EP3384223A1 - Refroidisseur pour solides granulaires - Google Patents

Refroidisseur pour solides granulaires

Info

Publication number
EP3384223A1
EP3384223A1 EP16815939.0A EP16815939A EP3384223A1 EP 3384223 A1 EP3384223 A1 EP 3384223A1 EP 16815939 A EP16815939 A EP 16815939A EP 3384223 A1 EP3384223 A1 EP 3384223A1
Authority
EP
European Patent Office
Prior art keywords
drum
cooler
coil
granular solids
drums
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.)
Granted
Application number
EP16815939.0A
Other languages
German (de)
English (en)
Other versions
EP3384223B1 (fr
Inventor
Stefano SOZZI
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.)
Simm Toscana Srl
Original Assignee
Simm Toscana Srl
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 Simm Toscana Srl filed Critical Simm Toscana Srl
Publication of EP3384223A1 publication Critical patent/EP3384223A1/fr
Application granted granted Critical
Publication of EP3384223B1 publication Critical patent/EP3384223B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0472—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being helically or spirally coiled
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/06—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
    • 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
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • F28D11/04—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller performed by a tube or a bundle of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0016—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F28F13/125—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation by stirring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/008—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using scrapers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F5/00—Elements specially adapted for movement
    • F28F5/02—Rotary drums or rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F5/00—Elements specially adapted for movement
    • F28F5/04—Hollow impellers, e.g. stirring vane
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F5/00—Elements specially adapted for movement
    • F28F5/06—Hollow screw conveyors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0045—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for granular materials

Definitions

  • the present invention relates to a cooler of the type as recited in the preamble of Claim 1 .
  • the present invention relates to a device for cooling granular solids and, in particular, powders.
  • coolers currently consist of a rotating drum defining an inner chamber to house the granular solids to be cooled; a jet of cold air that cools the granular solids as it flows through the drum; and a rotation apparatus that, by turning the drum, allows the granular solids to be cooled in a uniform manner by the cold air.
  • the prior art described above has a number of significant drawbacks.
  • a first important drawback consists in the fact that the prior art coolers have a limited cooling capacity and the granular solids must therefore be kept in the drum for a long time.
  • This aspect is due to the fact that the flow of cold air is only able to cool a limited portion of the inside surface. As a result, the granular solids are almost exclusively only cooled when they come into contact with said limited portion of drum.
  • Another drawback thus lies in the fact that, to cool large volumes of granular solids and, in particular, powders, several coolers and/or very large coolers must be used.
  • a further drawback is that the known coolers are low in efficiency and thus high in energy consumption.
  • Another no less important drawback lies in the fact that injecting cold air into a rotating drum requires the use of complex solutions which increase the cost of the cooler and are frequently subject to breakdowns as a result of which the cooler must be stopped.
  • the technical purpose of the present invention is to devise a cooler for granular solids that substantially overcomes the drawbacks mentioned above.
  • one important aim of the invention is to provide a cooler that is efficient and, thus, characterised by a high cooling capacity.
  • Another important aim of the invention is to provide a cooler that is compact in size.
  • a further aim of the invention is to obtain a cooler for granular solids that is highly efficient and, thus, has low energy consumption.
  • a no less important aim of the invention is to provide a cooler of simple construction, that is cost effective and highly reliable.
  • Fig. 1 shows a cooler according to the invention
  • Fig. 2 shows a front view of a cooler
  • Fig. 3 illustrates a section of an assembly of the cooler
  • Fig. 4 shows a detail of the cooler.
  • measurements, values, forms and geometric data such as perpendicularity and parallelism
  • terms such as “about” or other similar terms such as “practically” or “substantially”
  • such terms when associated with a value, preferably indicate a difference of not more than 10% of said value.
  • reference numeral 1 globally denotes the cooler according to the invention.
  • the cooler 1 defines a longitudinal axis 1a and, appropriately, two opposite faces, that is to say a front face 1 b and a rear face 1 c axially spaced with respect to one another.
  • axially and other similar terms such as “axial” define a direction, a length calculated substantially along the axis 1 a.
  • the cooler 1 comprises a first drum 2 suitable to receive the granular solids entering the cooler 1 ; a second drum 3 suitable to receive the granular solids in output from the first drum 2 and from which the granular solids leave the cooler 1 ; a first coil 4 enveloping the first drum 2; a second coil 5 enveloping the second drum 3; a cooling liquid passing through the coils 4 and 5; and, preferably, a pipe connecting the drums 2 and 3 suitable to allow the liquid to flow out of the second coil 5 and into the first coil 4.
  • the cooling liquid is water.
  • the first drum 2 defines a first main barycentric axis of extension practically parallel and, in particular, coincident with the longitudinal axis 1 a.
  • It is substantially cylindrical and has a ratio of length to diameter that is practically greater than 1 , in detail, substantially comprised between 1 .5 and 3.5 and, more precisely between 2.5 and 3.
  • the diameter of the first drum 2 is practically smaller than 2.5 m and, in detail, than 2 m and, preferably, substantially comprised between 0.3 m and 1 m.
  • the length of the first drum 2 is practically greater than 0.5 m and, in detail, than
  • the first drum 2 comprises a first hollow body 21 defining, for the first drum 2, a loading section 2a and an output section 2b of the granular solids; and a first inner auger 22 integral with the inner side surface of the first hollow body 21 and suitable to move the granular solids from the loading section
  • the first body 21 is a hollow cylinder.
  • the sections 2a and 2b are axially spaced.
  • the loading section 2a is proximal to the front face 1 b and the output section 2b is proximal to the rear face 1 c (Fig. 3).
  • the loading section 2a is identifiable in the bottom surface of the first drum 2.
  • the output section 2b is identifiable in the bottom surface of the first drum 2.
  • the output section 2b (Fig. 3) comprises one or more openings obtained along a ring of the first drum 2 distal to the loading section 2a.
  • the first auger 22 comprises a helical element extending along the longitudinal axis 1 a and suitable to move the granular solids along said axis 1 a defining a first direction of advancement 2c.
  • the second drum 3 defines a second main barycentric axis of extension practically parallel to and, in particular, coincident with the axis 1 a.
  • the drums 2 and 3 define barycentric axes of preferred extension substantially coincident with one another and, in detail, with the longitudinal axis 1 a.
  • the second drum 3 is substantially cylindrical and has a ratio of length to diameter that is practically greater than 1 , in detail, substantially comprised between 1 and 3 and, more precisely between 2.5 and 2.
  • the diameter of the second drum 3 is practically smaller than 3 m and, in detail, than 2 m and, preferably, substantially comprised between 0.7 m and 1 .5 m.
  • the length of the second drum 3 is practically greater than 0.5 m and, in detail, than 1 .5 m and, preferably, practically comprised between 2.5 m and 3 m.
  • the second drum 3 comprises a second hollow body 31 suitable to receive the granular solids in output from the first drum 2 and defining, for the second drum 3, a discharge section 3a of the granular solids; and a second inner auger 32 integral with the inner side surface of the second hollow body 31 and suitable to move the granular solids arriving from the first drum 2 towards the discharge section 3a.
  • the discharge section 3a is proximal to the front face 1 b. It is thus axially distal to the output section 2b and axially proximal to the loading section 2a.
  • the discharge section 3a is identifiable in a bottom surface of the second drum 3.
  • the discharge section 3a (Fig. 3) comprises one or more openings obtained along a ring of the second drum 3 axially distal to the output section 2a.
  • the second hollow body 31 may have, on the side opposite the loading section 3a and, in particular, in correspondence with the rear face 1 c, a closed base that defines the bottom of the drum 3.
  • the base of the second hollow body 31 may be distal to the open discharge section 3a as shown in Fig. 3.
  • the second hollow body 31 is a hollow cylinder.
  • first drum 2 It is suitable to at least partially house the first drum 2 so that the granular solids pass from the first drum 2 to the second drum 3 and, in detail, from the first hollow body 21 to the second hollow body 31 , preferably due to the force of gravity.
  • the first drum 2 is substantially entirely inside the second body 31 .
  • the second auger 32 is suitable to move the granular solids from the output section 2b, through which the granular solids pass from the first 2 to the second drum 3, to the discharge section 3a in order to leave the cooler 1 . It thus defines a second direction of advancement 3b of the granular solids that is opposite to the first direction of advancement 2c.
  • the second auger 32 comprises a helical element integral with the inner side surface of the second hollow body 31 and extending, in the opposite direction to the first auger 21 , substantially along the longitudinal axis 1 a.
  • the first coil 4 at least partially envelops the outer side surface of the first drum 2, that is, of the first hollow body 21 , so as to come into contact, appropriately directly, with said first body 21 to maximise heat exchange. In particular, it practically totally envelops the outer side surface of the first hollow body 21 .
  • the outer side surface is the side surface of the drum opposite that to which the auger is attached; whereas the term in direct contact means that said components come into contact with one another without the interposition of other elements.
  • the first coil 4 has a circular axis of extension substantially coincident with the first barycentric axis of preferred extension and, thus, the axis 1 a.
  • first drum 2 It is integral with the first drum 2 and, in detail, with the first hollow body 21 .
  • the first coil 4 is a double helix shape so as to have the first inlet mouth 41 and the first outlet mouth 42 of the cooling liquid from the first coil 4 proximal to one another.
  • the first inlet 41 and outlet 42 mouths are proximal to the rear face 1 c.
  • the first coil 4 is at least partially and, in particular, substantially completely housed inside the second drum 3.
  • the second coil 5 at least partially envelops the outer side surface of the second drum 3, that is, of the second hollow body 31 , so as to have the maximum surface in contact, appropriately directly, with said second body 31 , to maximise heat exchange.
  • the second coil 5 has a circular axis of extension practically coincident with the second barycentric axis and, thus, the axis 1 a.
  • the second coil 5 is integral with the second drum 3 and, in detail, with the second body 31 .
  • the second coil 5 is a double helix shape so as to have the second inlet mouth 51 and the second outlet mouth 52 of the liquid from the second coil 5 proximal to one another.
  • the second inlet 51 and outlet 52 mouths are proximal to the rear face 1 c.
  • first mouths 41 and 42 and the second mouths 51 and 52 are proximal to one another, more advantageously, to the rear face 1 c.
  • the second outlet mouth 52 is placed in fluidic through connection, appropriately by means of said connection pipe, with the first inlet mouth 41 so that the cooling liquid only passes through the first coil 4 after passing through the second coil 5.
  • the drum 1 may comprise a casing 6 suitable to at least partly contain the drums 2 and 3 and the coils 4 and 5; and, in some cases, a support structure 7 suitable to raise the casing 6 and, thus, the drums 2 and 3 and the coils 4 and 5 off the floor.
  • the casing 6 at least partially houses within it the drums 2 and 3 so that the loading 2a and discharge 3a sections and practically all of the coils 4 and 5 are visible.
  • It comprises a cylinder having an open base through which the loading 2a and discharge 3a sections are visible and, in detail, protrude; and a closed base 61 arranged in correspondence with the rear face 1 c from which at least the second inlet mouth 51 and the first outlet mouth 42 and, in detail, all four of the mouths 41 , 42, 51 and 52, protrude (Fig. 1 ).
  • the closed base 61 defines the bottom of the second cylinder 31 and, preferably, of the first cylinder 21 , as shown in Fig. 3.
  • the cooler 1 comprises at least one rotation member suitable to rotate the drums 2 and 3 and, in detail, the coils 4 and 5 about the longitudinal axis 1 a, leaving the casing 6 substantially stationary.
  • the cooler 1 may comprise a first rotation member suitable to rotate the first drum 2 and, in detail, the first coil 4 about the first barycentric axis; and a second rotation member suitable to rotate the second drum 3 and, in particular, the second coil 5 about the second axis, appropriately synchronously with the first member.
  • the drums 2 and 3 and, in detail, the hollow bodies 21 and 31 are integral with one another and the cooler 1 comprises a single rotation member 8 suitable to simultaneously rotate at least the drums 2 and 3 substantially about the axis 1 a.
  • the rotation member 8 is suitable to rotate the drums 2 and 3 and the coils 4 and 5 leaving the structure 7 practically stationary. Alternatively, it also leaves the casing 6 stationary.
  • the rotation member 8 illustrated in Fig. 2 comprises at least a motor 81, preferably an electric motor; a kinematic mechanism 82, such as a friction wheel, suitable to exploit the motion of the motor 81 to make the drums 2 and 3 and, preferably, the coils 4 and 5, rotate about the longitudinal axis 1 a.
  • a motor 81 preferably an electric motor
  • a kinematic mechanism 82 such as a friction wheel, suitable to exploit the motion of the motor 81 to make the drums 2 and 3 and, preferably, the coils 4 and 5, rotate about the longitudinal axis 1 a.
  • the rotation member 8 may comprise an idle support 83, for example a bearing, suitable to idly support the second drum 3.
  • the cooler 1 may comprise at least one hydraulic rotary joint 9 suitable to permit the passage of liquid between a fixed structure, in this case an external supply network, and a rotating structure, in this case the coils 4 and 5; and, preferably, connection pipes suitable to place the rotary joint 9 in fluidic through connection with an external network and with the coils 4 and 5.
  • it comprises a single rotary joint 9 suitable to allow the liquid to enter the cooler 1 and, thus, to enter the first coil 4 and to allow the liquid to flow out of the cooler 1 and, thus, out of the second coil 5.
  • the rotary joint 9 illustrated in Fig. 4 comprises a stator 91 suitable to be placed in fluidic through connection with the external network; a rotor 92 suitable to be placed in fluidic through connection with the coils 4 and 5; and, appropriately, sealing means suitable to prevent leakages of liquid in particular during the passage between the rotor 92 and the stator 91 .
  • the stator 91 is suitable to remain stationary during the operation of the cooler 1 whereas the rotor 92 is suitable to rotate about the longitudinal axis 1 a.
  • the stator 91 is integral with the support structure 7, whereas the rotor 92 is integral with the drums 2 and 3. More in particular, the rotor 92 is integrally connected to the casing 6 and, thus, to the drums 2 and 3.
  • the stator 91 comprises a body in which there are obtained a central stator duct 911 substantially extending along the longitudinal axis 1 a; a lateral stator duct 912 comprising, for example, a ring having an axis practically coincident with the longitudinal axis 1 a.
  • stator ducts 91 1 and 912 are suitable to be placed in fluidic through connection with the external network to allow the cooling liquid to flow into and out of the cooler 1 .
  • the central stator duct 91 1 comprises a cylindrical duct having an axis practically coincident with the longitudinal axis 1 a.
  • the lateral stator duct 912 comprises a ring having its axis practically coincident with the longitudinal axis 1 a.
  • the stator 91 further comprises connectors suitable to place the stator ducts 91 1 and 912 in fluidic through connection with the external network.
  • the rotor 92 is suitable to rotate, preferably idly, with respect to the stator 91 about the longitudinal axis 1 a.
  • It comprises a body in which there are obtained a central rotor duct 921 in fluidic through connection with the central stator duct 91 1 ; and a lateral rotor duct 912 is in fluidic through connection with the lateral stator duct 912.
  • the central rotor duct 921 substantially extends along the longitudinal axis 1 a. It comprises a cylindrical duct having an axis practically coincident with the longitudinal axis 1 a.
  • the lateral rotor duct 922 comprises a ring having an axis practically coincident with the longitudinal axis 1 a.
  • central rotor duct 921 and the lateral rotor duct 922 are in fluidic through connection one with the second inlet mouth 51 and the other with the first outlet mouth 42.
  • a granular solids discharge duct is arranged in correspondence with the loading section 2a and an external network is connected to the rotary joint 9 so as to allow a cooling liquid, appropriately water, to pass through the second coil 5 and, only then, through the first coil 4.
  • the rotation member 8 makes the drums 2 and 3, the coils 4 and 5, the casing 6 and the rotor 92 rotate, substantially about the longitudinal axis 1 a, leaving the structure 7 and the stator 91 substantially stationary.
  • the granular solids in output from the discharge duct, enter the first drum 2 through the loading section 2a. They fall onto the inside surface of the first hollow body 21 where they are received by the first inner auger 22.
  • the first auger 22 which is integral with the first hollow body 21 , rotates about the longitudinal axis 1 a and pushes the granular solids along the axis 1 a, in the first direction of advancement 2c, and towards the output section 2b.
  • the cooling liquid passing through the first coil 4 cools the first hollow body 21 and, thus, the granular solids passing over it.
  • the granular solids reach the output section 2b from where they pass owing to the force of gravity into the second hollow body 31 .
  • the granular solids are received by the second auger 32 which moves them in the second direction of advancement 3b, that is, in the opposite direction to the first direction of advancement 2c.
  • the granular solids slide along the inside surface of the second hollow body 31 and, when they arrive at the discharge section 3a, they leave the second drum 3 and, thus, the cooler 1 , owing to the force of gravity.
  • the invention achieves some important advantages.
  • a first important advantage lies in the fact that the cooler 1 has a high cooling capacity compared to those known in the prior art and the granular solids are thus cooled more quickly.
  • This aspect is due to the fact that since the coolant is a liquid, it is able to accumulate heat without heating as quickly as a gas. This aspect is enhanced by the use of a cooling process performed in two sequential stages, one in the first drum 2 and one in the second 3.
  • the use of two drums 2 and 3 allows the cooling liquid to cool the granular solids while they pass through the first drum 2 and the second drum 3 without becoming too hot and, thus, always remaining at a low temperature with a high cooling capacity.
  • the cooler 1 cools faster than the coolers of the same size currently available on the market.
  • a further advantage thus consists in the lower energy consumption of the cooler 1 compared to the known systems.

Landscapes

  • 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

L'invention concerne un refroidisseur (1) pour solides granulaires définissant un axe longitudinal (1a) et comportant un premier tambour (2) contenant une première vis sans fin (22) apte à déplacer les solides granulaires le long de l'axe longitudinal (1a) en définissant une première direction de progression (2c) des solides granulaires ; un premier serpentin (4) enveloppant le premier tambour (2) ; un deuxième tambour (3) contenant le premier tambour (2) et le premier serpentin (4), apte à recevoir les solides granulaires sortant du premier tambour (2) et contenant une deuxième vis sans fin (22) apte à déplacer les solides granulaires le long de l'axe longitudinal (1a) en définissant pour eux une deuxième direction de progression (3b) opposée à la première direction de progression (2c) ; un deuxième serpentin (5) enveloppant le deuxième tambour (3) ; et un liquide de refroidissement apte à passer au travers du deuxième serpentin (5) puis du premier serpentin (4).
EP16815939.0A 2015-12-01 2016-11-28 Refroidisseur pour solides granulaires Not-in-force EP3384223B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITUB2015A006040A ITUB20156040A1 (it) 2015-12-01 2015-12-01 Raffreddatore per solidi granulari
PCT/IB2016/057153 WO2017093876A1 (fr) 2015-12-01 2016-11-28 Refroidisseur pour solides granulaires

Publications (2)

Publication Number Publication Date
EP3384223A1 true EP3384223A1 (fr) 2018-10-10
EP3384223B1 EP3384223B1 (fr) 2019-09-18

Family

ID=55485196

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16815939.0A Not-in-force EP3384223B1 (fr) 2015-12-01 2016-11-28 Refroidisseur pour solides granulaires

Country Status (3)

Country Link
EP (1) EP3384223B1 (fr)
IT (1) ITUB20156040A1 (fr)
WO (1) WO2017093876A1 (fr)

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