EP0670461A1 - Tambour de congélation avec évaporateur incorporé et son procédé de fabrication - Google Patents

Tambour de congélation avec évaporateur incorporé et son procédé de fabrication Download PDF

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Publication number
EP0670461A1
EP0670461A1 EP95102633A EP95102633A EP0670461A1 EP 0670461 A1 EP0670461 A1 EP 0670461A1 EP 95102633 A EP95102633 A EP 95102633A EP 95102633 A EP95102633 A EP 95102633A EP 0670461 A1 EP0670461 A1 EP 0670461A1
Authority
EP
European Patent Office
Prior art keywords
chamber
freezing
jacket
knurling
evaporator
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.)
Withdrawn
Application number
EP95102633A
Other languages
German (de)
English (en)
Inventor
Renzo Grotti
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.)
Grb SNC Di Grotti Renzo & C
Original Assignee
Grb SNC Di Grotti Renzo & C
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 Grb SNC Di Grotti Renzo & C filed Critical Grb SNC Di Grotti Renzo & C
Publication of EP0670461A1 publication Critical patent/EP0670461A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F25C—PRODUCING, WORKING OR HANDLING ICE
    • F25C1/00—Producing ice
    • F25C1/12—Producing ice by freezing water on cooled surfaces, e.g. to form slabs
    • F25C1/14—Producing ice by freezing water on cooled surfaces, e.g. to form slabs to form thin sheets which are removed by scraping or wedging, e.g. in the form of flakes
    • 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
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites

Definitions

  • the present invention concerns a freezing drum with built-in evaporator and a method for the manufacture thereof.
  • the invention concerns a high performance freezing drum that is suitable to be used in machines for foodstuff processing, for instance in machine for ice-cream production.
  • a freezing drum with built-in evaporator includes a couple of tubular metal elements, coaxially positioned one inside the other, and a spiral-shaped metal strip with an edge inserted into a corresponding helical groove provided on the internal surface of the outer tubular element, whereas the opposite edge of the strip is put in tight contact with the external surface of the inner tubular element.
  • the freezing drum described in said previous patent application allowed to reduce the thickness of the freezing chamber and consequently improved the quickness of thermal exchange between the substance contained in the freezing chamber and the thermal exchange fluid circulating in the evaporator.
  • This indisputable advantage involves however a considerable manufacturing precision with very limited tolerances that, if not properly complied with, may jeopardize the efficiency of thermal exchange.
  • An object of the present invention is to provide a freezing drum with built-in evaporator allowing to obtain a better efficiency of thermal exchange versus those of the known type.
  • a further object of the present invention is to provide a freezing drum with built-in evaporator having a particularly sturdy structure even with reduced thicknesses of the wall of the freezing chamber.
  • a freezing drum of the type with built-in evaporator comprising a substantially cyclindrical external jacket made of metal, a cylindrical freezing chamber, made of metal as well, having a diameter lower than that of said jacket and placed in coaxial position within said jacket, as well as at least a spiral-shaped path provided in the hollow space between said jacket and said chamber, characterized in that said freezing chamber has a rough external surface.
  • the rough surface outside of the freezing chamber has the double advantage of creating turbulence in the fluid thermal exchange fluid lapping thereof, and of providing a larger superficial extent involved in the thermal exchange itself.
  • the invention also concerns a method to obtain such a freezing drum, that involves a machining of the external surface of the freezing chamber so as to allow the achievement of a rough surface.
  • the machining of the external surface of the freezing chamber may be carried out by chip removal or preferably may be carried out by plastic deformation of the material. In the latter case a knurling of the external surface of the freezing chamber is performed.
  • This kind of machining besides allowing the achievement of a rough surface, provides the considerable advantage of causing a so-called “surface hardening" of the material, namely an increase in superficial hardness that may result even double in respect of the hardness of the original material.
  • FIGS 1 and 2 show a freezing drum with built-in evaporator comprising an external jacket 1, a freezing chamber 2 housed inside the jacket 1 in coaxial position thereto and a helical path obtained by means of a spiral-shaped strip 3 positioned in the hollow space between the jacket 1 and chamber 2.
  • a through hole 16 may be provided for the drive shaft of the stirring means (not shown).
  • the evaporator built-in in the freezing drum is therefore constituted by at least a helical path defined by the internal surface of the jacket 1, by the external surface of the chamber 2 and by the strip 3 kept in tight contact between said surfaces.
  • the chamber 2 is made of stainless steel, whereas the jacket 1 and the strip 3 are made of soft iron.
  • the end portion 5 of the jacket 1 has an axial section having a diameter decreasing down to a value equal or slightly higher than the external diameter of the chamber 2. This allows to seal the hollow space between the jacket 1 and the chamber 2 at its bottom end by means of a continuous welding line 6 between the edge of the portion 5 and the external surface of the chamber 2.
  • the front end of the hollow space is sealed by an annular flange 7, previously welded on the chamber 2 along the continuous welding line 8, and by the subsequent welding along the line 9 between the flange 7 and the jacket 1.
  • the strip 3 is fixed, at least at its front end, by means of a welding spot 14 on the annular flange 7.
  • At least a couple of manifolds 12 and 13 is provided for the inlet and outlet of the thermal exchange fluid, for instance freon, that circulates within the hollow space.
  • the freezing chamber 2 has a rough external surface that can be obtained both by chip removal or by a plastic type machining of the material.
  • the superficial roughness allows to increase the turbulence of the thermal exchange fluid in the evaporator and increases the surface involved in the thermal exchange between the product contained in the chamber and the fluid circulating in the evaporator.
  • the roughness of the external surface 11 of chamber 2 is obtained by a "herringbone” knurling, namely by a double series of grooves slanting between each other.
  • Knurling be it parallel or "herringbone” consists in a plastic machining of the material that causes a "superficial hardening" of the treated surface. This provides the surface with a higher hardness, even more than double, in respect to that of the original material and allows to obtain a high resistance to mechanical stresses, to which the freezing chamber 2 is usually submitted, even for limited thicknesses of the wall of the chamber itself.
  • the improvement in the thermal exhchange efficiency through the wall of the freezing chamber 2 compensates the performance loss, though negligible, due to possible blow-by of the fluid of thermal exchange between contiguous sections of the evaporator.
  • the roughness of the surface itself jeopardizes the perfect sealing between the contiguous sections of the evaporator.
  • the amount of fluid not following the helical path, but flowing from a section to the subsequent one through the gaps present between the strip 3 and the external surface of the chamber 2 causes a definitely negligible performance loss if compared to the considerable performance increase due to the superficial roughness.
  • Figure 3 schematically shows the profile of a knurling tool with the characteristic factors that cause the configuration obtainable on the treated surface.
  • Said factors are in particular the pitch "p" equal to the distance between two consecutive grooves (see also figures 4 and 5) that generally varies as a function of the diameter of the piece to be machined; the notching angle “alpha” ranging between 50 and 90 degrees as a function of the hardness of the material to be treated, more precisely increasing as the material hardness decreases; finally the height “h” depending both on the angle “alpha” and the pitch "p".
  • the pitch "p" equal to the distance between two consecutive grooves (see also figures 4 and 5) that generally varies as a function of the diameter of the piece to be machined
  • the notching angle “alpha” ranging between 50 and 90 degrees as a function of the hardness of the material to be treated, more precisely increasing as the material hardness decreases
  • the height “h” depending both on the angle "alpha” and the pitch "p.
  • Figure 4 shows an enlargement of a portion of the external surface 11 of the freezing chamber 2. This is obtained by means of knurling tools consisting of a couple of washers having helical grooves slanting at respectively opposite directions to an angle beta. The grooves will therefore result to be slanting by an angle beta in respect of the axis 15 of the chamber 2, while they will be slanting between each other by an angle equivalent to 2beta. In the example of figure 4 the angle beta is about 30 degrees.
  • Figure 4A shows a section of the wall of the freezing chamber where, following the knurling machining, the thickness "S" of the original wall (represented by the profile with dashed line) is increased by a certain value "ds" corresponding to the maximum points of the external profile.
  • ds thickness of the original wall
  • Figures 5 and 5A show examples of parallel knurling such as the one used for the freezing chamber in figure 1.
  • the direction of grooves is substantially parallel to the axis 15 of the chamber 2.
  • the relations existing between "p" and “ds" are the same as those already mentioned for the treatment with herringbone knurling.
  • the increase in the external diameter of the chamber 2 contributes to increasing the mechanical resistance of the chamber itself even for relatively limited thicknesses of the original material.
  • the efficiency of the thermal exchange is also enhanced thanks to the increasing extent of the surface lapped by the fluid of thermal exchange.
  • the strip 3 is then wound up helicoidally onto the surface of chamber 2 as far as its opposite end where it is cut and possibly fixed by means of another welding spot.
  • the jacket 1 is then thermally enlarged and inserted externally onto the chamber-strip assembly.
  • the subsequent cooling of the jacket 1 allows the free edge of the strip 3 to come in tight contact with the external surface of the chamber 2 and with the internal surface of jacket 1.
  • the sealing between jacket 1 and chamber 2 in correspondence to their ends is obtained by means of a continuous welding line 9 between the jacket 1 and the flange 7, and a continuous welding line 6 between the end portion 5 of the jacket 1 and the external surface of the chamber 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Drying Of Solid Materials (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP95102633A 1994-03-04 1995-02-24 Tambour de congélation avec évaporateur incorporé et son procédé de fabrication Withdrawn EP0670461A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMI940382A IT1273366B (it) 1994-03-04 1994-03-04 Cilindro di congelamento con evaporatore incorporato e metodo per la sua fabbricazione
ITMI940382 1994-03-04

Publications (1)

Publication Number Publication Date
EP0670461A1 true EP0670461A1 (fr) 1995-09-06

Family

ID=11368047

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95102633A Withdrawn EP0670461A1 (fr) 1994-03-04 1995-02-24 Tambour de congélation avec évaporateur incorporé et son procédé de fabrication

Country Status (2)

Country Link
EP (1) EP0670461A1 (fr)
IT (1) IT1273366B (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1035387A1 (fr) * 1999-03-10 2000-09-13 Speciality Equipment Companies Inc. Système de réfrigération à haut rendement
WO2001007846A1 (fr) * 1999-07-28 2001-02-01 Iskerfi Hf Machine a glace
ES2166727A1 (es) * 2000-08-17 2002-04-16 Turro Agustin Mendoza Generador de hielo liquido.
EP1347257A2 (fr) * 2002-03-22 2003-09-24 Kee Voon Loke Serpentin d'évaporateur à haute efficacité d'une machine pour produire de la glace en écailles
EP1766302A1 (fr) * 2004-06-23 2007-03-28 Mikhail Mogilevsky Echangeur thermique pour le refroidissement des liquides
WO2012092929A1 (fr) 2011-01-06 2012-07-12 Tetra Laval Holdings & Finance S.A. Surface optimisée pour cylindre de congélation

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH303791A (de) * 1952-07-02 1954-12-15 Doebeli Oscar Verdampfer für Absorptionskälteapparate.
US3893322A (en) * 1974-08-21 1975-07-08 Universal Oil Prod Co Method for providing improved nucleate boiling surfaces
EP0108364A1 (fr) * 1982-11-04 1984-05-16 Hitachi, Ltd. Surface de transfert de chaleur
US4514900A (en) * 1981-11-20 1985-05-07 Con Rad Industries, Inc. Apparatus to manufacture heat exchanger finned tube
US4991407A (en) * 1988-10-14 1991-02-12 Mile High Equipment Company Auger type ice flaking machine with enhanced heat transfer capacity evaporator/freezing section

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH303791A (de) * 1952-07-02 1954-12-15 Doebeli Oscar Verdampfer für Absorptionskälteapparate.
US3893322A (en) * 1974-08-21 1975-07-08 Universal Oil Prod Co Method for providing improved nucleate boiling surfaces
US4514900A (en) * 1981-11-20 1985-05-07 Con Rad Industries, Inc. Apparatus to manufacture heat exchanger finned tube
EP0108364A1 (fr) * 1982-11-04 1984-05-16 Hitachi, Ltd. Surface de transfert de chaleur
US4991407A (en) * 1988-10-14 1991-02-12 Mile High Equipment Company Auger type ice flaking machine with enhanced heat transfer capacity evaporator/freezing section

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1035387A1 (fr) * 1999-03-10 2000-09-13 Speciality Equipment Companies Inc. Système de réfrigération à haut rendement
US6253573B1 (en) 1999-03-10 2001-07-03 Specialty Equipment Companies, Inc. High efficiency refrigeration system
WO2001007846A1 (fr) * 1999-07-28 2001-02-01 Iskerfi Hf Machine a glace
ES2166727A1 (es) * 2000-08-17 2002-04-16 Turro Agustin Mendoza Generador de hielo liquido.
EP1347257A2 (fr) * 2002-03-22 2003-09-24 Kee Voon Loke Serpentin d'évaporateur à haute efficacité d'une machine pour produire de la glace en écailles
EP1347257A3 (fr) * 2002-03-22 2004-01-07 Kee Voon Loke Serpentin d'évaporateur à haute efficacité d'une machine pour produire de la glace en écailles
EP1766302A1 (fr) * 2004-06-23 2007-03-28 Mikhail Mogilevsky Echangeur thermique pour le refroidissement des liquides
EP1766302A4 (fr) * 2004-06-23 2013-12-25 Mikhail Mogilevsky Echangeur thermique pour le refroidissement des liquides
US9267741B2 (en) 2004-06-23 2016-02-23 Icegen Patent Corp. Heat exchanger for use in cooling liquids
US9995521B2 (en) 2004-06-23 2018-06-12 Icegen Patent Corp. Heat exchanger for use in cooling liquids
NO344837B1 (no) * 2004-06-23 2020-05-25 1807983 Ontario Ltd Varmeveksler for bruk til kjølevæsker
US11566830B2 (en) 2004-06-23 2023-01-31 Icegen Patent Corp. Heat exchanger for use in cooling liquids
WO2012092929A1 (fr) 2011-01-06 2012-07-12 Tetra Laval Holdings & Finance S.A. Surface optimisée pour cylindre de congélation

Also Published As

Publication number Publication date
IT1273366B (it) 1997-07-08
ITMI940382A1 (it) 1995-09-05
ITMI940382A0 (it) 1994-03-04

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