EP4004474B1 - Échangeur de chaleur à faisceau tubulaire - Google Patents

Échangeur de chaleur à faisceau tubulaire Download PDF

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Publication number
EP4004474B1
EP4004474B1 EP20758111.7A EP20758111A EP4004474B1 EP 4004474 B1 EP4004474 B1 EP 4004474B1 EP 20758111 A EP20758111 A EP 20758111A EP 4004474 B1 EP4004474 B1 EP 4004474B1
Authority
EP
European Patent Office
Prior art keywords
tube
tubes
medium
inlet
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP20758111.7A
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German (de)
English (en)
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EP4004474A1 (fr
EP4004474C0 (fr
Inventor
Stefan Krolla
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kelvion Machine Cooling Systems GmbH
Original Assignee
Kelvion Machine Cooling Systems GmbH
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Publication of EP4004474A1 publication Critical patent/EP4004474A1/fr
Application granted granted Critical
Publication of EP4004474B1 publication Critical patent/EP4004474B1/fr
Publication of EP4004474C0 publication Critical patent/EP4004474C0/fr
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Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • 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
    • 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
    • F28D7/1607—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 particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • 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
    • F28F9/0229—Double end plates; Single end plates with hollow spaces
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
    • 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
    • F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications
    • 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
    • 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
    • F28D7/1669—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 an annular shape; the conduits being assembled around a central distribution tube

Definitions

  • the invention relates to a tube bundle heat exchanger with the features in the preamble of claim 1.
  • a tube bundle heat exchanger is from US-A-2986454 known.
  • a tube bundle heat exchanger can e.g. B. be configured so that a cryogenic medium flows into a lower cross-section half of a cylindrical heat exchanger, flows through the heat exchanger in the longitudinal direction, is deflected by 180° at the end of the cylindrical heat exchanger and flows back to the common tube sheet via a tube bundle in the upper half of the heat exchanger .
  • the result of the semi-circular tube fields of the tube sheet is that the lower half of the tube sheet has a correspondingly low temperature due to the cryogenic medium, while the second semi-circular tube field in the tube sheet is significantly warmer.
  • the direct flow of cryogenic media onto the tube sheet leads to stress peaks within the tube sheet. The This also applies to heat exchangers in which the medium is not deflected, i.e. in which the medium flows over the entire tube sheet.
  • the invention is based on the object of demonstrating a tube bundle heat exchanger in which the thermal load on the tube sheet, the tube connection to the tube bundle and the tube bundle is reduced.
  • the tube bundle heat exchanger has a tube bundle in a housing, the housing having a first inlet and a first outlet for a first medium to be passed through the tube bundle. Furthermore, the housing has a second inlet and a second outlet for a second medium for passage through a flow space surrounding the tube bundle within the housing.
  • the heat exchanger has tube sheets to hold the tubes and separate the two media.
  • a separating body is arranged as a flow distributor between the first inlet and the tube sheet.
  • the separating body has the function of preventing the first medium from flowing directly against the tube sheet. So that the first medium can nevertheless enter the tube bundle, inlet tubes are arranged on the separating body.
  • the inlet tubes bridge a compensating space between the separating body and the tube sheet and protrude into the individual tubes of the tube bundle.
  • the first medium is fed directly into the tubes by means of the individual tubes, bypassing the tube sheet.
  • the tube sheet is not flowed directly against.
  • the separating body that is directly subjected to the flow is cooled down considerably, in particular when it is being flowed on, by a cryogenic medium, which, according to the invention, has no effect on the thermal stresses in the tube sheet, because the tube sheet is decoupled from the separating body.
  • the tube sheet is just above the housing with connected to the separator. The tube sheet, the tube connections and also the tubes are significantly relieved.
  • the individual inlet tubes are not firmly connected to the tubes of the tube bundle. This compensates for thermal changes in length between the inlet tubes and the tubes of the tube bundle.
  • the separating body is used for thermal decoupling from the tube sheet.
  • Shell and tube heat exchangers in which the inlet and outlet are located at one end of the housing, while a deflection chamber is arranged at the other end of the housing, have greater thermally induced stresses within the tube sheet due to the design.
  • the temperature gradient in the tube sheet is greater.
  • the temperature of a cryogenic medium could be -160°C at the first inlet and +50°C at the first outlet. In this case, the temperature difference within the tube sheet is over 200 °C.
  • the tube sheet is not divided into an upper and lower half.
  • the first inlet is connected to a first group of tubes of the tube bundle that is adjacent to a second group of tubes.
  • the first group has an outer envelope surface which is predominantly, i.e. more than 50%, adjacent to an envelope surface of the second group.
  • the second group can enclose or surround the first group over more than 180° and in particular completely enclose it.
  • the second group of tubes is then arranged essentially annularly around the first group of tubes. In other words, one can also speak of a core area and an edge area. The areas are not necessarily strictly concentric.
  • a distinction can essentially be made between an inner group and an outer group of tubes, with the second group being the outer group having a larger proportion of tubes which are adjacent to the housing than the first, inner group.
  • the first medium Via a deflection at the end or a deflection chamber, the first medium first flows through the first group and, after deflection, back through the second group. Both groups of tubes are also connected to a common tube sheet.
  • Temperature gradient compared to semi-circular tube arrays. In a cryogenic medium, much lower temperatures prevail in the core area than in the edge area to the transition of the housing. The temperature gradient runs in a star shape between the core area and the outer areas.
  • the tube sheet is significantly shielded in the arrangement of the groups of tubes according to the invention and is therefore exposed to significantly lower thermally induced stresses than in the case of an arrangement with semi-circular tube patterns. This is particularly advantageous when using cryogenic gases or liquid nitrogen, because voltage peaks are capped. A radial temperature gradient, rather than a temperature gradient running from the edge to across the center, also results in a more favorable stress distribution within the tube bundle.
  • Another advantage is that due to the fact that there is no need for separating fixtures within the heat exchanger (inlet) chamber, an approx. 20% larger number of tubes with the same nominal diameter can be installed within the tube sheet or the cylindrical housing.
  • the required wall thicknesses for high-pressure applications are significantly reduced due to smaller nominal diameters. Analogously, this means a reduction in the shell diameter of the heat exchanger with the same number of tubes. As a result, the mass and the manufacturing costs can be reduced.
  • the inlet tubes extend over at least half the thickness of the tube sheet.
  • the thickness is measured between an upstream and a downstream side of the tubesheet with respect to the flow direction of the first medium.
  • the inlet tubes preferably penetrate the tube sheet completely, so that the first medium, e.g. B. a cryogenic medium with a very low temperature, is introduced remote from a point of attachment of the tubes in the tube sheet.
  • the tubes can be welded to the tubesheet. Due to better accessibility, the tubes are welded to the tube sheet from the inflow side. By the inlet pipes bridge this inflow-side connection points of the pipes and In particular, if the cryogenic medium is fed deep into the tubes of the tube sheet, the connection points between the tubes and the tube sheet are additionally relieved.
  • the tube bundle heat exchanger is designed as a double-tube safety heat exchanger.
  • the tubes carrying the first medium are each arranged in an outer tube.
  • the second medium only comes into contact with the outer tube.
  • the first medium only comes into contact with the inner tube.
  • the outer tubes are fixed in a tube sheet for the outer tubes. It is located on the downstream side of the tubesheet for the inner tubes.
  • the tubesheets are spaced apart so that there is a common leak space that can be monitored, which is connected to all spaces between the inner and outer tubes. This leakage space can also be used as a test space to monitor the pressure of a test medium in the leakage space.
  • a further separating body which serves as a flow collector and which, viewed in the direction of flow of the first medium, is arranged behind an outlet-side tube sheet and in front of the first outlet.
  • This design relates to a tube bundle heat exchanger in which the first inlet is located at one end of a particular cylindrical housing and the first outlet at the opposite end of the cylindrical housing. In this design, the first medium is therefore not deflected in a collection chamber at the end.
  • a separating body can also be useful when flowing out of such a tube bundle heat exchanger in order to reduce stress peaks on the tube base.
  • the separating body has discharge tubes which are connected in a fluid-conducting manner to the tubes carrying the first medium, in order to conduct the first medium through the tube sheet on the outlet side and the separating body to the first outlet.
  • it is a mirror image arrangement to the configuration on the inlet side of the shell and tube heat exchanger. In this sense, both ends of the tube bundle heat exchanger can be configured identically.
  • a collecting chamber is arranged in front of the tube plate on the inlet side.
  • the second group of tubes opens into this collection chamber.
  • the first outlet is connected to the collection chamber.
  • the collection chamber is essentially ring-shaped. It can be delimited in a fluid-tight manner from the compensation chamber.
  • the collection chamber is preferably connected to the compensation chamber in a fluid-conducting manner.
  • the compensating space preferably serves not only to compensate for thermal changes in length between the separating body and the tube sheet, but also to absorb leaks that result from the fact that the inlet tubes are preferably arranged to be longitudinally displaceable in the tubes of the tube bundle.
  • the compensating space is at the same time part of the collection chamber for the medium flowing back.
  • the leakage currents are usually so small that they can be neglected.
  • Sealing means can be arranged between the inlet tubes and the tubes of the tube bundle.
  • the inlet pipes completely pass through the separating body and are connected to the separating body on the inlet side.
  • the separating body is an independent component that is preferably welded into the housing.
  • the inlet pipes are in turn connected to the separating body, specifically preferably on the inflow side, ie on their side facing the first inlet. For example, they are connected to the separating body in a materially bonded manner.
  • the manufacture is comparable to the manufacture of a tube bundle that is connected to a tube sheet.
  • the separating body can be designed as a disk-shaped body, similar to a tube plate Having a plurality of openings into which the inlet tubes are inserted. The same applies to the structure of a separating body serving as a flow collector, which is mounted on the outlet side in a tube bundle through which flow occurs unidirectionally in the longitudinal direction.
  • the invention allows the first inlet to be directly opposite the separating body when required.
  • the direct flow against the separating body is harmless for the thermal stresses within the tube bundle heat exchanger and in particular within the tube bundle due to the indirect flow of the tube sheet or tube bundle in this sense.
  • the invention does not rule out that the inlet is arranged at an angle deviating from 180° to the separating body, so that the inflowing first medium is deflected.
  • the inlet opens into an inflow chamber. It can be expanded in the shape of a funnel as required.
  • the cross section of the inlet does not have to correspond to the cross section of the tube bundle or that of the separator.
  • the purpose of the inflow chamber is to distribute the inflowing medium evenly to all openings in the separating body or the individual inlet tubes and thus evenly to the tube bundle.
  • the figure 1 shows a tube bundle heat exchanger 1 to the prior art. Based on this tube bundle heat exchanger 1, the essential components are named, which are also in the following designs according to the invention figure 5 find again.
  • the tube bundle heat exchanger 1 has a housing 2.
  • the housing 2 is cylindrical.
  • the housing 2 has a first inlet 3 on the left in the image plane and a first outlet 4 on the right in the image plane for a first medium M1 which flows into the first inlet 3 and flows out of the first outlet 4 .
  • the first medium M1 is passed through a tube bundle 5 . Only a single tube 6 of the tube bundle 5 is shown for better illustration.
  • the tube bundle is surrounded by a flow space 7 for a second medium M2.
  • the second medium M2 flows in the image plane on the right via a second inlet 8 through the flow chamber 7 to the second outlet 9 at the other end of the housing 2.
  • the second medium M2 is deflected several times within the housing 2.
  • baffle plates 10 are arranged in the housing 2 so that the flow path of the second medium M2 is lengthened.
  • the second medium M2 does not come into contact with the first medium M1.
  • the tubes 6 of the tube bundle 5 are fastened in tube sheets 11 at the first inlet and on a tube sheet 12 at the first outlet 4 .
  • the tube bundle heat exchanger is designed as a double-tube safety heat exchanger.
  • each tube 6 is surrounded by an outer tube, which is connected in a second tube sheet 13 at the first inlet 3 or in a second tube sheet 14 at the first outlet 4 .
  • the space between the tube sheets 11, 13 or 12, 14 can be monitored for leak detection.
  • the tube sheets 11, 13 or 12, 14 are at a small distance from one another.
  • the figure 2 shows a shell and tube heat exchanger 15.
  • the tube bundle heat exchanger 15 has a cylindrical housing 2 with a first inlet 3 for the first medium M1.
  • a tube bundle 5 runs through a flow space 7 for a second medium, not shown in detail, which is fed via the figure 1 illustrated second inlet 8 or second outlet 9 can flow into and out of the housing 2.
  • the tubes 6 of the tube bundle 5 are fastened in a tube sheet 11 .
  • the separating body 16 is configured in a disk shape and has a plurality of through openings in which the inlet pipes 18 run.
  • the inlet pipes 18 are arranged in alignment with the pipes 6 so that in each case one inlet pipe 18 is aligned opposite the pipe 6 of the pipe bundle 5 in the axial direction.
  • the inlet pipes 18 all have the same length. They extend through the separating body 16 and bridge a gap-shaped compensation space 19 in front of the tube sheet 11. They extend to a downstream side 20 of the tube sheet 11 and thus also pass through the entire tube sheet 11.
  • the medium M1 flows through the one first inlet into the inflow chamber 17, only the separating body 16 or the inlet pipes 18 arranged therein are impinged directly.
  • the tube sheet 11 is not flowed directly against.
  • the medium M1 only enters the tube bundle 5 on the downstream side of the tube sheet 11 .
  • the inlet pipes 18 can be shifted in length relative to the pipes 6 of the pipe bundle 5 . Any leakage currents are collected in the compensating space 19 . They cannot escape here because the compensating space 19 is limited on the one hand by the separating body 16 and on the peripheral side by the head piece 35 .
  • the first medium M1 can only flow into the tubes 6 of the tube bundle 5 .
  • the figure 2 shows that the tubes 6 of the tube bundle 5 are fixed on an upstream side 21 of the tube sheet 11, in particular by welding.
  • the inlet pipes 18 are also fixed on the inlet side to a front side 22 of the separating body 16 facing the first medium M1.
  • the shape of the figure 3 differs from that of figure 2 characterized in that the tube bundle heat exchanger 23 is designed as a double tube safety heat exchanger.
  • the design of the figure 3 for each tube 6 carrying the medium M1 there is an outer tube 24 that is installed in the tube sheet 13 on the inlet side (see figure 1 ) is attached. Between the outer tube 24 and the respective inner tube 6 there is a monitorable leakage space. Due to the fact that the tube sheet 13 for the outer tubes 24 is arranged at a small distance from the tube sheet 11 for the tubes 6 of the tube bundle 5, leakage monitoring can be carried out via the intermediate space 25 between the tube sheets 11, 13. For this purpose, the intermediate space 25 is connected to the leakage space between the tube 6 for the medium M1 and the outer tube 24 . Leakage monitoring is not shown.
  • the inlet tubes 18 also extend through the second tube sheet 13 for the outer tubes 24. Accordingly, the inlet tubes 18 end on the downstream side 26 of the second tube sheet 13. All other structural features are identical to the exemplary embodiment in FIG figure 2 .
  • the figure 4 shows another tube bundle heat exchanger 27 for the prior art.
  • the main difference compared to the shell and tube heat exchanger figure 1 is that the shell-and-tube heat exchanger 27 has a deflection chamber 28 in the image plane on the right, with the first inlet 3 and the first outlet 4 for the first medium M1 being arranged on the left in the image plane.
  • the housing 2 is cylindrical. Accordingly, a circular tube pattern results here in the tube plate 11.
  • the tube bundle heat exchanger 27 is in turn designed as a double-tube safety heat exchanger, so that there is also a second tube plate 13 for the outer tubes, which are not shown in detail.
  • the second medium M2 flows in via the first inlet 8 .
  • the first outlet 4 is arranged adjacent to the first inlet 8 . Only the first inlet 3 is arranged at a distance from the second outlet 9 .
  • a separating plate 30 is located in a chamber 29 at the inlet-side end in the image plane on the left, in order to separate the medium M1 flowing in from below from the medium M1 flowing out above.
  • an additional separating body 16 can be provided, as in the exemplary embodiments of FIG figures 5 and 7 is shown.
  • the separating body 16 does not differ from that of the embodiment of FIG figures 2 and 3 .
  • the tube sheet 11 is also configured identically.
  • the header 32 is configured differently.
  • the medium M1 flows into the head piece 32 via the first inlet 3 and then flows through the inflow chamber 17 in order to enter the individual inlet pipes 18 in the separating body 16 .
  • the medium M1 now flows into the tubes 6 of the tube bundle 5 .
  • the medium M1 only flows into a first group G1 of tubes 6 .
  • the tubes 6 of the first group G1 open into a deflection chamber as shown in figure 4 denoted by the reference numeral 28.
  • a tube sheet 12 is also arranged there, so that the first medium M1 flows out of the core area and is conducted into those tubes 6 which surround the first group G1 of tubes 6 .
  • This second group G2 is located radially outside the first group G1. As far as possible, this second group G2 surrounds the first group G1, so to speak, on the circumference.
  • the figure 6 shows an example of a tube array looking at the end face of a tube plate 11.
  • the first group G1 of tubes 6 is marked with an X.
  • the first medium M1 flows into these tubes 6 into the image plane. It is deflected behind the second tube sheet 12 and flows back via the tubes 6 of the second group G2.
  • These tubes 6 are marked with a dot in the middle.
  • the dot indicates the opposite direction of flow Die figure 6 also shows an enveloping surface 37 of the first group G1.
  • the enveloping surface 37 surrounds the first group G1 of tubes 6. It is drawn in with a broken line. It is not physically present, but simply designates a boundary between the first group G1 and the second group G2.
  • the inner envelope surface of the second group G2 corresponds to the outer envelope surface 37 of the inner group G1. They lie congruently on top of each other. The two enveloping surfaces are therefore not only partially adjacent, rather the enveloping surface of the second group G2 surrounds the enveloping surface 37 of the first group G1.
  • the returning medium M2 flows out of the tubes 6 of the second group G2 into a collection chamber 33.
  • This collection chamber 33 is configured in the shape of a ring. All tubes 6 of the outer or second group G2 open into the collection chamber 33.
  • the collection chamber 33 in the head piece 32 is connected to the first outlet 4 for the medium. In this case, the first outlet is at the top of the image plane. A partition as in the embodiment of figure 4 not necessary.
  • the separating body 16 separates the medium M1 flowing back from the medium flowing in.
  • the separating body 16 is located for the most part within the collection chamber 33 and is surrounded by the medium M1 flowing back in the collection chamber 33 .
  • the compensation space 19 is thus also located within the collection chamber 33.
  • the compensation space 19 is connected to the collection chamber 33 in a fluid-conducting manner. So that any leakage flows can pass from the compensation chamber 19 into the collection chamber 33 and can also flow out via the first outlet 4 for the first medium M1.
  • figure 7 differs from that of figure 5 solely because a second tube sheet 13 has been installed, which is connected to corresponding outer tubes 24 .
  • the description is too figure 5 and the reference numerals introduced there or to the previous description of the figure 3 referenced, which also shows the design as a double-tube safety heat exchanger.
  • the tube bundle heat exchanger 34 according to figure 7 is a combination of the design of the figures 5 and 3 .
  • the figure 8 shows another embodiment with a differently designed head piece 36.
  • the first inlet 3 is not directly opposite the separating body 16.
  • the first inlet 3 is located off-centre at the end and essentially in the lower half of the head piece 36.
  • the first inlet 3 leads via a feed line into the inflow chamber 17.
  • the inflow chamber 17 is not arranged centrally in the head piece 36, but rather eccentrically. It is mainly located in the lower half of the head piece 36. In contrast to the other exemplary embodiments, it is also not funnel-shaped, but in this sectional view rectangular and essentially to the tube pattern of the tube sheet in figure 9 adjusted.
  • the figure 9 shows the head piece 36 in a view of the inflow chamber 17 from the viewing direction of the tube bundle.
  • the inflow chamber 17 is essentially configured in a semicircular or semicylindrical manner with rounded corners when viewed from this direction.
  • the access to the first inlet 3 is located in the lower area of the inflow chamber 17.
  • the collection chamber 33 is essentially circular and surrounds the inflow chamber 17 on the circumference.
  • the figure 10 shows a detailed representation of the separating body 16. He is in the inflow chamber 17 of figure 9 deployed. The assembly situation is in the figure 8 shown. In the installed position, the separating body 16 is welded to the inflow chamber 17 on the peripheral side in a fluid-tight manner and closes it off from the collecting space 33. The inlet pipes 18 are inserted into the individual through-openings 38 in the separating body 16, as in FIG figure 8 can be seen.
  • the drilling pattern of the through openings 38 in the separating body 16 corresponds to the hole pattern in the tube sheet 11 according to FIG figure 11 .
  • the tubes 6 marked with X denote the tubes of the first group G1.
  • the figure 11 shows an envelope surface 37 as a boundary between the first group G1 and the second group G2.
  • the inner envelope surface of the second group G2 is identical to the outer envelope surface 37 of the first group G1.
  • the difference to the embodiment of figure 6 consists in the fact that the first group G1 is offset relative to the second group G2 towards the underside of the image plane 11 .
  • this arrangement of the tubes 6 or the placement of the groups G1, G2 can be advantageous.
  • the first group G1 of tubes 6 is predominantly in the lower half of the tube sheet 11.
  • This exemplary embodiment makes it clear that the two groups G1, G2 of tubes 6 do not have to be arranged concentrically, but at least on the predominant peripheral area of the first group G1 Tubes 6 of the second group G2 are arranged. It shouldn't for reasons of space be possible to arrange lateral tubes 6 of the second group G2 next to the tubes 6 of the first group G1, as is the case for example in the horizontal plane, these positions in the tube sheet 11 remain free.
  • the distance between the tubes 6 of the first group G1 and the edge of the tube sheet 11, or the distance from the inside of the enclosing housing 2 is greater than the distance between the outer tubes 6 of the second group G2 and the housing 2.
  • the two bottom pipes are still assigned to group G1, ie to be used as inflow pipes.
  • group G1 three sides and thus the majority of the tubes 6 of the first group G1 would be surrounded on the outside by the second group G2 in relation to their common enveloping surface.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (9)

  1. Échangeur de chaleur à faisceau tubulaire avec un faisceau tubulaire (5) dans un boîtier (2), dans lequel le boîtier (2) présente une première entrée (3) et une première sortie (4) pour un premier milieu (M1) pour le passage à travers le faisceau tubulaire (5) et une seconde entrée (8) ainsi qu'une seconde sortie (9) pour un second milieu (M2) pour le passage à travers un espace d'écoulement (7) entourant le faisceau tubulaire (5) à l'intérieur du boîtier (2), dans lequel les extrémités des faisceaux tubulaires (5) sont agencées dans une plaque tubulaire (11) qui sépare l'espace d'écoulement (7) pour le second milieu (M2) du premier milieu (M1), dans lequel un corps de séparation (16) est agencé entre la première entrée (3) et la plaque tubulaire (11) comme distributeur d'écoulement qui empêche un afflux de la plaque tubulaire (11) par le premier milieu (M1) et qui présente des tubes d'introduction (18) qui pontent un espace d'équilibrage (19) entre le corps de séparation (16) et la plaque tubulaire (11) et qui pénètrent dans les tubes (6) individuels du faisceau tubulaire (5) afin de guider le premier milieu (M1) en contournant la plaque tubulaire (11) dans les tubes (6), caractérisé en ce que la première entrée (3) est raccordée à un premier groupe (G1) de tubes (6) du faisceau tubulaire (5), dans lequel le premier groupe (G1) possède une surface enveloppe (37) extérieure qui est contiguë principalement à une surface enveloppe d'un second groupe (G2) de tubes (6) qui est relié de manière à acheminer un fluide au premier groupe (G1) de tubes (6) et dans lequel la première sortie (4) est raccordée au second groupe (G2) de tubes (6).
  2. Échangeur de chaleur à faisceau tubulaire selon la revendication 1, caractérisé en ce que les tubes d'introduction (18) s'étendent sur au moins la moitié d'une épaisseur de la plaque tubulaire (11), dans lequel l'épaisseur est mesurée entre un côté amont et un côté aval (20) de la plaque tubulaire (11), par rapport au sens d'écoulement du premier milieu (M1).
  3. Échangeur de chaleur à faisceau tubulaire selon la revendication 1 ou 2, caractérisé en ce qu'il est réalisé comme échangeur de chaleur de sécurité à double tube, pour lequel les tubes (6) guidant le premier milieu (M1) sont agencés respectivement dans un tube extérieur (24) de sorte qu'un espace de fuite surveillable soit agencé entre le tube intérieur (6) et le tube extérieur (24), dans lequel une plaque tubulaire (13) pour les tubes extérieurs (24) est agencée sur le côté aval (20) de la plaque tubulaire (11) pour les tubes (6) guidant le premier milieu (M1).
  4. Échangeur de chaleur à faisceau tubulaire selon l'une quelconque des revendications 1 à 3, caractérisé en ce que considéré dans le sens d'écoulement du premier milieu (M1) derrière une plaque tubulaire (12) côté sortie et la première sortie (4), un autre corps de séparation est agencé comme collecteur d'écoulement, lequel possède des tubes d'évacuation qui sont raccordés de manière à acheminer un fluide aux tubes (6) guidant le premier milieu (M1) afin de guider le premier milieu (M1) à travers la plaque tubulaire (12) côté sortie et le corps de séparation à la première sortie (4).
  5. Échangeur de chaleur à faisceau tubulaire selon la revendication 1, caractérisé en ce qu'une chambre collectrice (33) est agencée entre le corps de séparation (16) côté entrée et la plaque tubulaire (11) côté entrée, dans laquelle le second groupe (G2) de tubes débouche, dans lequel la première sortie (4) est raccordée à la chambre collectrice (33).
  6. Échangeur de chaleur à faisceau tubulaire selon l'une quelconque des revendications 1 à 5, caractérisé en ce que les tubes d'introduction (18) sont agencés de manière mobile longitudinalement dans les tubes (6) guidant le premier milieu (M1), dans lequel un éventuel courant de fuite peut être recueilli dans l'espace d'équilibrage (19) entre le corps de séparation (16) et la plaque tubulaire (11).
  7. Échangeur de chaleur à faisceau tubulaire selon la revendication 6, caractérisé en ce que l'espace d'équilibrage (19) est relié de manière à acheminer un fluide à la chambre collectrice (33).
  8. Échangeur de chaleur à faisceau tubulaire selon l'une quelconque des revendications 1 à 7, caractérisé en ce que les tubes d'introduction (18) traversent complètement le corps de séparation (16) et sont reliés côté entrée au corps de séparation (16).
  9. Échangeur de chaleur à faisceau tubulaire selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la première entrée (3) débouche dans une chambre d'afflux (17).
EP20758111.7A 2019-07-25 2020-07-24 Échangeur de chaleur à faisceau tubulaire Active EP4004474B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019120096.2A DE102019120096A1 (de) 2019-07-25 2019-07-25 Rohrbündelwärmetauscher
PCT/DE2020/100663 WO2021013312A1 (fr) 2019-07-25 2020-07-24 Échangeur de chaleur à faisceau tubulaire

Publications (3)

Publication Number Publication Date
EP4004474A1 EP4004474A1 (fr) 2022-06-01
EP4004474B1 true EP4004474B1 (fr) 2023-06-07
EP4004474C0 EP4004474C0 (fr) 2023-06-07

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US (1) US11408682B2 (fr)
EP (1) EP4004474B1 (fr)
JP (1) JP2022534130A (fr)
KR (1) KR20220076450A (fr)
CN (1) CN114144633B (fr)
DE (1) DE102019120096A1 (fr)
WO (1) WO2021013312A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115790247B (zh) * 2023-01-06 2023-04-21 中国核动力研究设计院 均流部件及换热装置
CN116857995A (zh) * 2023-06-07 2023-10-10 约克（无锡）空调冷冻设备有限公司 换热器

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ITMI20022449A1 (it) * 2002-11-19 2004-05-20 Tycon Technoglass S P A Scambiatore di calore con fascio tubiero in carburo di silicio e
ITMI20031268A1 (it) * 2003-06-24 2004-12-25 Italprotec S A S Di Cotogni Carla E C Scambiatore di calore a fascio tubiero.
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Publication number Publication date
CN114144633A (zh) 2022-03-04
KR20220076450A (ko) 2022-06-08
WO2021013312A1 (fr) 2021-01-28
JP2022534130A (ja) 2022-07-27
US20220163265A1 (en) 2022-05-26
US11408682B2 (en) 2022-08-09
EP4004474A1 (fr) 2022-06-01
DE102019120096A1 (de) 2021-01-28
CN114144633B (zh) 2023-06-06
EP4004474C0 (fr) 2023-06-07

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