(19)
(11)EP 2 843 324 B1

(12)EUROPEAN PATENT SPECIFICATION

(45)Mention of the grant of the patent:
23.12.2020 Bulletin 2020/52

(21)Application number: 13181858.5

(22)Date of filing:  27.08.2013
(51)International Patent Classification (IPC): 
F25B 39/04(2006.01)
F25B 40/04(2006.01)
F28D 9/00(2006.01)
F25B 40/02(2006.01)
F28F 3/04(2006.01)

(54)

A shell-and-plate heat exchanger and use of a shell-and-plate heat exchanger

Mantel-Platten-Wärmetauscher und Verwendung eines Mantel-Platten-Wärmetauschers

Èchangeur de chaleur calandre-plaque et utilisation d'un échangeur calandre-plaque


(84)Designated Contracting States:
AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

(43)Date of publication of application:
04.03.2015 Bulletin 2015/10

(73)Proprietor: Johnson Controls Denmark ApS
8270 Højbjerg (DK)

(72)Inventor:
  • Bunde-Pedersen, Christian Per
    8270 Højbjerg (DK)

(74)Representative: Patentgruppen A/S 
Aaboulevarden 31, 4th Floor
8000 Aarhus C
8000 Aarhus C (DK)


(56)References cited: : 
EP-A2- 2 476 975
WO-A2-2010/114975
US-A- 5 129 449
WO-A2-2010/103190
FR-A1- 2 846 733
US-A1- 2009 100 854
  
      
    Note: Within nine months from the publication of the mention of the grant of the European patent, any person may give notice to the European Patent Office of opposition to the European patent granted. Notice of opposition shall be filed in a written reasoned statement. It shall not be deemed to have been filed until the opposition fee has been paid. (Art. 99(1) European Patent Convention).


    Description


    [0001] 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.

    Background of the Invention



    [0002] 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 round or oblong shell and plates ensure an even distribution of mechanical loads, without the stress concentrations that occur in the corners of rectangular plates. Thus, 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. From 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.

    [0003] Therefore, from US 5,129,449 it is known to integrate a desuperheater, a condenser and a subcooler in the same device. However this device is complex and not very efficient.

    [0004] Document WO2010/103190 discloses a shell-and-plate heat exchanger, whose shell encircles the whole stack of corrugated heat transfer plates. Documents EP2476975 and FR2846733 disclose plate heat exchangers with integrated condensers and subcoolers.

    [0005] It is therefore an object of the present invention to provide for a more simple and cost-efficient heat exchanger design.

    The invention



    [0006] The present invention is disclosed in the independent claims 1 and 14. Further embodiments are disclosed in the dependent claims.

    [0007] 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 shell-and-plate heat exchanger is characterized in that, the condenser and the subcooler are connected through a liquid refrigerant container arranged below the stack of condenser heat transfer plates and/or the stack of subcooler heat transfer plates, and 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.

    [0008] Pressure vessels like desuperheaters, condensers and subcoolers have to be pressure tested and approved by an independent authority before commercial use. This is both complex and expensive. Thus, by arranging the desuperheater, the condenser and the subcooler inside the same common continuous shell all three functions can be obtained by means of only one test and approval.

    [0009] Furthermore, by arranging the desuperheater, the condenser and the subcooler inside the same common continuous shell, complicated finishing arrangements and piping between the three can be avoided hereby reducing cost and simplifying installation. And the overall shell-and-plate heat exchanger arrangement is more compact hereby simplifying installation and increasing usability.

    [0010] The efficiency of the subcooler is severely reduced if the refrigerant is gaseous when entering the subcooler. And since the efficiency of 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.

    [0011] In an aspect of the invention, a conduit inlet opening of said subcooler inlet conduit is arranged at the bottom of said liquid refrigerant container.

    [0012] 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.

    [0013] In an aspect of the invention, said liquid refrigerant container is arranged outside said shell.

    [0014] Arranging the liquid refrigerant container outside the heat exchanger shell is advantageous in that it enables a simpler heat exchanger design.

    [0015] In an aspect of the invention, said shell encircles said desuperheater, said condenser and said subcooler.

    [0016] Making the shell encircle the desuperheater, the condenser and the subcooler is advantageous in that this design ensures a strong an durable shell capable of withstanding high internal pressure.

    [0017] In an aspect of the invention, 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.

    [0018] Arranging the refrigerant conduit inside the shell is advantageous in that complicated piping hereby can be avoided, thus reducing cost and simplifying installation.

    [0019] In an aspect of the invention, 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.

    [0020] 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.

    [0021] In an aspect of the invention, 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.

    [0022] 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 into the condenser, while at the same time ensuring that condensed liquid cannot pass from the condenser into the desuperheater. Hereby the efficiency of both components is increased.

    [0023] In an aspect of the invention, 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.

    [0024] 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 into the subcooler, hereby enabling that liquid and gaseous refrigerant can be separated to increase the functionality of the subcooler.

    [0025] In an aspect of the invention, said continuous shell is formed as a monolithic tube.

    [0026] 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.

    [0027] In an aspect of the invention, said continuous shell is formed by two or more connected shell parts.

    [0028] Forming the shell by two or more connected shell parts is advantageous in that hereby it is possible to subsequently open the shell e.g. in case of maintenance or repair work.

    [0029] In an aspect of the invention, said heat exchanger comprises endplates welded to both ends of said shell.

    [0030] Welding the endplates ensures that the pressure vessel is both stable and tight.

    [0031] In an aspect of the invention, said desuperheater heat transfer plates, said condenser heat transfer plates and said subcooler heat transfer plates are substantially identical.

    [0032] 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.

    [0033] In an aspect of the invention, 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 MPa and most preferred between 2.5 and 7.5 MPa.

    [0034] If the pressure, the shell is designed to withstand, is too low, the risk of leakage or even explosion is too big. However, if the pressure, the shell is designed to withstand, is too high the shell becomes too heavy and expensive. Thus, the present pressure ranges presents an advantageous relationship between safety and cost.

    [0035] The invention also relates to a use of a shell-and-plate heat exchanger according to any of the claims 1-13 for cooling and condensing a refrigerant in a refrigeration cycle.

    [0036] Using a shell-and-plate heat exchanger according to the present invention for cooling and condensing a refrigerant in a refrigeration cycle is advantageous in that it ensures a less expensive and a safer refrigeration cycle.

    Figures



    [0037] The invention will be explained further herein below with reference to the figures in which:
    Fig. 1
    shows an embodiment of the shell-and-plate heat exchanger, as seen from the side,
    Fig. 2
    shows an embodiment of the 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 according to the present invention, as seen from the front.

    Detailed description



    [0038] Figure 1 shows an embodiment of the shell-and-plate heat exchanger 1, as seen from the side.

    [0039] In this embodiment 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. Thus, in this embodiment the refrigerant and the coolant are arranged to flow countercurrently but in another embodiment the refrigerant and the coolant could flow in the same direction through the heat exchanger 1.

    [0040] Also, in another embodiment 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.

    [0041] According to the present invention 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 components.

    [0042] 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.

    [0043] The arrows on figure 1 illustrate a coolant flow through the coolant conduit 14 of the heat exchanger 1.

    [0044] First 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. In the condenser 4, condenser coolant blocking means 30 forces the coolant to run transversely towards the bottom of the condenser 4 and then longitudinally 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.

    [0045] Thus, in this embodiment 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.

    [0046] The differences between the flows of 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 to another (between gas and liquid form), while the coolants main purpose is to remove heat from the refrigerant.

    [0047] In this embodiment the coolant is water e.g. circulating through an additional external air cooled heat exchanger or transporting the absorbed heat to a particular place where it can be utilised.

    [0048] However, in another embodiment 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.

    [0049] In this embodiment 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 to simplify the 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, wherein making the design of the plates 3, 5, 7 in the heat exchanger different from each other.

    [0050] Likewise, in this embodiment all the plates 3, 5, 7, the shell 8 and the endplates 21 are all made from stainless steel because of its 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.

    [0051] Fig. 2 shows an embodiment of the shell-and-plate heat exchanger 1, as seen from the side.

    [0052] The arrows on figure 2 illustrate a refrigerant flow through the combined desuperheater 2, condenser 4 and subcooler 6.

    [0053] In this embodiment 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.

    [0054] 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.

    [0055] In 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.

    [0056] In this embodiment 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.

    [0057] In this embodiment 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.

    [0058] The shell-and-plate heat exchanger 1 according to the present invention 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.

    [0059] In the embodiment disclosed in figures 1-3 the different components in the heat exchanger 1 i.e. the desuperheater 2, the condenser 4 and the subcooler 6 are separated by means of a first separation plate 15 and a second separation plate 18. However, in another embodiment of the invention these components could be separated by means of dedicated gaskets (not shown) arranged to guide the refrigerant flow between the two neighbouring components . If 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.

    [0060] Fig. 3 shows a cross section through a dividable shell-and-plate heat exchanger 1, as seen from the side.

    [0061] In the embodiment disclosed in fig . 1 and 2 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. In another embodiment 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.

    [0062] In this embodiment 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.

    [0063] Fig. 4 shows an embodiment of a heat transfer plate 3, 5, 7 for a shell-and-plate heat exchanger 1 according to the present invention, as seen from the front.

    [0064] In this embodiment 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 and 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.

    [0065] In this embodiment the plates 3, 5, 7 are 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.

    [0066] In this embodiment 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.

    [0067] In this embodiment 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.

    [0068] In this embodiment 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.

    [0069] To ensure that the coolant do not mix with the refrigerant, 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.

    [0070] In the foregoing, the invention is described in relation to specific embodiments of shell-and-plate heat exchangers 1, desuperheaters 2, condensers 4, subcoolers 6 and other as shown in the drawings, but it is readily understood by a person skilled in the art that the invention can be varied in numerous ways within the scope of the appended claims.

    List



    [0071] 
    1. 1. Shell-and-plate heat exchanger
    2. 2. Desuperheater
    3. 3. Desuperheater heat transfer plates
    4. 4. Condenser
    5. 5. Condenser heat transfer plates
    6. 6. Subcooler
    7. 7. Subcooler heat transfer plates
    8. 8. Shell
    9. 9. Liquid refrigerant container
    10. 10. Subcooler inlet conduit
    11. 11. Conduit inlet opening
    12. 12. Bottom of liquid refrigerant container
    13. 13. Refrigerant conduit
    14. 14. Coolant conduit
    15. 15. First separation plate
    16. 16. Liquid refrigerant outlet
    17. 17. Coolant passage opening
    18. 18. Second separation plate
    19. 19. First shell part
    20. 20. Second shell part
    21. 21. Endplates
    22. 22. Coolant inlet
    23. 23. Coolant outlet
    24. 24. Refrigerant inlet
    25. 25. Refrigerant outlet
    26. 26. Inlet cassette opening
    27. 27. Outlet cassette opening
    28. 28. Peripheral cutting
    29. 29. Channel
    30. 30. Condenser coolant blocking means



    Claims

    1. A shell-and-plate heat exchanger (1) for cooling and condensing a circulating refrigerant, said heat exchanger (1) comprising
    a desuperheater (2) for lowering the temperature of the gaseous refrigerant to a temperature above the condensation temperature of said refrigerant, wherein said desuperheater (2) is formed by a stack of corrugated desuperheater heat transfer plates (3), said desuperheater (2) being connected to
    a condenser (4) for condensing said refrigerant, wherein said condenser (4) is formed by a stack of corrugated condenser heat transfer plates (5), said condenser (4) being connected to
    a subcooler (6) for further lowering the temperature of said condensed refrigerant, wherein said subcooler (6) is formed by a stack of corrugated subcooler heat transfer plates (7), and
    wherein said stack of corrugated desuperheater heat transfer plates (3), said stack of corrugated condenser heat transfer plates (5) and said stack of corrugated subcooler heat transfer plates (7) are arranged inside the same common continuous shell (8), characterised in that
    said condenser (4) and said subcooler (6) are connected through a liquid refrigerant container (9) arranged below said stack of condenser heat transfer plates (5) and/or
    said stack of subcooler heat transfer plates (7), wherein said condensed refrigerant is collected in said liquid refrigerant container (9) from which said liquid refrigerant continues into said subcooler (6) through a subcooler inlet conduit (10).
     
    2. A shell-and-plate heat exchanger (1) according to claim 1, wherein a conduit inlet opening (11) of said subcooler inlet conduit (10) is arranged at the bottom (12) of said liquid refrigerant container (9).
     
    3. A shell-and-plate heat exchanger (1) according to claim 1 or 2, wherein said liquid refrigerant container (9) is arranged outside said shell (8).
     
    4. A shell-and-plate heat exchanger (1) according to one or more of the preceding claims, wherein said shell (8) encircles said desuperheater (2), said condenser (4) and said subcooler (6).
     
    5. A shell-and-plate heat exchanger (1) according to one or more of the preceding claims, wherein said shell-and-plate heat exchanger (1) comprises a refrigerant conduit (13) through which said refrigerant is moved from said desuperheater (2) to said condenser (4) and wherein said refrigerant conduit (13) is arranged inside said shell (8).
     
    6. A shell-and-plate heat exchanger (1) according to one or more of the preceding claims, wherein said shell-and-plate heat exchanger (1) comprises a coolant conduit (14) extending continuously through said desuperheater (2), said condenser (4) and said subcooler (6) inside said common continuous shell (8).
     
    7. A shell-and-plate heat exchanger (1) according to one or more of the preceding claims, wherein said desuperheater (2) and said condenser (4) are separated by a first separation plate (15) arranged inside said common continuous shell (8) and wherein said first separation plate (15) comprises a refrigerant conduit (13) and a coolant passage opening (17).
     
    8. A shell-and-plate heat exchanger (1) according to one or more of the preceding claims, wherein said condenser (4) and said subcooler (6) are separated by a second separation plate (18) arranged inside said common continuous shell (8) and wherein said second separation plate (18) comprises only a coolant passage opening (17).
     
    9. A shell-and-plate heat exchanger (1) according to one or more of the preceding claims, wherein said continuous shell (8) is formed as a monolithic tube.
     
    10. A shell-and-plate heat exchanger (1) according to one or more of claims 1-8, wherein said continuous shell (8) is formed by two or more connected shell parts (19, 20).
     
    11. A shell-and-plate heat exchanger (1) according to one or more of the preceding claims, wherein said heat exchanger (1) comprises endplates (21) welded to both ends of said shell (8).
     
    12. A shell-and-plate heat exchanger (1) according to one or more of the preceding claims, wherein said desuperheater heat transfer plates (3), said condenser heat transfer plates (5) and said subcooler heat transfer plates (7) are substantially identical.
     
    13. A shell-and-plate heat exchanger (1) according to one or more of the preceding claims, wherein said common continuous shell (8) is a pressure vessel designed and/or approved to withstand a pressure between 0.7 and 15 MPa, preferably between 1.5 and 10 MPa and most preferred between 2.5 and 7.5 MPa.
     
    14. Use of a shell-and-plate heat exchanger (1) according to any of the preceding claims for cooling and condensing a refrigerant in a refrigeration cycle.
     


    Ansprüche

    1. Mantelplattenwärmeübertrager (1) zum Kühlen und Kondensieren eines zirkulierenden Kältemittels, wobei der Wärmeübertrager (1) umfasst: einen Enthitzer (2) zum Absenken der Temperatur des gasförmigen Kältemittels auf eine Temperatur oberhalb der Kondensationstemperatur des Kältemittels, wobei der Enthitzer (2) durch einen Stapel gewellter Enthitzerwärmeübertragungsplatten (3) ausgebildet wird, wobei der Enhitzer (2) verbunden ist miteinem Kondensator (4) zum Kondensieren des Kältemittels, wobei der Kondensator (4) durch einen Stapel gewellter Kondensatorwärmeübertragungsplatten (5) ausgebildet wird, wobei der Kondensator (4) verbunden ist mit einem Unterkühler (6) zum weiteren Absenken der Temperatur des kondensierten Kältemittels, wobei der Unterkühler (6) durch einen Stapel gewellter Unterkühlerwärmeübertragungsplatten (7) ausgebildet wird, und wobei der Stapel von gewellten Enthitzerwärmeübertragungsplatten (3), der Stapel von gewellten Kondensatorwärmeübertragungsplatten (5) und der Stapel von gewellten Unterkühlerwärmeübertragungsplatten (7) innerhalb desselben gemeinsamen durchgehenden Mantel (8) angeordnet sind; dadurch gekennzeichnet, dass der Kondensator (4) und der Unterkühler (6) durch einen Behälter (9) für flüssiges Kältemittel verbunden sind, der unter dem Stapel von Kondensatorwärmeübertragungsplatten (5) und/oder dem Stapel von Unterkühlerwärmeübertragungsplatten (7) angeordnet ist, wobei kondensiertes Kältemittel in dem Behälter (9) für flüssiges Kältemittel gesammelt wird, aus dem das flüssige Kältemittel durch eine Unterkühlereinlassleitung (10) in den Unterkühler (6) gelangt.
     
    2. Mantelplattenwärmeübertrager (1) nach Anspruch 1, wobei eine Leitungseinlassöffnung (11) der Unterkühlereinlassleitung (10) an dem Boden (12) des Behälters (9) für flüssiges Kältemittel angeordnet ist.
     
    3. Mantelplattenwärmeübertrager (1) nach Anspruch 1 oder 2, wobei der Behälter (9) für flüssiges Kältemittel außerhalb des Mantels (8) angeordnet ist.
     
    4. Mantelplattenwärmeübertrager (1) nach einem oder mehreren der vorhergehenden Ansprüche, wobei der Mantel (8) den Enthitzer (2), den Kondensator (4) und den Unterkühler (6) umgibt.
     
    5. Mantelplattenwärmeübertrager (1) nach einem oder mehreren der vorhergehenden Ansprüche, wobei der Mantelplattenwärmeübertrager (1) eine Kältemittelleitung (13) umfasst, durch die das Kältemittel von dem Enthitzer (2) zu dem Kondensator (4) bewegt wird und wobei die Kältemittelleitung (13) innerhalb des Mantels (8) angeordnet ist.
     
    6. Mantelplattenwärmeübertrager (1) nach einem oder mehreren der vorhergehenden Ansprüche, wobei der Mantelplattenwärmeübertrager (1) eine Kühlmittelleitung (14) umfasst, die sich kontinuierlich durch den Enthitzer (2), den Kondensator (4) und den Unterkühler (6) innerhalb der gemeinsamen durchgehenden Mantel (8) erstreckt.
     
    7. Mantelplattenwärmeübertrager (1) nach einem oder mehreren der vorhergehenden Ansprüche, wobei der Enthitzer (2) und der Kondensator (4) durch eine erste Trennplatte (15) getrennt sind, die in dem gemeinsamen durchgehenden Mantel (8) angeordnet ist, und wobei die erste Trennplatte (15) eine Kältemittelleitung (13) und eine Kühlmitteldurchgangsöffnung (17) umfasst.
     
    8. Mantelplattenwärmeübertrager (1) nach einem oder mehreren der vorhergehenden Ansprüche, wobei der Kondensator (4) und der Unterkühler (6) durch eine zweite Trennplatte (18) getrennt sind, die in dem gemeinsamen durchgehenden Mantel (8) angeordnet ist, und wobei die zweite Trennplatte (18) nur eine Kühlmitteldurchgangsöffnung (17) umfasst.
     
    9. Mantelplattenwärmeübertrager (1) nach einem oder mehreren der vorhergehenden Ansprüche, wobei der durchgehende Mantel (8) als ein monolithisches Rohr ausgebildet wird.
     
    10. Mantelplattenwärmeübertrager (1) nach einem oder mehreren der Ansprüche 1 bis 8, wobei der durchgehende Mantel (8) durch zwei oder mehr verbundene Mantelteile (19, 20) ausgebildet wird.
     
    11. Mantelplattenwärmeübertrager (1) nach einem oder mehreren der vorhergehenden Ansprüche, wobei der Wärmetauscher (1) Endplatten (21) umfasst, die an beide Enden des Mantels (8) geschweißt sind.
     
    12. Mantelplattenwärmeübertrager (1) nach einem oder mehreren der vorhergehenden Ansprüche, wobei die Enthitzerwärmeübertragungsplatten (3), die Kondensatorwärmeübertragungsplatten (5) und die Unterkühlerwärmeübertragungsplatten (7) im Wesentlichen identisch sind.
     
    13. Mantelplattenwärmeübertrager (1) nach einem oder mehreren der vorhergehenden Ansprüche, wobei der gemeinsame durchgehende Mantel (8) ein Druckbehälter ist, der ausgelegt und/oder zugelassen ist, um einem Druck zwischen 0,7 und 15 MPa, vorzugsweise zwischen 1,5 und 10 MPa und am stärksten bevorzugt zwischen 2,5 und 7,5 MPa standzuhalten.
     
    14. Verwendung eines Mantelplattenwärmeübertragers (1) nach einem der vorhergehenden Ansprüche zum Kühlen und Kondensieren eines Kältemittels in einem Kältekreislauf.
     


    Revendications

    1. Échangeur de chaleur à plaques et calandre (1) destiné à refroidir et condenser un réfrigérant en circulation, ledit échangeur de chaleur (1) comprenant un désurchauffeur (2) destiné à abaisser la température du réfrigérant gazeux à une température supérieure à la température de condensation dudit réfrigérant, dans lequel ledit désurchauffeur (2) est formé par un empilement de plaques de transfert de chaleur de désurchauffeur ondulées (3), ledit désurchauffeur (2) étant connecté à un condenseur (4) destiné à condenser ledit réfrigérant, dans lequel ledit condenseur (4) est formé par un empilement de plaques de transfert de chaleur de condenseur ondulées (5), ledit condenseur (4) étant connecté à un sous-refroidisseur (6) destiné à abaisser encore la température dudit réfrigérant condensé, dans lequel ledit sous-refroidisseur (6) est formé par un empilement de plaques de transfert de chaleur de sous-refroidisseur ondulées (7), et dans lequel ledit empilement de plaques de transfert de chaleur de désurchauffeur ondulées (3), ledit empilement de plaques de transfert de chaleur de condenseur ondulées (5) et ledit empilement de plaques de transfert de chaleur de sous-refroidisseur ondulées (7) sont agencés à l'intérieur de la même calandre continue commune (8), caractérisé en ce que ledit condenseur (4) et ledit sous-refroidisseur (6) sont connectés via un conteneur de réfrigérant liquide (9) agencé sous ledit empilement de plaques de transfert de chaleur de condensateur (5) et / ou ledit empilement de plaques de transfert de chaleur de sous-refroidisseur (7), dans lequel ledit réfrigérant condensé est collecté dans ledit conteneur de réfrigérant liquide (9) à partir duquel ledit réfrigérant liquide continue dans ledit sous-refroidisseur (6) à travers un conduit d'entrée de sous-refroidisseur (10).
     
    2. Échangeur de chaleur à plaques et calandre (1) selon la revendication 1, dans lequel une ouverture d'entrée de conduit (11) dudit conduit d'entrée de sous-refroidisseur (10) est agencée au fond (12) dudit conteneur de réfrigérant liquide (9).
     
    3. Échangeur de chaleur à plaques et calandre (1) selon la revendication 1 ou 2, dans lequel ledit conteneur de réfrigérant liquide (9) est agencé à l'extérieur de ladite calandre (8).
     
    4. Échangeur de chaleur à plaques et calandre (1) selon une ou plusieurs des revendications précédentes, dans lequel ladite calandre (8) enveloppe ledit désurchauffeur (2), ledit condenseur (4) et ledit sous-refroidisseur (6).
     
    5. Échangeur de chaleur à plaques et calandre (1) selon une ou plusieurs des revendications précédentes, dans lequel ledit échangeur de chaleur à plaques et calandre (1) comprend un conduit de réfrigérant (13) à travers lequel ledit réfrigérant est déplacé dudit désurchauffeur (2) audit condenseur (4) et dans lequel ledit conduit de réfrigérant (13) est agencé à l'intérieur de ladite calandre (8).
     
    6. Échangeur de chaleur à plaques et calandre (1) selon une ou plusieurs des revendications précédentes, dans lequel ledit échangeur de chaleur à plaques et calandre (1) comprend un conduit de réfrigérant (14) s'étendant en continu à travers ledit désurchauffeur (2), ledit condenseur (4) et ledit sous-refroidisseur (6) à l'intérieur de ladite calandre continue commune (8).
     
    7. Échangeur de chaleur à plaques et calandre (1) selon une ou plusieurs des revendications précédentes, dans lequel ledit désurchauffeur (2) et ledit condenseur (4) sont séparés par une première plaque de séparation (15) agencée à l'intérieur de ladite calandre continue commune (8) et dans lequel ladite première plaque de séparation (15) comprend un conduit de réfrigérant (13) et une ouverture de passage de réfrigérant (17).
     
    8. Échangeur de chaleur à plaques et calandre (1) selon une ou plusieurs des revendications précédentes, dans lequel ledit condenseur (4) et ledit sous-refroidisseur (6) sont séparés par une deuxième plaque de séparation (18) agencée à l'intérieur de ladite calandre continue commune (8) et dans lequel ladite deuxième plaque de séparation (18) comprend uniquement une ouverture de passage de réfrigérant (17).
     
    9. Échangeur de chaleur à plaques et calandre (1) selon une ou plusieurs des revendications précédentes, dans lequel ladite calandre continue (8) est formée sous la forme d'un tube monolithique.
     
    10. Échangeur de chaleur à plaques et calandre (1) selon une ou plusieurs des revendications 1 à 8, dans lequel ladite calandre continue (8) est formée par deux ou plus parties de calandre connectées (19, 20).
     
    11. Échangeur de chaleur à plaques et calandre (1) selon une ou plusieurs des revendications précédentes, dans lequel ledit échangeur de chaleur (1) comprend des plaques d'extrémité (21) soudées aux deux extrémités de ladite calandre (8).
     
    12. Échangeur de chaleur à plaques et calandre (1) selon une ou plusieurs des revendications précédentes, dans lequel lesdites plaques de transfert de chaleur de désurchauffeur (3), lesdites plaques de transfert de chaleur de condenseur (5) et lesdites plaques de transfert de chaleur de sous-refroidisseur (7) sont sensiblement identiques.
     
    13. Échangeur de chaleur à plaques et calandre (1) selon une ou plusieurs des revendications précédentes, dans lequel ladite calandre continue commune (8) est une cuve sous pression conçue et / ou certifiée pour résister à une pression comprise entre 0,7 et 15 MPa, de préférence entre 1,5 et 10 MPa et tout particulièrement entre 2,5 et 7,5 MPa.
     
    14. Utilisation d'un échangeur de chaleur à plaques et calandre (1) selon l'une quelconque des revendications précédentes pour refroidir et condenser un réfrigérant dans un cycle de réfrigération.
     




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    Cited references

    REFERENCES CITED IN THE DESCRIPTION



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    Patent documents cited in the description