EP2802835B1 - Modulare platte und schalenwärmetauscher - Google Patents

Modulare platte und schalenwärmetauscher Download PDF

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Publication number
EP2802835B1
EP2802835B1 EP13735908.9A EP13735908A EP2802835B1 EP 2802835 B1 EP2802835 B1 EP 2802835B1 EP 13735908 A EP13735908 A EP 13735908A EP 2802835 B1 EP2802835 B1 EP 2802835B1
Authority
EP
European Patent Office
Prior art keywords
heat transfer
heat exchanger
pairs
primary fluid
plates
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.)
Not-in-force
Application number
EP13735908.9A
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English (en)
French (fr)
Other versions
EP2802835A4 (de
EP2802835A1 (de
Inventor
Creed Taylor
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.)
Westinghouse Electric Co LLC
Original Assignee
Westinghouse Electric Co LLC
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from US13/348,832 external-priority patent/US20120103578A1/en
Application filed by Westinghouse Electric Co LLC filed Critical Westinghouse Electric Co LLC
Publication of EP2802835A1 publication Critical patent/EP2802835A1/de
Publication of EP2802835A4 publication Critical patent/EP2802835A4/de
Application granted granted Critical
Publication of EP2802835B1 publication Critical patent/EP2802835B1/de
Not-in-force legal-status Critical Current
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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/023—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers with heating tubes for nuclear reactors, as long as they are not classified according to a specified heating fluid, in another group
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0006—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the plate-like or laminated conduits being enclosed within a pressure vessel
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F28F3/083—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning capable of being taken apart
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/20—Fastening; Joining with threaded elements
    • F28F2275/205—Fastening; Joining with threaded elements with of tie-rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2280/00—Mounting arrangements; Arrangements for facilitating assembling or disassembling of heat exchanger parts
    • F28F2280/02—Removable elements

Definitions

  • feedwater for steam generators in nuclear power plants is typically preheated before being introduced into the secondary side of the steam generators.
  • feedwater is preheated before being introduced into boilers for non-nuclear power plant applications.
  • Feedwater heat exchangers are typically used for this purpose.
  • heat exchanger designs are divided into two general classes; heat exchangers with a plate structure and those with a tube and shell structure. The major difference in the two classes, with regard to both construction and heat transfer, is that the heat transfer surfaces are mainly plates in one structure and tubes in the other.
  • the tube and shell heat exchanger in a number of feedwater heater applications employs a horizontal or vertical tubular shell having hemispherical or flat ends.
  • the inside of the horizontal shell is divided into sections by a tube sheet which is normal to the axis of the shell. More specifically, at one end of the shell, a water chamber section is defined on one side of the tube sheet that includes a water inlet chamber having a water inlet opening and a water outlet chamber having a water outlet opening.
  • a U-tube tube and shell heat exchanger plurality of heat transfer tubes are bent at their mid portions in a U shape and extend from the other side of the tube sheet along the axis of the shell.
  • tubes are fixed to the tube sheet at both ends such that one end of each of the tubes opens in the water inlet chamber, while the other end opens in the water outlet chamber.
  • Another type of tube and shell heat exchanger employs straight tubes with an inlet chamber and an outlet chamber respectively at opposite ends of the tubes.
  • the heat transfer tubes are supported by a plurality of tube supporting plates, spaced at a suitable pitch in the longitudinal direction of the tubes.
  • An inlet opening for steam and a drain inlet and outlet are formed in the shell in the portion in which the tubes extend.
  • the feedwater coming into the feedwater heater from the water inlet chamber flows through the U-shaped heat transfer tubes and absorbs the heat from the heating steam coming into the feedwater heater from the steam inlet opening to condense the steam.
  • the condensate is collected at the bottom of the shell and discharged to the outside through a drain in the bottom of the shell. Thanks to the cylindrical shape of the shell and the heat exchange tubes, the structure is well suited as a pressure vessel, and thus tube and shell heat exchangers have been used in extremely high pressure applications.
  • the most significant drawback of the tube and shell heat exchangers is their heavy weight when compared to the surface area of the heat transfer surfaces. Due to that, the tube and shell heat exchangers are usually large in size. Also, it is difficult to design and manufacture tube and shell heat exchangers when the heat transfer, flow characteristics and expense are taken into account.
  • a typical plate heat exchanger is composed of rectangular, ribbed or grooved plates, which are pressed against each other by means of end plates, which, in turn, are tightened to the ends of the plate stack by means of tension rods or tension screws.
  • the clearances between the plates are closed and sealed with banded seals on their outer circumference and the seals are also used at the flow channels. Since the bearing capacity of the sleek plates is poor, they are strengthened with the grooves which are usually arranged crosswise in adjacent plates, wherein they also improve the pressure endurance of the structure when the ridges of the grooves are supported by each other. However, a more important aspect is the significance of the grooves for heat transfer; the shape of the grooves and their angle with respect to the flow, affect the heat transfer and pressure losses.
  • a heat supplying medium flows in every other clearance between the plates and a heat receiving medium flows in the remaining clearances.
  • the flow is conducted in between the plates via holes located in the vicinity of the corners of the plates.
  • Each clearance between the plates in alternate plate pairs always contains two holes with closed rims and two other holes functioning as inlet and outlet channels for the clearance between the plates.
  • the plate heat exchangers are usually constructed of relatively thin plates when a small and light structure is desired. Because the plates can be profiled into any desired shape, it is possible to make the heat transfer properties suitable for almost any type of application.
  • the greatest weakness in conventional plate heat exchangers is the seals which limit the pressure and temperature endurance of the heat exchangers. In several cases, the seals have impaired the possibility of use with heat supplying or heat receiving corrosive medium.
  • seals are utilized which are primarily used as deflectors for the flow. Obviously, pressure endurance is not required of the deflectors. Due to the structure of the plate stack, it is difficult to implement the seals. Elastic rubber gaskets are suggested for the seals so that it is possible to disassemble the heat exchanger, e.g., for cleaning purposes.
  • the foregoing objectives are achieved by a heat exchanger as defined in claim 1.
  • the inlet and outlet conduits and heat transfer plate pairs form a heat transfer assembly that is preferably supported by a structure which rests on and is moveable along an internal track attached to the interior of the shell, which facilitates removal of the heat transfer plates from the shell.
  • the modular plate and shell feedwater heater has a removable head integral with the shell for removal of the heat transfer plates for inspection, repair or replacement.
  • the inlet and outlet nozzles are sealed to and extend through the removable head.
  • the heat exchanger provided for herein includes a means for increasing the heat exchange capacity of the unit over time to accommodate upratings of the plant in which the heat exchanger is installed.
  • the inlet and outlet conduits include a number of additional attachment points for pairs of the heat transfer plates that are initially plugged.
  • the inlet and outlet conduits can be expanded by the attachment of additional heat transfer plate pairs or modules.
  • the heat exchanger is provided with a spacer module having no or relatively negligible heat transfer capacity that is supported in tandem with the heat transfer plate modules. A heat transfer plate module may later be substituted for the spacer module to increase the heat transfer capacity of the heat exchanger.
  • At least some of the couplings between the pairs of heat transfer plates, or modules of bonded pairs of heat transfer plates, are detachable for ease of repair and replacement.
  • tie rods connect the modules; and in the embodiment where the inlet and outlet conduits extend between modules, the tie rods provide compressive force for pressure seals at the interface of the conduit segments of the interfacing modules to form a tight seal.
  • the heat transfer assembly is withdrawn from the shell with the removable head.
  • a manway is provided in the shell for gaining access to the interior of the shell for disconnecting the feedwater inlet nozzle from the feedwater inlet conduit and for disconnecting the feedwater outlet conduit from the feedwater outlet nozzle or both options may be provided.
  • the modules have support panels at each end between which the tie rods extend.
  • the heat transfer plate pairs are sandwiched between the support panels and in one embodiment, the primary fluid inlet conduit and the primary fluid outlet conduit pass through the modules.
  • the support panels are thicker than the heat transfer plates.
  • the heat transfer plates between the support panels are welded to each other and to the support panels and adjacent support panels are mechanically connected to each other.
  • the invention also provides for a method of cleaning or repairing the feedwater heater which includes the steps of: accessing the interior of the pressure vessel shell; removing at least one pair of heat transfer plates from the heat transfer assembly of heat transfer plates; cleaning, repairing, or replacing the removed pair of heat transfer plates; and reconnecting the cleaned, repaired or replaced pair of heat transfer plates to the heat transfer assembly.
  • the step of accessing the interior of the pressure vessel shell includes removing the detachable head; and the step of removing at least one pair of heat transfer plates comprises removing the one pair of heat transfer plates from the feedwater inlet conduit and the feedwater outlet conduit.
  • the invention further includes a method of repairing, inspecting, cleaning or uprating the feedwater heater wherein the pressure vessel has a detachable head.
  • the method comprises the steps of: removing the detachable head or otherwise accessing the interior of the pressure vessel shell; and disconnecting the feedwater inlet conduit and the feedwater outlet conduit from the feedwater inlet nozzle and the feedwater outlet nozzle, respectively, while the heat transfer assembly is in the pressure vessel.
  • This method further includes the step of replacing a defective pair of heat transfer plates as well as the step of increasing the number of pairs of heat transfer plates after the feedwater heater has been placed in service to uprate the feedwater heater.
  • feedwater heater, 10, of the inventions claimed hereafter is illustrated in the elevational view shown in Figure 1 and the top view shown in Figure 2 .
  • Two heat transfer plates 12 and 14 are welded together to form a welded plate pair 16 that therebetween form a flowpath for feedwater fluid as in a traditional plate heat exchanger.
  • the heat transfer plate pair 16 is removably connected, such as with gaskets 18 and bolted flange joints 20, to and in fluid communication with an inlet header pipe 22 at one end of the welded heat transfer plate pair 16 and an outlet header pipe 24 at the other end of the welded heat transfer plate pair 16.
  • a number of these welded heat transfer plate pairs 16 are stacked in a spaced tandem arrangement, each coupled between the inlet header and outlet header to form a heat transfer assembly having a parallel flow path.
  • One such arrangement is shown in Figure 2 .
  • a number of the heat transfer plate pairs 16 can be coupled in series with the ends of the series arrangement removably attached in a similar fashion to the inlet header pipe 22 and the outlet header pipe 24.
  • the terminal ends of the heat transfer plate pairs 16 are connected either directly or indirectly to the inlet header pipe 22 and the outlet header pipe 24.
  • the header pipes 22 and 24 are supported by a frame structure 30 which rests on an internal track 32 attached to the lower portion of the cylindrical shell 34 that forms a pressure vessel that surrounds the heat transfer plate assembly 36.
  • the track 32 and wheels 33 on the frame structure 30 facilitate removal of the heat transfer plate assembly from the shell for repair, cleaning or uprating.
  • the shell has an integral hemispherical end 38 on one side and a removable hemispherical head 40 on the other side to completely enclose and seal the heat transfer assembly 36 within the pressure vessel formed by the cylindrical shell 34, hemispherical end 38 and removable head 40.
  • the removable head 40 has the feedwater inlet nozzle 26 and the feedwater outlet nozzle 28 extending therethrough as shown in Figures 1 and 2 .
  • the hemispherical end 38 can be constructed to be removable instead of the head 40 or both can be connected by bolted flange connections to the shell 34 for added flexibility in gaining access to the interior of the shell 34 to service the heat transfer plate assembly 36.
  • the shell 34 is also fitted with an extraction steam inlet 42, drain inlets 44 and 46 and drain outlets 48 and 50.
  • the inlet feedwater passes through the inlet nozzle 26, the inlet header pipe 22, the heat transfer welded plate pairs 16 where it is heated by the drain flow and extraction steam, the outlet header pipe 24 and the outlet nozzle 28.
  • the extraction steam upon entering the feedwater heater through the extraction steam inlet 42, is distributed by the steam impingement plate 52 and passes through the upper shell region where it mixes with the entering drain flow from the drain flow inlet nozzles 44 and 46.
  • the extraction steam and drain flow then pass between the heat transfer plate welded pairs 16, where it is cooled by the feedwater and condenses to the lower shell region where it exits through the drain flow outlet nozzles 48 and 50.
  • an inspection of the heat transfer plates and shell internal surface can be performed using the following steps. First, the shell end 38 is unbolted at the flange 54 and removed. The header pipes 22 and 24 may then be disconnected from the inlet and outlet nozzles 26 and 28. A manway 56 on the head 40 can be used to gain access to the connection between the inlet and outlet header pipes 22 and 24 and the inlet and outlet nozzles 26 and 28. Alternately, when the head 40 is removed at the flange 58, the head 40 can be moved out with the heat transfer assembly 36 sliding on the track 32 so that access can be gained to the connection between the inlet and outlet headers 22 and 24 and the feedwater inlet and outlet nozzles 26 and 28.
  • the heat transfer plate assembly 36 can be moved as a unit along the tracks 32 located in the bottom of the shell 34 to a point where the individual heat transfer plates 12 and 14 and the interior of the shell 34 can be inspected for damage.
  • the individual heat transfer plate pairs 16 can then be cleaned or, if necessary, repaired or replaced. If repair or replacement is necessary, the heat transfer plate pair 16 in need of attention can be unbolted from the inlet header pipe 22 and the outlet header pipe 24 and replaced with a new or repaired heat transfer plate pair 16 bolted in its place.
  • the outlet header pipe 24 and inlet header pipe 22 are also provided with one or more additional openings 60 that are initially sealed by plugs. These additional openings can be unsealed to accommodate additional heat transfer plate pairs 16 if uprating in the future is desirable.
  • the removable plate design allows for replacement of the heat transfer surface and mass production of heat transfer plates and gaskets results in a relatively low cost for critical spares.
  • Employing this design makes it possible to increase the number of plates and thus the heat transfer area to accommodate power uprates and provides improved shell side inspection.
  • the heat transfer plate assembly 36 in the embodiment shown in Figures 3 , 4 and 5 is formed from a number of heat transfer plate modules 17. Four such heat transfer plate modules are visible in Figure 5 . Each such module 17 is formed from a number of tandemly spaced heat transfer plate pairs 16 which are bonded together as an integral unit. Each of the modules 17 shown in Figures 3 , 4 and 5 has approximately 10 such heat transfer plate pairs, though it should be appreciated that any number of such heat transfer plate pairs 16 may be used with the consequence that the more heat transfer plate pairs 16 to a module 17 the more costly the module will be to replace. Alternatively, the more modules there are the more will be spent on gaskets and closure hardware. An optimum range of the number of plates per module should be determined on an application specific basis based on economic considerations. Also, the number of modules 17 in the heat transfer assembly 36 may vary depending on the number of heat transfer plate pairs 16 per module and the heat transfer requirements of the application in which the heat exchanger is going to be employed.
  • each heat transfer plate pair 16 has two openings on either side with the corresponding openings substantially aligned with each other and to which incremental segments 23 of the inlet and outlet conduits 22 and 24 are bonded such as by welding, brazing or any other suitable bond that forms a substantially rigid durable joint that is substantially impervious to the fluids flowing in and around the inlet and outlet conduits 22 and 24 in the area between the heat transfer plate pairs 16.
  • the incremental segments of the inlet and outlet conduits 22 and 24 that pass between the heat transfer plate pairs 16 and the outside surface of the adjoining heat transfer plate pairs 16 provide a flow path between the heat transfer plate pairs 16 for the extraction steam and drain flow to pass.
  • the face plate 62 in the front of the heat transfer plate assembly has openings for the inlet and outlet conduits 22 and 24 so that the flanges on the outer segments 23 can be respectively attached to the inlet and outlet nozzles 26 and 28 (shown in Figure 2 ).
  • the outer segments 23, i.e., both inlet and outlet on the rear heat transfer plate at the end 80 of the heat transfer assembly 36 are either plugged to close the feedwater flow loop or the rear heat transfer plate is made without the inlet and outlet holes.
  • FIG. 6 A schematic of the flow of the primary fluid through the heat transfer plate assembly of the embodiments described above having a parallel flow path through the heat transfer plate pairs 16 is illustrated in Figure 6.
  • Figure 7 shows the construction of the heat transfer plate pairs.
  • a weld bead 66 extends around each of the incremental segments 23 of the inlet conduit 22 at the corresponding openings in the heat transfer plates 12 and 14 and form a fluid tight seal at the interface.
  • a weld bead 68 extends around the incremental segments 23 of the outlet conduit 24 at the corresponding openings in the heat transfer plates 12 and 14 and form a fluid tight seal at the interface.
  • a girth weld 70 extends around the entire circumference of the heat transfer plate pair 16.
  • the primary fluid enters the inlet conduit 22 inlet 72 of each heat transfer plate pair 16 connecting it to adjacent pairs or support plates.
  • a portion of the fluid flows down between the heat transfer plates 12 and 14 where it absorbs heat from the extraction steam and drain flow passing on the outside of the heat transfer plate pairs and exits at the outlet 78 to the outlet conduit 24 where it joins with the primary fluid upstream flow from other heat transfer plate pairs that entered through the outlet conduit inlet 76 to the heat transfer plate pair 16.
  • FIG 8 is a schematic of one embodiment of a heat transfer plate module 17.
  • the module 17 is shown with four heat transfer plate pairs 16, though as previously stated the number of heat transfer plate pairs 16 may vary.
  • the heat transfer plate pairs 16 have relatively thin heat transfer plates 12 and 14, as compared to the outer support plates 82, which are thicker than the inner heat transfer plate pairs 16.
  • the support plates 82 are referred to as support plates and are longer than the others and extend past the others to accept the tie rods shown in Figures 3 , 4 and 5 , though it should be appreciated that this embodiment is slightly different than the embodiment shown in Figures 3 , 4 and 5 .
  • the inner heat transfer plates are welded to each other with the conduit incremental segments 23 (shown in Figure 4 ) extending therebetween, with the welds extending around the circular openings in the incremental segments of the inlet conduit 22 and outlet conduit 24, and the outer edges by the circumferential plate welds 70.
  • Gasket grooves 84 are provided around the inlet conduit 22 and outlet conduit 24 openings in the support plates 82 for gaskets to seal the openings at the interface with mating support plates 82 of adjoining modules 17.
  • a spacer module 88 is inserted in place of a heat transfer plate pair module 17 to preserve space for the later addition of another heat transfer plate pair module 17 should a future uprating of the plant in which the heat exchanger is installed require additional heat transfer capacity within the existing shell.
  • One embodiment of such a spacer module 88 is illustrated in Figure 10 .
  • the spacer module 88 is the same size as a standard heat transfer plate pair module 17 for the heat exchange unit 10 in which it is to be employed.
  • the spacer module in this embodiment has two support plates 82 with gasket grooves 84, as previously described, that are separated by an upper support 96 and lower support 98 with a secondary fluid drain 94.
  • the upper support 96 and lower support 98 may (but need not) be part of one continuous support cylinder.
  • the embodiment shown in Figure 10 is intended to be inserted between heat transfer plate pair modules 17 and has a pipe 90 which is welded around its circumference at each support plate interface to form a hermetic seal.
  • the pipe 90 forms a portion of the inlet conduit 22, carrying the primary fluid between the heat transfer plate pair modules 17 that it connects.
  • a pipe 92 is sealed to and spans the space between the support plates 82 of the spacer module 88 to carry the primary fluid through the outlet conduit 24. If the spacer is used at the end of the end 80 of the heat transfer plate assembly 36 then the openings in the spacer module support plates 82 is unnecessary.
  • FIG 11 illustrates one embodiment of a tie rod arrangement that can be used to draw the modules 17 and 88 together.
  • the tie rod 64 is designed to span between support plates 82, similar to the spans between support frames 62 shown in Figure 5 .
  • the tie rods 64 have one end with a reduced diameter that has a circumferential thread 104.
  • the circumferential thread 104 terminates at a bearing surface 106 that is sized to abut one side of a periphery of a module support plate around a hole in which the thread 104 is sized to extend through and out the other side.
  • the heat transfer plate assembly 36 has wheels 33 that ride on the track 32 previously described to facilitate servicing of the heat transfer plate assembly. Servicing is the same as described for the embodiment illustrated in Figures 1 and 2 , except to uprate the heat transfer plate assembly, the spacer module 88 is removed and an additional heat transfer plate module 17 is coupled in its place.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Claims (14)

  1. Wärmetauscher (10), umfassend:
    eine längliche Druckgefäßhülle (34) mit einer axialen Dimension mit einem abnehmbaren Verschluss (40) an einem Ende der axialen Dimension, einem Primärfluid-Einlass (26), einem Primärfluid-Auslass (28), einem Sekundärfluid-Einlass (42, 44, 46), einem Ablaufauslass (48, 50) und einer Wärmeübertragungsanordnung (36) umfassend:
    eine Primärfluid-Einlassleitung (22), die sich in das Druckgefäß (34) von dem Primärfluid-Einlass (26) erstreckt;
    eine Primärfluid-Auslassleitung (24), die sich in das Druckgefäß (34) von dem Primärfluid-Auslass (28) erstreckt;
    eine Vielzahl von Paaren von Wärmeübertragungsplatten (16), die im Tandem getragen werden, wobei jedes der Paare von Platten um den Umfang herum abgedichtet (70) ist, um einen Primärfluid-Strömungskanal zwischen einer ersten und zweiten Wärmeübertragungsplatte (12, 14) eines jeden Paars zu definieren, wobei jedes Paar eine Wärmeübertragungsplatten-Einlassöffnung (72), die entweder direkt oder indirekt fluidmäßig mit der Primärfluid-Einlassleitung (22) verbunden ist, und eine Wärmeübertragungsplatten-Auslassöffnung (78), die entweder direkt oder indirekt fluidmäßig mit der Primärfluid-Auslassleitung verbunden ist, um einen parallelen Strömungspfad mit einer Strömung in dieselbe Richtung durch jedes der Paare von Wärmeübertragungsplatten in eine Richtung senkrecht auf die axiale Dimension der Druckgefäßhülle zu bilden;
    Mittel zur Erweiterung einer Wärmeübertragungskapazität der Wärmeübertragungsanordnung gegenüber einer ursprünglichen Wärmeübertragungskapazität, die der Wärmetauscher aufweist, wenn er erstmalig in Betrieb genommen wird; und
    wobei die Vielzahl von Paaren von Wärmeübertragungsplatten (16) in Modulen (17) angeordnet sind, wobei zumindest eines der Module, das zumindest eines der Paare von Wärmeübertragungsplatten umfasst, im Tandem mit einem benachbarten Modul oder dem Primärfluid-Einlass oder dem Primärfluid-Auslass mit einer zerstörungsfrei entfernbaren mechanischen Kupplung (84) verbunden ist, und
    dadurch gekennzeichnet, dass die Mittel zur Erweiterung der Wärmeübertragungskapazität der Wärmeübertragungsanordnung ein Abstandhaltermodul umfassen, das eine im Wesentlichen geringere Wärmeübertragungskapazität als die Module von Paaren von Wärmeübertragungsplatten aufweist, wobei das Abstandhaltermodul im Tandem mit den Modulen von Paaren von Wärmeübertragungsplatten verbunden ist, wobei das Abstandhaltermodul (88) in der axialen Dimension zumindest so lang wie die Module der Paare von Wärmeübertragungsplatten ist und einen axial dort hindurch verlaufenden Einlasskanal aufweist, der fluidmäßig entweder direkt oder indirekt mit der Primärfluid-Einlassleitung verbunden ist, und einen axial dort hindurch verlaufenden Auslasskanal, der fluidmäßig entweder direkt oder indirekt mit der Primärfluid-Auslassleitung verbunden ist.
  2. Wärmetauscher (10) nach Anspruch 1, wobei zumindest einige der Module (17) eine Vielzahl der Paare von Wärmeübertragungsplatten (16) umfassen, wobei die Paare von Wärmeübertragungsplatten innerhalb der zumindest einigen Module mit einem Zuganker (64) zusammengehalten werden.
  3. Wärmetauscher (10) nach Anspruch 2, wobei die zumindest einigen der Module (17), die im Tandem mit einem benachbarten Modul verbunden sind, durch Koppeln ihrer jeweiligen Zuganker (64) verbunden sind.
  4. Wärmetauscher (10) nach Anspruch 1, wobei die Wärmeübertragungsanordnung (36) aus der Druckgefäßhülle (34) verschiebbar ist, wenn der abnehmbare Verschluss (40) geöffnet wird.
  5. Wärmetauscher (10) nach Anspruch 1, wobei die Wärmeübertragungsanordnung (36) beweglich auf einer Schiene (32) gelagert ist, die an einer Innenseite des Druckgefäßes (34) angebracht ist, so dass die Wärmeübertragungsanordnung als eine Einheit aus dem Druckgefäß durch das eine Ende (40) entfernt werden kann, indem die Wärmeübertragungsanordnung entlang der Schiene bewegt wird.
  6. Wärmetauscher (10) nach Anspruch 5, wobei die Wärmeübertragungsanordnung (36) auf der Schiene (32) auf Rädern (33) getragen wird, die auf der Schiene laufen.
  7. Wärmetauscher (10) nach Anspruch 1, wobei der Primärfluid-Einlass (26) und der Primärfluid-Auslass (28) sich von dem abnehmbaren Verschluss (40) weg erstrecken.
  8. Wärmetauscher (10) nach Anspruch 1, wobei die Wärmeübertragungsanordnung (36) mit einer Anzahl von zusätzlichen Kupplungen (60) ausgerüstet ist, die dazu ausgestaltet sind, zusätzliche Paare von Wärmeübertragungsplatten (16) zu befestigen, wobei die zusätzlichen Kupplungen ursprünglich zugestopft sind und für eine spätere Aufrüstung der Wärmeübertragungskapazität des Wärmetauschers gegenüber einer ursprünglichen Wärmeübertragungskapazität verfügbar sind, nachdem der Wärmetauscher in Betrieb genommen wurde, indem zumindest einige Kupplungen geöffnet und eine Anzahl von zusätzlichen Paaren von Wärmeübertragungsplatten befestigt werden.
  9. Wärmetauscher (10) nach Anspruch 1, wobei die Druckgefäßhülle (34) eine zylindrische Gestalt mit halbkugelförmigen Enden (40, 38) ist.
  10. Wärmetauscher (10) nach Anspruch 1, wobei zumindest einige der Module (17) eine Vielzahl von Paaren von Wärmeübertragungsplatten (16) umfassen, wobei jedes der Paare von Wärmeübertragungsplatten innerhalb eines Moduls in der Tandemanordnung über eine geschweißte Kupplung (23) miteinander verbunden ist.
  11. Wärmetauscher (10) nach Anspruch 1, wobei zumindest einige der Module (17) eine Trägerplatte (82) an einem ersten und einem zweiten Ende aufweisen, wobei die Wärmeübertragungsplatten (12, 14) dazwischen angeordnet sind, wobei die Trägerplatten dicker als die Wärmeübertragungsplatten sind.
  12. Wärmetauscher (10) nach Anspruch 1, wobei die Module (17) durch Zuganker (64) im Tandem gehalten werden.
  13. Verfahren zum Reparieren, Inspizieren, Reinigen oder Aufrüsten des Wärmetauschers (10) nach Anspruch 1, umfassend die folgenden Schritte:
    Zugreifen auf das Innere der Druckgefäßhülle (34);
    Trennen der Primärfluid-Einlassleitung (22) bzw. der Primärfluid-Auslassleitung (24) jeweils von dem Primärfluid-Einlass (26) bzw. dem Primärfluid-Auslass (28), und
    umfassend den Schritt des Ersetzens eines defekten Paars von Wärmeübertragungsplatten (16).
  14. Verfahren nach Anspruch 13, umfassend den Schritt der Erhöhung der Anzahl von Paaren von Wärmeübertragungsplatten (16) innerhalb der Wärmeübertragungsanordnung (36), nachdem der Wärmetauscher (10) in Betrieb genommen wurde, um den Wärmetauscher aufzurüsten.
EP13735908.9A 2012-01-12 2013-01-04 Modulare platte und schalenwärmetauscher Not-in-force EP2802835B1 (de)

Applications Claiming Priority (2)

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US13/348,832 US20120103578A1 (en) 2009-04-29 2012-01-12 Modular plate and shell heat exchanger
PCT/US2013/020206 WO2013106240A1 (en) 2012-01-12 2013-01-04 Modular plate and shell heat exchanger

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EP2802835A1 EP2802835A1 (de) 2014-11-19
EP2802835A4 EP2802835A4 (de) 2016-01-13
EP2802835B1 true EP2802835B1 (de) 2018-09-05

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CN (1) CN104040282B (de)
BR (1) BR112014016949B1 (de)
CA (1) CA2864231C (de)
ES (1) ES2699809T3 (de)
MX (1) MX368753B (de)
TW (1) TWI593934B (de)
WO (1) WO2013106240A1 (de)

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EP2802835A4 (de) 2016-01-13
EP2802835A1 (de) 2014-11-19
CA2864231C (en) 2020-01-21
KR20140112543A (ko) 2014-09-23
MX368753B (es) 2019-10-15
TWI593934B (zh) 2017-08-01
BR112014016949A2 (pt) 2020-06-23
KR101962996B1 (ko) 2019-07-31
MX2014008117A (es) 2014-08-27
JP6200433B2 (ja) 2017-09-20
CN104040282A (zh) 2014-09-10
CN104040282B (zh) 2016-08-24
CA2864231A1 (en) 2013-07-18
WO2013106240A1 (en) 2013-07-18
BR112014016949B1 (pt) 2021-05-11
JP2015505027A (ja) 2015-02-16
ES2699809T3 (es) 2019-02-12
TW201339532A (zh) 2013-10-01

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