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WO2015028021A1 - Échangeur de chaleur à plaques et calandre et utilisation d'un échangeur de chaleur à plaques et calandre - Google Patents

Échangeur de chaleur à plaques et calandre et utilisation d'un échangeur de chaleur à plaques et calandre Download PDF

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Publication number
WO2015028021A1
WO2015028021A1 PCT/DK2014/050236 DK2014050236W WO2015028021A1 WO 2015028021 A1 WO2015028021 A1 WO 2015028021A1 DK 2014050236 W DK2014050236 W DK 2014050236W WO 2015028021 A1 WO2015028021 A1 WO 2015028021A1
Authority
WO
WIPO (PCT)
Prior art keywords
shell
heat exchanger
subcooler
condenser
refrigerant
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.)
Ceased
Application number
PCT/DK2014/050236
Other languages
English (en)
Inventor
Christian Per Bunde-Pedersen
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.)
Johnson Controls Denmark ApS
Original Assignee
Johnson Controls Denmark ApS
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
Application filed by Johnson Controls Denmark ApS filed Critical Johnson Controls Denmark ApS
Priority to US14/906,602 priority Critical patent/US20160161191A1/en
Priority to CN201480043801.4A priority patent/CN105473958B/zh
Publication of WO2015028021A1 publication Critical patent/WO2015028021A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F28D9/0006—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
    • 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters
    • 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
    • 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
    • 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
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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

Definitions

  • the present invention relates to a shell-and-plate heat exchanger for cooling and condensing a circulating refrigerant.
  • the invention further relates to use of a shell- and-plate heat exchanger.
  • Shell-and-plate (or plate-and-shell) heat exchangers consist of a series of corrugated plates peripherally welded to each other in pairs (so-called cassettes) which in turn is welded to each other along the entrance holes and exit holes to for a complete plate pack.
  • the welded plate pack is inserted and either welded or bolted within a tubular shell, typically formed from steel and typically without peripheral gaskets.
  • the shell- and-plate heat exchanger is a versatile design which combines the strength of a shell- and-tube exchanger with the thermal efficiency of a plate exchanger in that the shell- and-plate heat exchanger combines the pressure and temperature capabilities of a typically cylindrical shell with the excellent heat transfer performance of a plate heat exchanger.
  • the shell-and-plate heat exchanger combines the benefits of a traditional shell and tube type heat exchanger but with the high efficiency provided for in a plate type exchanger.
  • WO 97/45689 it is therefore known to use a plate and shell heat exchanger for evaporating the refrigerant in a refrigerator circuit and another plate and shell heat exchanger for condensing the refrigerant in the refrigerator circuit. But this heat exchanger design is complex and difficult to install. It is therefore an object of the present invention to provide for a simpler and cost- efficient heat exchanger design.
  • the invention relates to a shell-and-plate heat exchanger for cooling and condensing a circulating refrigerant.
  • the heat exchanger comprises a desuperheater for lowering the temperature of the gaseous refrigerant to a temperature above the condensation temperature of the refrigerant, wherein the desuperheater is formed by a stack of corrugated desuperheater heat transfer plates.
  • the desuperheater is connected to a condenser for condensing the refrigerant, wherein the condenser is formed by a stack of corrugated condenser heat transfer plates.
  • the condenser is connected to a subcooler for further lowering the temperature of the condensed refrigerant, wherein the subcooler is formed by a stack of corrugated subcooler heat transfer plates, and wherein the stack of corrugated desuperheater heat transfer plates, the stack of corrugated condenser heat transfer plates and the stack of corrugated subcooler heat transfer plates are arranged inside the same common continuous shell.
  • the condenser and the subcooler are connected through a liquid refrigerant container arranged bellow the stack of condenser heat transfer plates and/or the stack of subcooler heat transfer plates, in that the condensed refrigerant is collected in the liquid refrigerant container from which the liquid refrigerant continues into the subcooler through a subcooler inlet conduit.
  • a refrigeration cycle is also severely reduced if the shell-and-plate heat exchanger delivers gaseous refrigerant it is advantageous to ensure that only liquid refrigerant is continued into the subcooler by using gravity to collect the liquid refrigerant in a liquid refrigerant container arranged beneath the condenser and/or the subcooler.
  • a conduit inlet opening of said subcooler inlet conduit is arranged at the bottom of said liquid refrigerant container.
  • Arranging the inlet opening of the subcooler inlet conduit at the bottom of the liquid refrigerant container is advantageous in that it increases the capacity of the refrigerant container, in that the subcooler inlet conduit hereby is capable of almost completely emptying the liquid refrigerant container.
  • said liquid refrigerant container is arranged outside said shell. Arranging the liquid refrigerant container outside the heat exchanger shell is advantageous in that it enables a simpler heat exchanger design.
  • said shell encircles said desuperheater, said condenser and said subcooler.
  • said shell-and-plate heat exchanger comprises a refrigerant conduit through which said refrigerant is moved from said desuperheater to said condenser and wherein said refrigerant conduit is arranged inside said shell.
  • Arranging the refrigerant conduit inside the shell is advantageous in that complicated piping hereby can be avoided, thus reducing cost and simplifying installation.
  • said shell-and-plate heat exchanger comprises a coolant conduit extending continuously through said desuperheater, said condenser and said subcooler inside said common continuous shell.
  • Arranging the coolant conduit to extend continuously through the desuperheater, the condenser and the subcooler inside the shell is advantageous in that external piping is avoided, thus reducing cost and simplifying installation.
  • said desuperheater and said condenser are separated by a first separation plate arranged inside said common continuous shell and wherein said first separation plate comprises a refrigerant conduit and a coolant passage opening.
  • Arranging a separation plate between the desuperheater and the condenser is advantageous in that the plate will ensure that refrigerant is guided correctly from the desuperheater and into the condenser, while at the same time ensuring that condensed liquid cannot pass from the condenser and into the desuperheater.
  • the efficiency of both functions increased.
  • said condenser and said subcooler are separated by a second separation plate arranged inside said common continuous shell and wherein said second separation plate comprises only a coolant passage opening.
  • Arranging a separation plate between the condenser and the subcooler is advantageous in that the plate will prevent that refrigerant is passed directly from the condenser and into the subcooler, hereby enabling that liquid and gaseous refrigerant can be separated to increase the function of the subcooler.
  • a separation gasket is arranged between one or more of said heat transfer plates and said shell to guide the refrigerant flow between said condenser and said subcooler and/or said desuperheater and said condenser.
  • gaskets to separate the condenser from the subcooler and/or the desuperheater from the condenser - instead of a first and/or a second separation plate - is advantageous in that gaskets entail a simpler and less expensive heat exchanger design.
  • said continuous shell is formed as a monolithic tube.
  • Forming the shell as a monolithic tube is advantageous in that it simplifies the manufacturing process and reduces cost, since the shell is a pressure vessel.
  • said continuous shell is formed by two or more connected shell parts.
  • Forming the shell by two or more connected shell parts is advantageous in that it hereby is possible to subsequently open the shell e.g. in case of maintenance or repair work.
  • said heat exchanger comprises endplates welded to both ends of said shell. Welding the endplates ensures that the pressure vessel is both strong and tight.
  • said shell is cylindrical.
  • Forming the shell cylindrical is advantageous in that this shape ensure an even distribution of the pressure load on the shell.
  • said desuperheater heat transfer plates, said condenser heat transfer plates and said subcooler heat transfer plates are substantially identical.
  • Forming all the heat transfer plates inside the shell-and-plate heat exchanger substantially identical is advantageous in that it reduces production costs and simplifies assembly.
  • said common continuous shell is a pressure vessel designed and/or approved to withstand a pressure between 0.7 and 15 MPa, preferably between 1.5 and 10 and most preferred between 2.5 and 7.5 MPa.
  • the present pressure ranges presents an advantageous relationship between safety and cost.
  • the invention also relates to use of a shell-and-plate heat exchanger according to any of the previously disclosed shell-and-plate heat exchangers for cooling and condensing a refrigerant in a refrigeration cycle.
  • Fig. 1 shows an embodiment of the coolant flow through a cross section of a shell-and-plate heat exchanger, as seen from the side,
  • Fig. 2 shows an embodiment of the refrigerant flow through a cross section of a shell-and-plate heat exchanger, as seen from the side
  • Fig. 3 shows a cross section through a dividable shell-and-plate heat exchanger, as seen from the side, and
  • Fig. 4 shows an embodiment of a heat transfer plate for a shell-and-plate heat exchanger, as seen from the front.
  • Figure 1 shows an embodiment of the coolant flow through a cross section of a shell- and-plate heat exchanger 1, as seen from the side.
  • the coolant inlet 22 is arranged in one endplate 21 and the coolant outlet 23 is arranged in the opposite endplate 21, while the refrigerant inlet 24 is arranged at the coolant outlet 23 end of the shell 8 and the refrigerant outlet 25 is arranged at the other end of the shell 8.
  • the refrigerant and the coolant is arranged to flow countercurrently but in another embodiment the refrigerant and the coolant could flow in the same direction through the heat exchanger 1.
  • the heat exchanger 1 could comprise more than one coolant inlet 22, coolant outlet 23, refrigerant inlet 24 and/or refrigerant outlet 25 and/or some or all the inlets 22, 24 and/or all the outlets 23, 25 could be arranged in the endplates 22.
  • the heat exchanger 1 comprises a desuperheater 2, a condenser 4 and a subcooler 6 arranged inside the same common continuous shell 8 encircling all three heat exchanger functions.
  • Each of the desuperheater 2, the condenser 4 and the subcooler 6 are formed by a number of heat transfer plates 3, 5, 7 welded together as discussed in relation with fig. 4.
  • the arrows on figure 1 illustrate an embodiment of a coolant flow through the coolant conduit 14 of the heat exchanger 1.
  • the entire coolant conduit 14 is arranged inside said shell 8 but in another embodiment at least parts of the coolant conduit 14 could be arranged outside the shell 8 e.g. to pass a separation plate 15, 18 or other.
  • the coolant enters the heat exchanger 1 at the coolant inlet 22 and flows through the subcooler 6.
  • a second separation plate 18 blocks the access to the condenser 4 and thus forces the coolant to run transversely towards the upper coolant passage opening 17 in the second separation plate 18 from which it enters the condenser 4.
  • condenser coolant blocking means 30 forces the coolant to run transversely towards the bottom of the condenser 4 and then longitudinal until a first separation plate 15 forces the coolant upwards towards the upper coolant passage opening 17 in the first separation plate 15. From the coolant passage opening 17 the coolant is forced down through the desuperheater 2 and finally out through the coolant outlet 23.
  • the coolant performs one pass in the subcooler 6 and the desuperheater 2 and two passes in the condenser 4 but in another embodiment one or more of the desuperheater 2, condenser 4 and subcooler 6 could be arranged to comprise means for allowing fewer or particularly more passes.
  • the differences between the refrigerant and the coolant, flowing through the heat exchanger 1, are that the refrigerant is always circulating in a closed circuit, wherein it changes phase from one state of matter to another (between gas and liquid form) at least twice during circulation, while the coolants main purpose is to remove heat from the refrigerant.
  • the coolant is water e.g. circulating through an external air cooled heat exchanger or transporting the absorbed heat to a particular place where it can be utilised.
  • the coolant could be brine or another form of natural or artificial coolant suitable for flowing through a combined desuperheater 2, condenser 4 and subcooler 6.
  • the desuperheater heat transfer plates 3, the condenser heat transfer plates 5 and the subcooler heat transfer plates 7 are substantially identical to reduce production cost and simplifying assembly but in another embodiment the plates 3, 5, 7 could be designed for their specific use, for their specific location in the heat exchanger 1, for specific temperatures or other making the design of the plates 3, 5, 7 in the heat exchanger vary.
  • all the plates 3, 5, 7, the shell 8 and the endplates 21 are all made from stainless steel because of this materials strength and durability but in another embodiment all or some of the heat exchanger parts could be made from another material such as titanium, aluminium, a composite material or other.
  • Fig. 2 shows an embodiment of the refrigerant flow through a cross section of a shell-and-plate heat exchanger 1, as seen from the side.
  • the arrows on figure 2 illustrate an embodiment of a refrigerant flow through the combined desuperheater 2, condenser 4 and subcooler 6.
  • the hot gaseous refrigerant enters the heat exchanger 1 through the refrigerant inlet 24 from which it is directed up through the desuperheater 2 to dissipate some of its heat to the coolant flowing through the inside of the plate pack in the desuperheater 2.
  • a refrigerant conduit 13 along the upper periphery of the first separation plate 15 ensures that the desuperheated gaseous refrigerant is directed into the condenser there the refrigerant condenses while passing down through the relatively cold heat transfer plates 5 in the condenser 4.
  • the liquid refrigerant is then guided out of the shell 8 through the liquid refrigerant outlet 16 and collected in a liquid refrigerant container 9 arranged outside the shell 8.
  • liquid refrigerant could instead or also be collected inside the shell 8 before being lead to the subcooler 6.
  • a subcooler inlet conduit 10 extends down into the liquid refrigerant container 9 so that an conduit inlet opening 11 of the subcooler inlet conduit 10 is arranged at the bottom 12 of the liquid refrigerant container 9 to ensure that only liquid is guided into the subcooler 6.
  • the liquid refrigerant is further cooled before it exits the heat exchanger 1 through the refrigerant outlet 25 arranged at the top of the shell 8.
  • the refrigerant only makes one pass through each of the desuperheater 2, the condenser 4 and the subcooler 6 but in another embodiment one or more of the desuperheater 2, condenser 4 and subcooler 6 could be arranged to comprise means for allowing more than one pass.
  • the refrigerant is ammonia but in another embodiment the refrigerant could be carbon dioxide, Butane, a HFC, water vapour or another fluid suitable for acting as a refrigerant in a shell-and-plate heat exchanger 1.
  • the shell-and-plate heat exchanger 1 is used for cooling and condensing a refrigerant in a refrigeration cycle. I.e. after the cold liquid refrigerant leaves the shell-and-plate heat exchanger 1 it is typically directed to an expansion valve, which will reduce the pressure making at least some of the refrigerant evaporate and thus making its temperature drop drastically. At this stage the cold refrigerant is then used for cooling purposes by which the entire refrigerant evaporates. The gaseous refrigerant is then directed through a compressor compressing the refrigerant, which in turn raises its temperature drastically.
  • the hot gaseous refrigerant is then lead to the desuperheater 2, where the refrigerants temperature is lowered to just above the condensation temperature before it enters the condenser 4 where the gaseous refrigerant is condensed into a liquid refrigerant. Finally, the liquid refrigerant is cooled further in the subcooler 6 before the cycle is repeated.
  • the different functions in the heat exchanger 1 i.e. the desuperheater 2, condenser 4 and subcooler 6 are separated by means of a first separation plate 15 and a second separation plate 18.
  • functions could be separated by means of dedicated gaskets (not shown) arranged to guide the refrigerant flow between the two neighbouring functions.
  • gaskets are used instead of separation plates 15, 18, the desuperheater 2, condenser 4 and subcooler 6 could be formed as one big plate pack with coolant blocking means strategically arranged in one of the inlet cassette opening 26 and outlet cassette opening 27 where the gasket(s) is arranged - Inlet cassette opening 26 or outlet cassette opening 27 are shown and discussed in relation with fig. 4.
  • Fig. 3 shows a cross section through a dividable shell-and-plate heat exchanger 1, as seen from the side.
  • the shell 8 is formed as a single monolithic cylindrical tube to increase the strength of the shell 8 and reduce the risk of unwanted stress concentrations in the shell 8.
  • the shell 8 could also be formed by a number of shell parts welded together or as disclosed in fig. 3 by means of several shell parts 19, 20 bolted together to ensure that the shell 8 subsequently can be opened e.g. in case of maintenance and/or repair.
  • the fully welded desuperheater heat transfer plate pack, condenser heat transfer plate pack and subcooler heat transfer plate pack allows quick and easy removal and refitting in the shell 8, thus ensuring that process downtime is kept to a minimum.
  • the first separation plate 15 is arranged to extend out between the two shell parts 19, 20 in the joint. It is hereby possible to securely arrange the first separation plate 15 in a fixed position.
  • Fig. 4 shows an embodiment of a heat transfer plate 3, 5, 7 for a shell-and-plate heat exchanger 1, as seen from the front.
  • the plate 3, 5, 7 is welded back to back to another plate 3, 5, 7 to form a so-called cassette.
  • the plates 3, 5, 7 are welded along the outer periphery so that water entering the cassette at the inlet cassette opening 26 will only be able to exit the cassette through the outlet cassette opening 27.
  • a number of these cassettes are then welded together around the inlet cassette openings 26 and the outlet cassette openings 27 to form a desuperheater heat transfer plate pack, a condenser heat transfer plate pack or a subcooler heat transfer plate pack.
  • the coolant flow is then established inside the cassettes and the refrigerant flow is established across the outside of (i.e. between) the cassettes.
  • the plate 3, 5, 7 is primarily circular to fit into a circular shell 8 but in another embodiment the plates 3, 5, 7 could be formed differently to fit into a shell 8 of a different shape - such as oval or prolonged.
  • the plate 3, 5, 7 is provided with an embossed pattern of channels 29 so that when a cassette is formed the coolant can flow through these channels 29 from the inlet cassette opening 26 to the outlet cassette opening 27.
  • the embossed pattern also increases the surface area of the plate 3, 5, 7 thus increasing its heat transferring ability.
  • the plate 3, 5, 7 is provided with a peripheral cutting 28 both at the top and at the bottom of the plate 3, 5, 7 to allow the refrigerant to pass this plate along both the upper and the lower periphery while at the same time ensuring that the refrigerant does not pass along the sides of the plate 3, 5, 7 and ensuring that the plate 3, 5, 7 is firmly centred inside the shell 8.
  • the plates 3, 5, 7 - and thus the cassettes, and the plate packs - fits firmly inside the shell 8 to ensure correct refrigerant flow through and around the plates 3, 5, 7 but in another embodiment the plates 3, 5, 7, cassettes and /or plate packs could comprise gaskets or other form of sealing means ensuring correct flow through the shell 8.
  • the respective plate packs are also welded to the respective separation plates 15, 18 around the coolant passage openings 17, inlet cassette openings 26 and outlet cassette openings 27.

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

Abstract

La présente invention concerne un échangeur de chaleur à plaques et calandre (1) pour refroidir et condenser un réfrigérant circulant. L'échangeur de chaleur (1) comprend un désurchauffeur (2) pour abaisser la température du réfrigérant gazeux à une température supérieure à la température de condensation du réfrigérant, le désurchauffeur (2) étant formé d'un empilage de plaques de transfert thermique de désurchauffeur ondulées (3). Le désurchauffeur (2) est raccordé à un condenseur (4) pour condenser une partie principale du réfrigérant, le condenseur (4) étant formé d'un empilage de plaques de transfert thermique de condenseur ondulées (5). Le condenseur (4) est raccordé à un sous-refroidisseur (6) pour abaisser davantage la température du réfrigérant condensé, le sous-refroidisseur (6) étant formé d'un empilage de plaques de transfert thermique de sous-refroidisseur ondulées (7), et l'empilage de plaques de transfert thermique de désurchauffeur ondulées (3), l'empilage de plaques de transfert thermique de condenseur ondulées (5) ainsi que l'empilage de plaques de transfert thermique de sous-refroidisseur ondulées (7) étant agencés à l'intérieur de la même calandre continue commune (8). Le condenseur (4) et le sous-refroidisseur (6) sont raccordés par l'intermédiaire d'un réservoir de réfrigérant liquide (9) agencé au-dessous de l'empilage de plaques de transfert thermique de condenseur (5) et/ou l'empilage de plaques de transfert thermique de sous-refroidisseur (7), le réfrigérant condensé étant collecté dans le réservoir de réfrigérant liquide (9) depuis lequel le réfrigérant liquide continue de s'écouler jusqu'au sous-refroidisseur (6) par l'intermédiaire d'un conduit d'entrée de sous-refroidisseur (10). L'invention concerne en outre l'utilisation d'un échangeur de chaleur à plaques et calandre (1).
PCT/DK2014/050236 2013-08-27 2014-08-05 Échangeur de chaleur à plaques et calandre et utilisation d'un échangeur de chaleur à plaques et calandre Ceased WO2015028021A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US14/906,602 US20160161191A1 (en) 2013-08-27 2014-08-05 Shell-and-plate heat exchanger and use of a shell-and-plate heat exchanger
CN201480043801.4A CN105473958B (zh) 2013-08-27 2014-08-05 一种壳板式热交换器及壳板式热交换器的使用

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP13181858.5 2013-08-27
EP13181858.5A EP2843324B1 (fr) 2013-08-27 2013-08-27 Èchangeur de chaleur calandre-plaque et utilisation d'un échangeur calandre-plaque

Publications (1)

Publication Number Publication Date
WO2015028021A1 true WO2015028021A1 (fr) 2015-03-05

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PCT/DK2014/050236 Ceased WO2015028021A1 (fr) 2013-08-27 2014-08-05 Échangeur de chaleur à plaques et calandre et utilisation d'un échangeur de chaleur à plaques et calandre

Country Status (6)

Country Link
US (1) US20160161191A1 (fr)
EP (1) EP2843324B1 (fr)
CN (1) CN105473958B (fr)
DK (1) DK2843324T3 (fr)
ES (1) ES2848207T3 (fr)
WO (1) WO2015028021A1 (fr)

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EP3236188B1 (fr) * 2016-04-18 2018-12-19 Hamilton Sundstrand Corporation Échangeurs thermiques
EP3236190A1 (fr) * 2016-04-19 2017-10-25 HS Wroclaw Sp. z o.o. Échangeurs thermiques
FI127511B (en) 2016-12-19 2018-08-15 Vahterus Oy Evaporator and method for vaporizing the substance in the evaporator
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CN105473958B (zh) 2019-01-04
EP2843324B1 (fr) 2020-12-23
DK2843324T3 (da) 2021-03-08
US20160161191A1 (en) 2016-06-09
ES2848207T3 (es) 2021-08-05
EP2843324A1 (fr) 2015-03-04

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