US20210131752A1 - Heat exchanger and heat exchange system comprising the heat exchanger - Google Patents
Heat exchanger and heat exchange system comprising the heat exchanger Download PDFInfo
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- US20210131752A1 US20210131752A1 US17/086,912 US202017086912A US2021131752A1 US 20210131752 A1 US20210131752 A1 US 20210131752A1 US 202017086912 A US202017086912 A US 202017086912A US 2021131752 A1 US2021131752 A1 US 2021131752A1
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- Prior art keywords
- heat exchanger
- shell
- receiving portion
- heat exchange
- exchange tubes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
- F28D7/1638—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
- F28D7/1646—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one with particular pattern of flow of the heat exchange medium flowing outside the conduit assemblies, e.g. change of flow direction
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0243—Header boxes having a circular cross-section
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
- F28B9/08—Auxiliary systems, arrangements, or devices for collecting and removing condensate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
- F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
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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
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/007—Auxiliary supports for elements
- F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/007—Auxiliary supports for elements
- F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
- F28F9/0131—Auxiliary supports for elements for tubes or tube-assemblies formed by plates
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
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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
- F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
- F28D2021/0063—Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/007—Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
- F28D7/1653—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
- F28D7/1661—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape with particular pattern of flow of the heat exchange media, e.g. change of flow direction
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
- F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
- F28F2009/224—Longitudinal partitions
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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
- F28F2210/00—Heat exchange conduits
- F28F2210/10—Particular layout, e.g. for uniform temperature distribution
Definitions
- the present disclosure relates to the technical field of heat exchange, and more particularly to a heat exchanger and a heat exchange system comprising the heat exchanger.
- the present disclosure provides a heat exchanger and a heat exchange system comprising the heat exchanger, thereby resolving or at least alleviating one or more of the problems described above as well as problems of other aspects existing in the prior art.
- a heat exchanger which comprises a shell and heat exchange tubes located in the shell, wherein the heat exchanger further comprises a flow guide device, which is disposed in the shell and comprises a receiving portion arranged between two adjacent rows of heat exchange tubes and extending substantially horizontally along a length direction of the shell for receiving liquid, and a guiding portion arranged to guide the liquid received by the receiving portion to a bottom inside the shell.
- the receiving portion comprises a first portion and a second portion that are at the same height or different heights in a height direction of the shell, and the guiding portion is arranged to be located between the first portion and the second portion and face a guiding groove at the bottom inside the shell.
- At least a part of the receiving portion is configured to have a contour that urges the liquid to flow toward the guiding portion.
- the receiving portion is configured such that an end portion on at least one side thereof is higher than a middle part of the receiving portion in a height direction of the shell, a gas flow channel is formed between the end portion and an inner wall of the shell, and the guiding portion is connected to the receiving portion and arranged in the middle part of the receiving portion.
- the receiving portion is arranged such that the number of heat exchange tubes located above the receiving portion is not larger than the number of heat exchange tubes located below the receiving portion.
- the receiving portion is arranged to be at a first preset distance from the nearest row of heat exchange tubes located above the receiving portion and at a second preset distance from the nearest row of heat exchange tubes located below the receiving portion, the second preset distance being not smaller than the first preset distance.
- the receiving portion is arranged to extend to tube plates at both ends of the heat exchanger.
- the heat exchanger further comprises: a support member arranged in the shell for supporting at least part of the heat exchange tubes; and/or a superheated gas diffuser arranged above the heat exchange tubes for guiding fluid entering from an inlet of the heat exchanger to diverge from both sides of the superheated gas diffuser; and/or a supercooling chamber arranged inside the shell and communicating with an outlet of the heat exchanger, wherein the liquid at the bottom inside the shell enters the supercooling chamber through an opening at the bottom of the supercooling chamber.
- the heat exchanger is provided with at least two support members and the flow guide device is arranged at least between two adjacent support members.
- a heat exchange system which comprises any one of the heat exchangers described above.
- the technical solutions of the present disclosure are easy to manufacture, install and maintain, and have a low cost of use. They can overcome the adverse effects caused by the inundation effect of the tube bundle, save consumables such as heat exchange tubes, and effectively ensure and improve work performance, safety and reliability of the system.
- the present disclosure has significant practicability.
- FIG. 1 is a schematic view of the internal three-dimensional structure of an embodiment of a heat exchanger according to the present disclosure after a shell is removed, in which some parts such as heat exchange tubes are omitted.
- FIG. 2 is a schematic side sectional view of the heat exchanger according to the embodiment shown in FIG. 1 .
- FIG. 3 is a comparative explanatory view, in which “tube bundle inundation effect” in a condenser is schematically demonstrated by experimental test data, and the dashed line in the figure schematically shows an improvement of the tube outside heat transfer coefficient of the heat exchange tubes at the bottom after the embodiment of the heat exchanger of the present disclosure is applied.
- the technical term “substantially” is intended to include non-substantive errors associated with the measurement of a specific quantity (e.g., it may include a range of ⁇ 8 %, ⁇ 5 % or ⁇ 2 % of a given value).
- the technical terms “upper”, “lower”, “top”, “bottom”, “inner”, “outer” and their derivatives should be associated with the orientations in the drawings. The present disclosure may take various alternative orientations, unless otherwise clearly indicated.
- FIGS. 1 and 2 an embodiment of a heat exchanger according to the present disclosure is schematically shown, which can be used as a heat exchange device such as a shell-and-tube type condenser in a heat exchange system according to application requirements.
- the heat exchanger 100 may include a shell 1 , a flow guide device 10 , heat exchange tubes 20 , support members 30 , and a superheated gas diffuser 40 .
- the heat exchange tubes 20 are arranged inside the shell 1 . Heat energy transfer is achieved through heat exchange between a first fluid (such as liquid, gas or a mixture thereof) flowing inside these heat exchange tubes 20 and a second fluid (such as liquid, gas or a mixture thereof) flowing into an inner space of the shell 1 from an inlet 2 at the top of the heat exchanger 100 and flowing out of an outlet 3 at the bottom of the heat exchanger 100 .
- a first fluid such as liquid, gas or a mixture thereof
- a second fluid such as liquid, gas or a mixture thereof
- the specific number, installation layout, structural dimensions and the like of the heat exchange tubes 20 inside the shell 1 may be set or adjusted according to specific requirements.
- these heat exchange tubes 20 may be stacked to form a tube bundle array of two, three or more rows, wherein the numbers of heat exchange tubes 20 in different rows may be the same or different from each other.
- the second fluid As shown in FIG. 2 , for the above-mentioned second fluid, it will enter the interior of the heat exchanger 100 via the inlet 2 along the direction indicated by arrow A. Since the superheated gas diffuser 40 (which may, for example, take the form of a baffle or the like) is disposed near the inlet 2 and located above the heat exchange tubes 20 , the second fluid will be blocked by the superheated gas diffuser 40 at this position. Therefore, the second fluid will flow downward from both sides of the superheated gas diffuser 40 respectively in the directions indicated by the arrows drawn on both sides of the superheated gas diffuser 40 as shown in FIG.
- the superheated gas diffuser 40 which may, for example, take the form of a baffle or the like
- the second fluid may directly condense on outer surfaces of at least part of the heat exchange tubes 20 to form a liquid (which, in many cases, may exist in the form of “liquid droplets”).
- the condensed liquid will increase with the operating time of the system, and will drip to the bottom of the shell 1 and accumulate more and more, so that the heat exchange tubes 20 near the bottom will be affected by the condensed liquid to produce the so-called “tube bundle inundation effect”.
- the outer surfaces of some heat exchange tubes 20 are even completely wrapped by the condensed liquid, which makes the surface heat transfer coefficient of these heat exchange tubes 20 seriously decrease, resulting in a significant decrease in the heat exchange efficiency and working performance of the system.
- the flow guide device 10 is arranged inside the shell 1 , and it may be provided with a receiving portion 11 and a guiding portion 12 .
- the receiving portion 11 and the guiding portion 12 may be connected, but they may not be connected.
- the guiding portion 12 may be directly arranged below the receiving portion 11 and fixed to the shell 1 or other components in the shell 1 , as long as it is ensured that the guiding portion 12 can guide the liquid received by the receiving portion 11 to the bottom 14 of the shell 1 .
- the installation position of the receiving portion 11 may be set between any two adjacent rows of heat exchange tubes 20 .
- the receiving portion 11 will extend substantially horizontally along the length direction L of the shell 1 (for example, optionally, it extends in the shell 1 all the way to tube plates 50 at both ends of the heat exchanger 100 ) to receive the above-mentioned condensed liquid.
- the liquid received by the receiving portion 11 will then be guided to the bottom 14 of the shell 1 through the guiding portion 12 , so that the adverse effects caused by the lower half of the heat exchange tubes 20 due to the existence of the “tube bundle inundation effect” can be effectively reduced.
- a supercooling chamber 13 can also be provided in the shell 1 , and heat exchange tubes are also provided in the supercooling chamber 13 .
- the supercooling chamber 13 is also in communication with the outlet 3 of the heat exchanger, and the liquid entering the supercooling chamber 13 can be discharged to the outside through the outlet 3 .
- the liquid located at the bottom 14 can enter the supercooling chamber 13 through, for example, one or more openings 15 provided at the bottom of the supercooling chamber 13 , and then can exchange heat with the first fluid in the heat exchange tubes 20 in the supercooling chamber 13 to generate subcooling, which can increase the cooling capacity.
- the supercooling chamber 13 may be configured into any suitable shape to meet various possible needs; for example, structural configuration such as rectangular parallelepiped, cube, cylinder, ellipsoid, or an irregular structure may be used.
- the present disclosure also allows the supercooling chamber 13 to be arranged at any suitable position inside the shell 1 , such as on a directly lower side, a lower left side, or a lower right side of the interior of the shell 1 .
- the supercooling chamber 13 may be arranged to be partially or completely located in an array space formed by the heat exchange tubes 20 , so that the space can be fully utilized to for example overcome the problems caused by the above “tube bundle inundation effect”.
- the above arrangement is schematically shown in FIG. 2 .
- the supercooling chamber 13 and the receiving portion 11 may be set to have the same length or different lengths in the length direction L of the heat exchanger 100 .
- the corresponding length of the supercooling chamber 13 may be set to be smaller than the corresponding length of the receiving portion 11 .
- the receiving portion 11 of the flow guide device 10 is optionally configured to have a first portion 111 and a second portion 112 , and the guiding portion 12 is disposed between the first portion 111 and the second portion 112 to form a guiding groove for guiding the liquids received by the first portion 111 and the second portion 112 respectively to the bottom 14 of the shell 1 .
- the flow guide device 10 adopts a completely symmetrical or substantially symmetrical structural arrangement in the shell 1 , that is, the first portion 111 and the second portion 112 are based on the same or substantially the same structure in this situation. They are also at the same height in the height direction H of the shell 1 .
- the first portion 111 and the second portion 112 may not only have different structures, but they may also be at different heights in the height direction H; for example, one is arranged at a higher position than the other. In some applications, possibly, this is to meet considerations such as the array arrangement of the heat exchange tubes 20 , etc., so it can bring about more advantageous technical effects.
- the receiving portion 11 may be partially or entirely configured to have a contour that can urge the liquid that has been received by the receiving portion 11 to flow toward the guiding portion 12 more easily, while simultaneously avoiding outward leakage and overflow of the received liquid from the side of the receiving portion 11 .
- the above-mentioned contour may be of any feasible shape such as a curved arc surface or an inclined surface (such as forming a bent structure) inclined toward the guiding portion 12 .
- one side end or both side ends of the receiving portion 11 may be set to be higher than the middle part of the receiving portion 11 in the height direction H, so as to urge the fluid to flow more easily into the guiding portion 12 arranged below the middle part of the receiving portion 11 in this situation.
- the receiving portion 11 may be arranged to form a gas flow channel between its two side ends and the inner wall of the shell 1 , and the guiding portion 12 located in the middle forms a liquid flow channel, so that the receiving portion 11 and the guiding portion 12 form gas and liquid flow channels that are clearly separated.
- the receiving portion 11 is arranged such that the number of heat exchange tubes 20 located above the receiving portion 11 is not larger than the number of heat exchange tubes 20 located below the receiving portion 11 , which can be determined based on application requirements.
- the receiving portion 11 may be arranged to be at a preset distance Si from the nearest row of heat exchange tubes 20 located above it and at another preset distance S 2 from the nearest row of heat exchange tubes 20 located below it.
- the preset distance S 2 may be optionally set to be not smaller than the preset distance S 1 .
- FIG. 1 Although the solutions of the present disclosure have been discussed above in detail in combination with the embodiment shown in FIG. 1 and FIG. 2 , it should be understood that many modifications, adjustments or replacements to the solutions of the present disclosure are allowed in practical applications.
- several support members 30 are simultaneously provided inside the shell 1 of the heat exchanger 100 shown in FIG. 1 , and components such as some or all of the heat exchange tubes 20 in the heat exchanger 100 can be supported and protected by these support members 30 .
- FIG. 1 For example, several support members 30 are simultaneously provided inside the shell 1 of the heat exchanger 100 shown in FIG. 1 , and components such as some or all of the heat exchange tubes 20 in the heat exchanger 100 can be supported and protected by these support members 30 .
- the flow guide device 10 can be optionally installed between two adjacent support members 30 ; of course, in some other embodiments, it is also possible to provide no support member 30 or only one support member 30 in the present disclosure, or in some other embodiments, it is also possible to remove the above-mentioned superheated gas diffuser 40 and/or the supercooling chamber 13 in the present disclosure, and the flow guide device 10 may be arranged inside the shell 1 of the heat exchanger 100 in an asymmetric manner.
- FIG. 3 provides a performance test comparison between an embodiment of the heat exchanger according to the present disclosure and a solution in the prior art.
- the abscissa represents the number of rows of heat exchange tubes arranged in the heat exchanger
- the ordinate represents a ratio of the tube outside heat transfer coefficient hro(N) of the Nth row of heat exchange tubes and an average tube outside heat transfer coefficient hro(5) of the first five rows of heat exchange tubes.
- the above average tube outside heat transfer coefficient hro(5) is used to ensure the accuracy, reliability and comparability of the test data.
- the same structural configuration was used during the test, and different heat exchange conditions (8 different heat exchange amounts of 900-2000 Ton) were implemented.
- the solid-line test data in FIG. 3 shows the “tube bundle inundation effect” occurring in existing condensers: the heat transfer coefficient of the tube bundle located at the lower part of the condenser will attenuate as the number of tube rows increases.
- the dashed line in FIG. 3 schematically shows that after the present disclosure is applied, the tube outside heat transfer coefficient of the heat exchange tubes located at the lower part of the heat exchanger can be effectively improved.
- a heat exchange system is also provided, and the heat exchange system can be provided with the heat exchanger designed and provided according to the present disclosure as illustrated above.
- the heat exchanger can be used as a heat exchange device such as a condenser in the heat exchange system, so as to better solve the problems such as the “tube bundle inundation effect” in the prior art and for example realize the prominent technical advantages of the above-discussed present disclosure that are significantly superior to the prior art.
Abstract
Description
- This application claims priority to Chinese Patent Application No. 201911076230.5, filed Nov. 6, 2019, and all the benefits accruing therefrom under 35 U.S.C. § 119, the contents of which in its entirety are herein incorporated by reference.
- The present disclosure relates to the technical field of heat exchange, and more particularly to a heat exchanger and a heat exchange system comprising the heat exchanger.
- Various types of heat exchange devices, apparatuses or systems have already emerged in the prior art, which have been widely used in many industrial fields, places, etc., and can bring great convenience. However, these existing heat exchange devices, apparatuses or systems still have some drawbacks and shortcomings in terms of structural configuration, heat exchange effect, work performance, manufacture, installation, maintenance and the like, and can be further improved and optimized. For example, when some centrifugal condensers are in operation, a tube bundle inundation effect may arise to cause a rapid decrease in the value of the tube outside heat transfer coefficient of the heat exchange tubes in the lower half of the condenser, thereby affecting the heat exchange efficiency and safe operation of the system. When the condenser shell has a large size and the number of tube rows is large, the above disadvantages will be more serious.
- In view of the foregoing, the present disclosure provides a heat exchanger and a heat exchange system comprising the heat exchanger, thereby resolving or at least alleviating one or more of the problems described above as well as problems of other aspects existing in the prior art.
- First, according to an aspect of the present disclosure, a heat exchanger is provided, which comprises a shell and heat exchange tubes located in the shell, wherein the heat exchanger further comprises a flow guide device, which is disposed in the shell and comprises a receiving portion arranged between two adjacent rows of heat exchange tubes and extending substantially horizontally along a length direction of the shell for receiving liquid, and a guiding portion arranged to guide the liquid received by the receiving portion to a bottom inside the shell.
- In the heat exchanger according to the present disclosure, optionally, the receiving portion comprises a first portion and a second portion that are at the same height or different heights in a height direction of the shell, and the guiding portion is arranged to be located between the first portion and the second portion and face a guiding groove at the bottom inside the shell.
- In the heat exchanger according to the present disclosure, optionally, at least a part of the receiving portion is configured to have a contour that urges the liquid to flow toward the guiding portion.
- In the heat exchanger according to the present disclosure, optionally, the receiving portion is configured such that an end portion on at least one side thereof is higher than a middle part of the receiving portion in a height direction of the shell, a gas flow channel is formed between the end portion and an inner wall of the shell, and the guiding portion is connected to the receiving portion and arranged in the middle part of the receiving portion.
- In the heat exchanger according to the present disclosure, optionally, the receiving portion is arranged such that the number of heat exchange tubes located above the receiving portion is not larger than the number of heat exchange tubes located below the receiving portion.
- In the heat exchanger according to the present disclosure, optionally, the receiving portion is arranged to be at a first preset distance from the nearest row of heat exchange tubes located above the receiving portion and at a second preset distance from the nearest row of heat exchange tubes located below the receiving portion, the second preset distance being not smaller than the first preset distance.
- In the heat exchanger according to the present disclosure, optionally, the receiving portion is arranged to extend to tube plates at both ends of the heat exchanger.
- In the heat exchanger according to the present disclosure, optionally, the heat exchanger further comprises: a support member arranged in the shell for supporting at least part of the heat exchange tubes; and/or a superheated gas diffuser arranged above the heat exchange tubes for guiding fluid entering from an inlet of the heat exchanger to diverge from both sides of the superheated gas diffuser; and/or a supercooling chamber arranged inside the shell and communicating with an outlet of the heat exchanger, wherein the liquid at the bottom inside the shell enters the supercooling chamber through an opening at the bottom of the supercooling chamber.
- In the heat exchanger according to the present disclosure, optionally, the heat exchanger is provided with at least two support members and the flow guide device is arranged at least between two adjacent support members.
- Second, according to another aspect of the present disclosure, a heat exchange system is also provided, which comprises any one of the heat exchangers described above.
- From the following detailed description combined with the accompanying drawings, the principles, features, characteristics and advantages of various technical solutions according to the present disclosure will be clearly understood. For example, as compared with the prior art, the technical solutions of the present disclosure are easy to manufacture, install and maintain, and have a low cost of use. They can overcome the adverse effects caused by the inundation effect of the tube bundle, save consumables such as heat exchange tubes, and effectively ensure and improve work performance, safety and reliability of the system. The present disclosure has significant practicability.
- The technical solutions of the present disclosure will be described in further detail below with reference to the accompanying drawings and embodiments. However, it should be understood that these drawings are designed merely for the purpose of explanation and only intended to conceptually illustrate the structural configurations described herein, and are not required to be drawn to scale.
-
FIG. 1 is a schematic view of the internal three-dimensional structure of an embodiment of a heat exchanger according to the present disclosure after a shell is removed, in which some parts such as heat exchange tubes are omitted. -
FIG. 2 is a schematic side sectional view of the heat exchanger according to the embodiment shown inFIG. 1 . -
FIG. 3 is a comparative explanatory view, in which “tube bundle inundation effect” in a condenser is schematically demonstrated by experimental test data, and the dashed line in the figure schematically shows an improvement of the tube outside heat transfer coefficient of the heat exchange tubes at the bottom after the embodiment of the heat exchanger of the present disclosure is applied. - First, it should be noted that the structural components, characteristics, advantages and the like of the heat exchanger and the heat exchange system comprising the heat exchanger according to the present disclosure will be specifically described below by way of example. However, it should be understood that all the descriptions are merely given for illustration, and should not be understood as limiting the present disclosure in any way. Herein, the technical terms “first” and “second” are merely used for distinguishing purpose, and are not intended to indicate their order and relative importance. The technical term “connect (or connected, etc.)” covers a situation where a specific component is directly connected to another component and/or indirectly connected to another component. The technical term “substantially” is intended to include non-substantive errors associated with the measurement of a specific quantity (e.g., it may include a range of ±8%, ±5% or ±2% of a given value). The technical terms “upper”, “lower”, “top”, “bottom”, “inner”, “outer” and their derivatives should be associated with the orientations in the drawings. The present disclosure may take various alternative orientations, unless otherwise clearly indicated.
- In addition, for any single technical feature described or implied in the embodiments mentioned herein, the present disclosure still allows for any combination or deletion of these technical features (or equivalents thereof), so that more other embodiments of the present disclosure that may not have been mentioned directly herein can be obtained. In addition, for the sake of simplification of the drawings, the same or similar parts and features may only be marked in one or several places in the same drawing.
- Reference is made to
FIGS. 1 and 2 in combination, an embodiment of a heat exchanger according to the present disclosure is schematically shown, which can be used as a heat exchange device such as a shell-and-tube type condenser in a heat exchange system according to application requirements. - As shown in
FIGS. 1 and 2 , theheat exchanger 100 may include a shell 1, aflow guide device 10,heat exchange tubes 20,support members 30, and a superheatedgas diffuser 40. Theheat exchange tubes 20 are arranged inside the shell 1. Heat energy transfer is achieved through heat exchange between a first fluid (such as liquid, gas or a mixture thereof) flowing inside theseheat exchange tubes 20 and a second fluid (such as liquid, gas or a mixture thereof) flowing into an inner space of the shell 1 from aninlet 2 at the top of theheat exchanger 100 and flowing out of anoutlet 3 at the bottom of theheat exchanger 100. In practical applications, the specific number, installation layout, structural dimensions and the like of theheat exchange tubes 20 inside the shell 1 may be set or adjusted according to specific requirements. For example, theseheat exchange tubes 20 may be stacked to form a tube bundle array of two, three or more rows, wherein the numbers ofheat exchange tubes 20 in different rows may be the same or different from each other. - Hereinafter, an exemplary description will be given in conjunction with the embodiment shown in the above drawings. As shown in
FIG. 2 , for the above-mentioned second fluid, it will enter the interior of theheat exchanger 100 via theinlet 2 along the direction indicated by arrow A. Since the superheated gas diffuser 40 (which may, for example, take the form of a baffle or the like) is disposed near theinlet 2 and located above theheat exchange tubes 20, the second fluid will be blocked by thesuperheated gas diffuser 40 at this position. Therefore, the second fluid will flow downward from both sides of thesuperheated gas diffuser 40 respectively in the directions indicated by the arrows drawn on both sides of thesuperheated gas diffuser 40 as shown inFIG. 2 , then each contact theheat exchange tubes 20 arranged in tube bundles under thesuperheated gas diffuser 40 to achieve heat energy exchange, and finally flows to the outside from theoutlet 3 of theheat exchanger 100. In the above heat energy exchange process, the second fluid may directly condense on outer surfaces of at least part of theheat exchange tubes 20 to form a liquid (which, in many cases, may exist in the form of “liquid droplets”). The condensed liquid will increase with the operating time of the system, and will drip to the bottom of the shell 1 and accumulate more and more, so that theheat exchange tubes 20 near the bottom will be affected by the condensed liquid to produce the so-called “tube bundle inundation effect”. For example, the outer surfaces of someheat exchange tubes 20 are even completely wrapped by the condensed liquid, which makes the surface heat transfer coefficient of theseheat exchange tubes 20 seriously decrease, resulting in a significant decrease in the heat exchange efficiency and working performance of the system. - In the
heat exchanger 100, the above problems can be effectively solved by providing theflow guide device 10. Specifically, as shown inFIGS. 1 and 2 , theflow guide device 10 is arranged inside the shell 1, and it may be provided with a receivingportion 11 and a guidingportion 12. Thereceiving portion 11 and the guidingportion 12 may be connected, but they may not be connected. For example, the guidingportion 12 may be directly arranged below thereceiving portion 11 and fixed to the shell 1 or other components in the shell 1, as long as it is ensured that the guidingportion 12 can guide the liquid received by thereceiving portion 11 to thebottom 14 of the shell 1. According to different application requirements, the installation position of the receivingportion 11 may be set between any two adjacent rows ofheat exchange tubes 20. Thereceiving portion 11 will extend substantially horizontally along the length direction L of the shell 1 (for example, optionally, it extends in the shell 1 all the way totube plates 50 at both ends of the heat exchanger 100) to receive the above-mentioned condensed liquid. The liquid received by the receivingportion 11 will then be guided to thebottom 14 of the shell 1 through the guidingportion 12, so that the adverse effects caused by the lower half of theheat exchange tubes 20 due to the existence of the “tube bundle inundation effect” can be effectively reduced. - In an optional situation, a
supercooling chamber 13 can also be provided in the shell 1, and heat exchange tubes are also provided in thesupercooling chamber 13. Thesupercooling chamber 13 is also in communication with theoutlet 3 of the heat exchanger, and the liquid entering thesupercooling chamber 13 can be discharged to the outside through theoutlet 3. The liquid located at thebottom 14 can enter thesupercooling chamber 13 through, for example, one ormore openings 15 provided at the bottom of thesupercooling chamber 13, and then can exchange heat with the first fluid in theheat exchange tubes 20 in thesupercooling chamber 13 to generate subcooling, which can increase the cooling capacity. In practical applications, thesupercooling chamber 13 may be configured into any suitable shape to meet various possible needs; for example, structural configuration such as rectangular parallelepiped, cube, cylinder, ellipsoid, or an irregular structure may be used. In addition, the present disclosure also allows thesupercooling chamber 13 to be arranged at any suitable position inside the shell 1, such as on a directly lower side, a lower left side, or a lower right side of the interior of the shell 1. As another example, in an optional situation, the supercoolingchamber 13 may be arranged to be partially or completely located in an array space formed by theheat exchange tubes 20, so that the space can be fully utilized to for example overcome the problems caused by the above “tube bundle inundation effect”. For example, the above arrangement is schematically shown inFIG. 2 . - In addition, the supercooling
chamber 13 and the receivingportion 11 may be set to have the same length or different lengths in the length direction L of theheat exchanger 100. For example, the corresponding length of the supercoolingchamber 13 may be set to be smaller than the corresponding length of the receivingportion 11. - With continued reference to
FIGS. 1 and 2 , in the embodiment given, the receivingportion 11 of theflow guide device 10 is optionally configured to have afirst portion 111 and asecond portion 112, and the guidingportion 12 is disposed between thefirst portion 111 and thesecond portion 112 to form a guiding groove for guiding the liquids received by thefirst portion 111 and thesecond portion 112 respectively to the bottom 14 of the shell 1. In the above-mentioned embodiment, theflow guide device 10 adopts a completely symmetrical or substantially symmetrical structural arrangement in the shell 1, that is, thefirst portion 111 and thesecond portion 112 are based on the same or substantially the same structure in this situation. They are also at the same height in the height direction H of the shell 1. However, it should be pointed out that in some embodiments, thefirst portion 111 and thesecond portion 112 may not only have different structures, but they may also be at different heights in the height direction H; for example, one is arranged at a higher position than the other. In some applications, possibly, this is to meet considerations such as the array arrangement of theheat exchange tubes 20, etc., so it can bring about more advantageous technical effects. - In addition, in an optional situation, the receiving
portion 11 may be partially or entirely configured to have a contour that can urge the liquid that has been received by the receivingportion 11 to flow toward the guidingportion 12 more easily, while simultaneously avoiding outward leakage and overflow of the received liquid from the side of the receivingportion 11. For example, the above-mentioned contour may be of any feasible shape such as a curved arc surface or an inclined surface (such as forming a bent structure) inclined toward the guidingportion 12. For another example, one side end or both side ends of the receivingportion 11 may be set to be higher than the middle part of the receivingportion 11 in the height direction H, so as to urge the fluid to flow more easily into the guidingportion 12 arranged below the middle part of the receivingportion 11 in this situation. In addition, the receivingportion 11 may be arranged to form a gas flow channel between its two side ends and the inner wall of the shell 1, and the guidingportion 12 located in the middle forms a liquid flow channel, so that the receivingportion 11 and the guidingportion 12 form gas and liquid flow channels that are clearly separated. - It should be noted that for the receiving
portion 11, optionally, it is arranged such that the number ofheat exchange tubes 20 located above the receivingportion 11 is not larger than the number ofheat exchange tubes 20 located below the receivingportion 11, which can be determined based on application requirements. In addition, as shown inFIG. 2 , the receivingportion 11 may be arranged to be at a preset distance Si from the nearest row ofheat exchange tubes 20 located above it and at another preset distance S2 from the nearest row ofheat exchange tubes 20 located below it. By setting the above two preset distances S1 and S2, the second fluid can be promoted to flow therebetween, thus avoiding the formation of undesired flow dead zones and helping ensure and improve heat exchange. Their specific design conditions may be flexibly set according to different application requirements. For example, the preset distance S2 may be optionally set to be not smaller than the preset distance S1. - Although the solutions of the present disclosure have been discussed above in detail in combination with the embodiment shown in
FIG. 1 andFIG. 2 , it should be understood that many modifications, adjustments or replacements to the solutions of the present disclosure are allowed in practical applications. For example,several support members 30 are simultaneously provided inside the shell 1 of theheat exchanger 100 shown inFIG. 1 , and components such as some or all of theheat exchange tubes 20 in theheat exchanger 100 can be supported and protected by thesesupport members 30.FIG. 1 also schematically shows that theflow guide device 10 can be optionally installed between twoadjacent support members 30; of course, in some other embodiments, it is also possible to provide nosupport member 30 or only onesupport member 30 in the present disclosure, or in some other embodiments, it is also possible to remove the above-mentionedsuperheated gas diffuser 40 and/or the supercoolingchamber 13 in the present disclosure, and theflow guide device 10 may be arranged inside the shell 1 of theheat exchanger 100 in an asymmetric manner. - As an exemplary illustration,
FIG. 3 provides a performance test comparison between an embodiment of the heat exchanger according to the present disclosure and a solution in the prior art. InFIG. 3 , the abscissa represents the number of rows of heat exchange tubes arranged in the heat exchanger, and the ordinate represents a ratio of the tube outside heat transfer coefficient hro(N) of the Nth row of heat exchange tubes and an average tube outside heat transfer coefficient hro(5) of the first five rows of heat exchange tubes. In the comparison test, the above average tube outside heat transfer coefficient hro(5) is used to ensure the accuracy, reliability and comparability of the test data. Except for the innovative setting of the flow guide device in the heat exchanger of the present disclosure, the same structural configuration was used during the test, and different heat exchange conditions (8 different heat exchange amounts of 900-2000 Ton) were implemented. First, the solid-line test data inFIG. 3 shows the “tube bundle inundation effect” occurring in existing condensers: the heat transfer coefficient of the tube bundle located at the lower part of the condenser will attenuate as the number of tube rows increases. Second, the dashed line inFIG. 3 schematically shows that after the present disclosure is applied, the tube outside heat transfer coefficient of the heat exchange tubes located at the lower part of the heat exchanger can be effectively improved. - It should be pointed out that according to the innovative design of the present disclosure, not only an improvement in the heat transfer performance outside the heat exchange tubes (especially, those at the lower part of the heat exchanger) can be brought about, but also due to the space occupied by the installation of the receiving
portion 11 and the guidingportion 12 in the flow guide device, some heat exchange tubes may be omitted. According to a practical application example, the present disclosure can save about 10% of the number of heat exchange tubes and the system can still have the same working performance. Since the heat exchange tubes are usually made of copper material with good heat transfer performance but relatively expensive price, the material saving effect brought by the solutions of the present disclosure can lead to considerable benefits. - According to another technical solution of the present disclosure, a heat exchange system is also provided, and the heat exchange system can be provided with the heat exchanger designed and provided according to the present disclosure as illustrated above. For example, the heat exchanger can be used as a heat exchange device such as a condenser in the heat exchange system, so as to better solve the problems such as the “tube bundle inundation effect” in the prior art and for example realize the prominent technical advantages of the above-discussed present disclosure that are significantly superior to the prior art.
- The heat exchanger and the heat exchange system comprising the heat exchanger according to the present disclosure have been elaborated above in detail by way of example only. These examples are merely used to illustrate the principles and embodiments of the present disclosure, rather than limiting the present disclosure. Various modifications and improvements can be made by those skilled in the art without departing from the spirit and scope of the present disclosure. Therefore, all equivalent technical solutions should fall within the scope of the present disclosure and be defined by the claims of the present disclosure.
Claims (10)
Applications Claiming Priority (2)
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CN201911076230.5A CN112762734A (en) | 2019-11-06 | 2019-11-06 | Heat exchanger and heat exchange system including the same |
CN201911076230.5 | 2019-11-06 |
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US20210131752A1 true US20210131752A1 (en) | 2021-05-06 |
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US17/086,912 Abandoned US20210131752A1 (en) | 2019-11-06 | 2020-11-02 | Heat exchanger and heat exchange system comprising the heat exchanger |
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US (1) | US20210131752A1 (en) |
EP (1) | EP3819563A1 (en) |
CN (1) | CN112762734A (en) |
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Publication number | Priority date | Publication date | Assignee | Title |
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JP3869095B2 (en) * | 1997-11-26 | 2007-01-17 | 株式会社東芝 | Water heater |
WO2009089100A1 (en) * | 2008-01-02 | 2009-07-16 | Johnson Controls Technology Company | Heat exchanger |
US20140034275A1 (en) * | 2011-04-21 | 2014-02-06 | Carrier Corporation | Condenser/Accumulator and Systems and Operation Methods |
US9658003B2 (en) * | 2013-07-11 | 2017-05-23 | Daikin Applied Americas Inc. | Heat exchanger |
-
2019
- 2019-11-06 CN CN201911076230.5A patent/CN112762734A/en active Pending
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2020
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CN112762734A (en) | 2021-05-07 |
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