet another preferred embodiment, the heat exchanger has a joint outlet for the gas coming from the first tubes, whereby the only possible passage for gas is from the first tubes to the outlet via the second tubes and the aforementioned holes. Alternatively, this can be defined as an embodiment in which the heat exchanger is provided with a housing, leaving no space between the screen structure and the housing.
    This ensures that it is not possible that liquid separated from the gas at the space between the first and second tubes can again cross the path of the gas and can therefore be entrained.
    In yet another preferred embodiment, the inner diameter of the second tubes gradually increases over at least a part of their length in the direction of the screen.
    This makes it possible to reduce the pressure drop of the gas flowing through these second tubes because the length of the narrowest part of the second tubes is limited to a minimum.
    In yet another preferred embodiment, the heat exchanger is provided with an outlet channel for condensate which leads away from the space between the screen and the tube plate, so that condensate can be prevented from accumulating in the heat exchanger.
    This outlet channel will preferably be provided with a valve to prevent gas or condensate from being blown out in an uncontrolled manner.
    In yet another preferred embodiment, the first tubes are internally provided with means for deflecting the flow of gas flowing past the means. This creates a radial force on any condensed liquid droplets that forces them to the walls of the first tubes and thereby increases the collection efficiency of the screen structure.
    These means are of course placed upstream of the position of the second tube. They preferably comprise a spiral flow conductor.
    The invention further relates to a method for separating a liquid from a gas, wherein in a first step a gas containing a liquid is passed through a first tube so that at least a part of the liquid is deposited on the tube wall, and wherein in a second step the gas and the aforementioned part of the liquid are passed along the inlet of a second tube, the second tube being partially inserted into the first tube, the inlet of the second tube being located in the first tube, the second tube having an outer diameter at its inlet that is smaller than the inner diameter of the first tube, so that a space is formed between the first tube and the second tube, so that in this second step at least a portion of the liquid flows through the space and the gas, which is partially or completely stripped of liquid, flows through the second tube.
    With the insight to better illustrate the features of the invention, a preferred embodiment of an improved device is described below as an example without any limiting nature, reference being made to the accompanying drawings, in which:
    Figure 1 shows schematically a compressor installation with an aftercooler and a liquid clarifier, the aftercooler being shown in cross section; Figure 2 shows an enlarged view of the area indicated by F2 in Figure 1; and figure 3 shows an perspective view of some components of the compressor installation of figure 1 in perspective.
    It is noted that in order to better illustrate the invention, Figures 1-3 are not necessarily to scale.
    The compressor installation 1 of Figure 1 is a compressor installation for supplying compressed air. The main components of the compressor installation 1 are a compressor element 2, a jacket tube bundle heat exchanger 3, the jacket side of which is intended to be flowed through a cooling medium, and a water separator 4.
    The heat exchanger 3 mainly consists of a bundle of first tubes 5 in two tube plates 6, 7, which are housed in a housing 8, the housing 8 at the ends of the heat exchanger having a common inlet 9 for the first tubes 5 and a common outlet 10 of the first tubes 5. The first tubes 5 have a length L and an internal diameter Di, with L = 1000 mm and Di = 14 mm in this case, but this need not be the case.
    Between the common outlet 10 and the tube plate closest to the outlet, hereinafter referred to as the first tube plate 6, a screen structure 11 is provided. The screen structure 11 is in this case formed by a flat screen 12 and a series of short second tubes 13, but this need not be the case.
    The flat screen 12 is provided with a raised edge 14 at its circumference. The external diameter D 0 of the second tubes 13 is smaller than the internal diameter D 1 of the first tubes 5. In the present example, D 0 is 12 mm.
    Figure 3 shows a perspective view, viewed from the side of the common outlet 10, of the screen structure 11, the first tube plate 6 and the bundle of first tubes 5.
    By placing the upstanding edge 14 against the first tube plate 6, the screen 12 is placed parallel to the first tube plate 6 at a distance d and is provided with holes 15 at positions corresponding to the position of the first tubes 5. In the current example is d equal to 4 mm.
    The second tubes 13 are each connected to a hole 15, so that one end of the second tubes 13 is placed at the screen 12 and the second end of each second tube 13, hereinafter referred to as the inlet 16, in one of the first tubes 5 is placed.
    The second tubes 13 have an internal diameter Ds which gradually increases from a first value Ds1 at the inlet 16 to a second value Ds2 at the screen 12. In the present example, Ds1 equals 11mm and Ds2 equals 15mm.
    The central axes of the first tubes 5 and second tubes 13 are straight and these are aligned with each other and placed at right angles with the screen 12 and with the first tube plate 6.
    In this way an annular space 17 with a width of 0.5 * (Di-Do), in this case 1 mm, is formed between the first tubes 5 and the second tubes 13, and a collection space 18 is formed between the first tube plate 6 and the screen 12.
    The second tubes are inserted into the first tubes over a distance w, which in this case is 10 mm.
    At the bottom of this collection space 18, an outlet channel 19 is provided in the housing 5, which leads away from this collection space 18. At this point the raised edge 14 has a lower height than around the rest of the circumference of the screen 12, so that the raised edge 14 does not form a barrier between the collecting space 18 and the outlet channel 19. The outlet channel 19 is provided with a valve which is not shown in the figures.
    Spiral flow conductors 20 are provided in the first tubes 5 from the other tube plate, which will further be referred to as the second tube plate 7, close to the second tubes, as shown in Figure 2. These are formed by fins which are placed as internal parts in the first tubes 5 against the walls of the first tubes 5 and which have a spiral shape. The spiral flow guides extend up to a distance x from the second tubes. The distance x in this case is 5 mm.
    The use of the compressor installation 1 is as follows.
    A cooling medium is pumped through the jacket side as indicated by arrow P. The compressor element draws in air from the environment as indicated by arrow Q and compresses this air. This compressed air (compressed air) is thereby heated.
    The heated compressed air is led via the common inlet 9 of the heat exchanger 3 and the first tubes 5 to the common outlet of the heat exchanger 3, as indicated by arrows R, which causes water vapor to condense in the compressed air.
    When the compressed air passes the spiral flow guides 20, it is given an angular deflection by the spiral flow guides 20 and thus a rotating movement around the central axes of the first tubes 5.
    This leads to the droplets of condensed water being forced to the walls of the first tubes and deposited thereon.
    The spiral flow conductors also provide an additional cooling effect on the air through their direct contact with the cooled walls of the first tubes.
    When the mixed flow of air and condensed water reaches the inlet 16 of the second tubes 13, the air will flow through the second tubes 13 and the holes 15 in the screens 12 to the common outlet 10 of the heat exchanger 3.
    The liquid water that has collected on the walls of the first tubes 5 will flow via the annular space 17 to the collection space 18, as indicated by arrows S, and then down to the outlet channel 19.
    Because of the screen construction 11, the water in the collecting space 18 can no longer come into contact with the flowing air and can be carried away again.
    The collected water is removed from the heat exchanger 3 via the outlet channel 19, as indicated by arrow T.
    The air that has been stripped of part of its water flows from the common outlet 10 to the water separator 4, where the rest of the water is removed, as indicated by arrow U.
    The compressed air is now ready to be delivered to end users, as indicated by arrow V, or may alternatively undergo a further compression step in a similar compressor installation to further increase the pressure thereof.
    The present invention is in no way limited to the embodiment described by way of example and shown in the figures and such an improved heat exchanger can therefore be realized in various forms without departing from the scope of the invention.
    权利要求:
    Claims (16)
    [1]
    Conclusions
    Heat exchanger (3) for cooling a gas, which heat exchanger comprises first tubes (5) mounted in a tube plate (6), characterized in that the heat exchanger (3) comprises a screen structure (11), the screen construction comprises a screen (12) mounted at a distance from the tube plate (6), the screen (12) being provided with holes (15) around the passage of the gas coming from the first tubes (5), enable, wherein the screen structure (11) further comprises second tubes (13) connected to the holes (15), the second tubes (13) extending from the screen (12) into the first tubes (5) and have an outer diameter (Do) smaller than the inner diameter (Di) of the first tubes (5), to form a space (17) between the second tubes (13) and the first tubes (5) .
    [2]
    Heat exchanger according to claim 1, characterized in that the placement and shape of the first tubes (5) and the second tubes (13) are such that an annular space is formed between the second tubes (13) and the first tubes ( 5).
    [3]
    Heat exchanger according to one of the preceding claims, characterized in that the second tubes (13) have a central axis that is straight and forms a right angle with respect to the tube plate (6). of the preceding claims, characterized in that the screen (12) and the tube plate (6) are parallel to each other.
    [5]
    Heat exchanger according to one of the preceding claims, characterized in that it has a common outlet (10) for gas coming from the first tubes (5), the only possible passage for gas from the first tubes (5) to the common outlet (10) via the second tubes (13) and the aforementioned holes (15).
    [6]
    Heat exchanger according to one of the preceding claims, characterized in that the internal diameter of the second tubes gradually increases over at least a part of its length in the direction of the screen.
    [7]
    Heat exchanger according to one of the preceding claims, characterized in that it is provided with an outlet channel (19) for liquid, which leads away from the space (18) between the screen (12} and the tube plate (6).
    [8]
    Heat exchanger according to one of the preceding claims, characterized in that the first tubes (5) are internally provided with means (20) for deflecting the flow of gas flowing along the means (20).
    [9]
    Heat exchanger according to claim 8, characterized in that the aforementioned means (20) comprise a spiral flow conductor.
    [10]
    Heat exchanger according to claim 9, characterized in that the spiral flow conductor (20) extends to a certain distance (x) from the second tubes (13) in the first tubes, said determined distance (x) being at least 5% of the internal diameter (Di) of the first tubes (5) is.
    [11]
    11. Method for separating a liquid from a gas, wherein in a first step a gas containing a liquid is passed through a first tube (5), so that at least a part of the liquid on the wall of the first tube (5) is deposited and wherein in a second step the gas and the aforementioned part of the liquid are passed along an inlet (16) of a second tube (13), the second tube (13) being at least partially in the first tube (15) is inserted, the inlet (16) of the second tube (13) being in the first tube (5), the second tube (13) having an external diameter (Do) at its inlet (16) , which is smaller than the internal diameter (Di) of the first tube (5), so that a space (17) is formed between the first tube (5) and the second tube (13), wherein in this second step at least one part of the liquid flows through the space (17) and the gas, partially or completely stripped of liquid, flows through the second tube (13) .
    [12]
    Method according to claim 11, characterized in that the first tube (5) is cooled externally. Method according to claim 11 or 12, characterized in that an angular movement is imposed on the gas containing the liquid in the first tube (5) before the second step.
    [14]
    Method according to one of claims 11 to 13, characterized in that the space between the first tube (5) and the second tube {13} is an annular space (17).
    [15]
    Method according to one of claims 11 to 14, characterized in that it is carried out in a heat exchanger (3) according to one of claims 1 to 9.
    [16]
    Method according to any of claims 10 to 15, characterized in that the gas is air and the liquid is water.
    [17]
    A method for producing dry compressed air, wherein air is compressed in a first compressor element (2) and the compressed air is cooled and treated according to a method according to claim 16.
    [18]
    A method according to claim 17, wherein after being cooled and treated according to a method according to claim 16, the compressed air in a second compressor element is further compressed.
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    同族专利:
    公开号 | 公开日
    BE1023641A1|2017-05-30|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    AT287030B|1966-06-27|1971-01-11|Waagner Biro Ag|Device to prevent overheating of the inlet points of the tubes or the tube plates of tube heat exchangers|
    NL7416887A|1974-12-24|1976-06-28|Breda Backer Rueb Maschf|PIPE HEAT EXCHANGER.|
    DE4022802A1|1990-07-18|1992-01-23|Milorad Bozovic|Drying appts. esp. for compressed air - has two heat exchange regions operating in freeze-thaw counter-cycles|
    US5715696A|1993-07-26|1998-02-10|Hiross International Corporation B.V.|Arrangement for reducing the humidity content of a gaseous medium|
    US20030116306A1|2001-12-26|2003-06-26|Besik Ferdinand K.|Rotating film shell and tube type heat exchanger - evaporator|
    EP1475579A2|2003-05-08|2004-11-10|Alley Enterprises Limited|A condensing unit|
    DE102012208100A1|2012-05-15|2013-11-21|Behr Gmbh & Co. Kg|Exhaust gas heat exchanger|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    US201562258786P| true| 2015-11-23|2015-11-23|
    US62/258,786|2015-11-23|
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