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EP1702699B1 - Refroidisseur en forme de spirale - Google Patents

Refroidisseur en forme de spirale Download PDF

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Publication number
EP1702699B1
EP1702699B1 EP06005685A EP06005685A EP1702699B1 EP 1702699 B1 EP1702699 B1 EP 1702699B1 EP 06005685 A EP06005685 A EP 06005685A EP 06005685 A EP06005685 A EP 06005685A EP 1702699 B1 EP1702699 B1 EP 1702699B1
Authority
EP
European Patent Office
Prior art keywords
conveyor channel
cooling air
air
workpieces
conveyor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP06005685A
Other languages
German (de)
English (en)
Other versions
EP1702699A1 (fr
Inventor
Manfred Kreft
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.)
Joest GmbH and Co KG
Original Assignee
Joest GmbH and Co KG
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 Joest GmbH and Co KG filed Critical Joest GmbH and Co KG
Publication of EP1702699A1 publication Critical patent/EP1702699A1/fr
Application granted granted Critical
Publication of EP1702699B1 publication Critical patent/EP1702699B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D30/00—Cooling castings, not restricted to casting processes covered by a single main group

Definitions

  • the present invention relates to a spiral cooler and a method for cooling workpieces.
  • the WO 2004/058602 A2 discloses a spiral cooler with a coiled conveying channel for workpieces to be cooled by cooling air.
  • the cooling air is supplied by supply air ducts extending radially into the delivery channel, so that workpieces located in the delivery channel are exposed to the cooling air in the axial direction.
  • the suction takes place in the radial direction via corresponding, axially in the interior of the spiral cooler extending suction channels.
  • the said structure is very expensive.
  • the feed channels can be easily damaged by workpieces in the delivery channel.
  • the DE 41 06 712 C1 discloses a spiral conveyor in which gas, such as cooling air, is supplied by means of radially extending, tubular leads, which are connected to a central support tube, a work conveyor duct, so that the gas impinges on the workpieces substantially in the axial direction. The gas is discharged via the open coil end again. This structure is complicated.
  • the DE 42 28 543 C1 discloses a spiral conveyor in which gas for heat exchange several times radially supplied and removed. This structure is complicated.
  • the US 2,688,807 A discloses a spiral conveyor for drying workpieces by hot air in countercurrent.
  • a fan recirculates a part of the exhaust air into a heater for the supply air.
  • the present invention has for its object to provide a spiral cooler and a method for cooling workpieces, with a simple, robust construction of the spiral cooler is made possible with good cooling effect.
  • negative pressure is generated in the conveying channel. This prevents an undesired escape of dust and also makes it possible, for example, to open inspection openings during operation.
  • the negative pressure is generated in a very simple and effective manner - even with a high flow resistance for the cooling air in the delivery channel - preferably characterized in that a partial stream of cooling air is sucked out of the delivery channel and introduced at a higher speed back into the delivery channel. This takes place in the vicinity of the first end, ie in the vicinity of the task of the workpieces to be cooled or the exhaust device.
  • a negative pressure to the second end - output end - of the delivery channel can be generated.
  • the negative pressure or, if appropriate, the flow of ambient air sucked into the delivery channel can be controlled or regulated.
  • Another aspect of the present invention is to cool the workpieces in countercurrent by cooling air, wherein the cooling air to the conveying channel preferably only in the region of the second end for discharging the cooled workpieces and the exhaust air in the region of the first end, where to be cooled Workpieces are placed in the conveyor channel, preferably exclusively dissipated.
  • This allows a very simple and therefore cost-effective and also robust construction.
  • no axial or radial air ducts, collecting tanks or the like are required. Rather, an at least substantially continuous inner and outer walls of the conveyor channel can be realized.
  • Fig. 1 and 2 schematically show a proposed helical radiator 1 in a preferred embodiment.
  • the spiral cooler 1 is used for cooling of workpieces 2, in particular castings, such as brake discs or the like., As in Fig. 1 indicated.
  • the cooling is done by cooling air, if necessary, however, other gas can be used for cooling. Alternatively or additionally, additional media can be used for cooling.
  • the spiral cooler 1 has a preferably at least substantially coiled or spiral conveyor channel 3 for the workpieces 2.
  • the conveying channel 3 preferably represents a conveying path for the workpieces 2 that is closed on all sides Fig. 1 and 2 is the upper helical pitch of the conveyor channel 3 only for illustrative reasons on the left side each open - so not covered - shown.
  • the length of the conveyor channel 3 - ie the conveyor line for the workpieces 2 in the coil cooler 1, preferably more than 50 m.
  • the delivery channel 3 has in the illustrated example on five superposed Wendel réelle.
  • the spiral cooler 1 has an air supply 4 for supplying cooling air and an exhaust device 5 for discharging cooling air, as in Fig. 1 indicated.
  • Arrow Z indicates the feed direction of the cooling air.
  • Arrow A indicates the direction of the discharged exhaust air.
  • the workpieces 2 are placed at a first end 6 in the conveying channel 3 and delivered cooled at the other, second end 7 of the conveyor channel 3.
  • the air supply device 4 is connected in the region of the second end 7 to the conveyor channel 3 and the exhaust device 5 in the region of the first end 6 to the conveyor channel 3.
  • only an end-side supply and discharge of cooling air so that the usual in the prior art inlet and outlet channels for axial or radial supply and discharge of cooling air are dispensable.
  • the supply of cooling air in the region of the second end 7 is preferably carried out obliquely from above into the conveying channel, in particular by means of a nozzle, not shown, or the like.
  • the spiral cooler 1 is preferably designed such that ambient air is introduced together with cooling air into the second end 7, in particular sucked by injector action.
  • the proportion of ambient air in the total flow in the conveyor channel is preferably 10% to 70%, in particular substantially 50% or more. This allows, for example, a reduction in the dust load in the vicinity of the spiral cooler.
  • negative pressure is generated in the delivery channel 3, at least over a substantial area.
  • a partial flow of cooling air is sucked out of the delivery channel 3 and reintroduced into the delivery channel 3 at a higher speed.
  • the spiral cooler 1 for suction on a terminal 8, to which a fan 9 connects which then introduces the partial flow at a higher speed in the delivery channel 3, preferably at least substantially tangentially and / or horizontally, in particular by means of a nozzle 10th the like.
  • the branching or suction of the partial flow and re-introduction of the partial flow take place in the vicinity of the first end 6 of the conveying channel 3, in particular about a helical passage in front of the first end 6.
  • the distance of the nozzle 10 from the branch through the port 8 along the conveying channel 3 is preferably about 1/4 of a helical turn.
  • the desired negative pressure in the delivery channel 3 can be generated before the diversion or suction.
  • the negative pressure in the region upstream of the connection 8, ie upstream with respect to the flow direction of the cooling air is preferably at least 2000 Pa, in particular 2500 Pa or more.
  • the partial flow is preferably at least 50%, in particular about 70 to 90%, of the total cooling air flow in the conveying channel 3.
  • the higher speed with which the partial flow is introduced again into the conveying channel 3 is at least a factor of 2, preferably 3 or more, greater than the speed of the cooling air in the delivery channel 3 before the terminal. 8
  • an overpressure of about 500 Pa to 800 Pa can be set in the delivery channel 3. On the way to the first end 6, this pressure then drops to a negative pressure of about 200 Pa due to a corresponding suction through the exhaust device 5.
  • the flow velocity of the cooling air in the conveying channel 3 is on average preferably at least 10 m / s, in particular about 15 m / s or more.
  • a very turbulent or sufficiently turbulent flow can be achieved around the workpieces 2 with a correspondingly good cooling effect.
  • cooling air flow rate mass flow
  • this is preferably kept at least substantially constant.
  • the flow velocity of the cooling air then changes depending on the air temperature, ie in particular increases from the second end 7 to the first end 6 towards, if necessary, the mass flow in dependence on the required cooling capacity and / or to achieve a desired Flow rate or a desired flow rate range in the delivery channel 3 are controlled or regulated.
  • an unillustrated sensor for detecting the flow of supplied or sucked in ambient air is provided in the region of the second end 7.
  • the sensor thus detects in particular the volume flow or mass flow of the supplied ambient air.
  • This measured value serves as the actual value of a control loop.
  • the speed and / or the volume or mass flow of the diverted and re-introduced partial flow is varied, in particular the speed of the fan 9 is changed. This is preferably done via a frequency converter.
  • the injector effect of the partial flow can be adapted to the changing operating conditions and in particular a desired flow of ambient air: can be achieved in the delivery channel 3.
  • the exhaust device 4 or its suction can be controlled or regulated to allow adaptation to different operating conditions.
  • the spiral cooler 1 is preferably assigned at least one vibration generator 11 in order to vibrate the conveyor channel 3, in particular the entire spiral conveyor, and thereby to achieve the conveyance of the workpieces 2 through the conveyor channel 3.
  • two vibration generators 11 are provided, which generate the desired vibrations, for example via unbalanced shafts.
  • the delivery channel 3 is formed in helical radiator 1 by screw-miniature arranged bottom elements 12 which are arranged and held between preferably hollow cylindrical side walls.
  • a side wall is radial outside and a side wall radially disposed within the bottom elements 12 and the conveyor channel 3.
  • the side walls are preferably formed at least substantially without interruption, since no radial inlets or outlets as in the prior art are required.
  • closable openings 13 for inspections or the like are provided in the outer side wall. Due to the normally prevailing in the delivery channel 3 negative pressure these can also be opened during operation if necessary.
  • the screening device 14 is formed in particular by a perforated bottom element, below which a collecting tray 15, as in FIG Fig. 2 indicated, is arranged. Trapped particles can then be removed or discharged by means of a preferably arranged inside, axially extending channel 16 from the conveyor channel 3 to a bottom 17 of the spiral cooler 1 or other recording.
  • the supply of the workpieces 2 is preferably carried out by means of a in Fig. 1 schematically indicated, in particular encapsulated separation channel 19 or the like. However, a different supply of the workpieces 2 can take place.
  • the proposed helical radiator 1 has in particular an at least substantially cylindrical or hollow cylindrical shape.
  • the spiral cooler 1 is preferably divisible for transport or assembly purposes along a plane containing the cylinder or helix axis, as indicated by the connection 18.
  • the proposed helical radiator 1 is characterized in particular by a simple and therefore inexpensive construction.
  • the proposed helical radiator 1 is very robust, since - except for the discharge and supply of the partial flow - no other inlets and outlets along the conveyor duct 3 are required. This reduces or prevents possible damage due to workpieces 2 in the conveyor 3.
  • the invention is not limited to refrigeration. Rather, the supply and discharge of air or other gas for other purposes, such as a gas treatment or heat treatment serve. Accordingly, the term "helical radiator” in the context of the present invention to understand that it is a particular helical or spiral conveyor, wherein a supply and discharge of air or other gas for heat exchange with workpieces and / or other Purposes.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Screw Conveyors (AREA)

Claims (15)

  1. Refroidisseur hélicoïdal (1) pour le refroidissement de pièces à usiner (2) par de l'air de refroidissement, comprenant un canal de transport en hélice ou en spirale (3) pour les pièces à usiner (2), ainsi qu'un dispositif d'entrée d'air (4) et un dispositif de sortie d'air (5) pour l'air de refroidissement, les pièces à usiner (2) pouvant être introduites à une première extrémité (6) dans le canal de transport (3) et pouvant être évacuées à l'autre extrémité, à savoir la deuxième extrémité (7) du canal de transport (3), caractérisé en ce qu'un ventilateur (9) est attribué au refroidisseur hélicoïdal (1), pour pouvoir aspirer, avant la première extrémité (6), un courant partiel d'air de refroidissement hors du canal de transport (3) et le réintroduire à une vitesse supérieure dans le canal de transport (3) à proximité de la première extrémité (6), approximativement à une spire de vis avant la première extrémité (6), si bien qu'avant l'aspiration, on génère un vide dans le canal de transport (3).
  2. Refroidisseur hélicoïdal selon la revendication 1, caractérisé en ce que le dispositif d'entrée d'air (4) présente une buse de préférence réglable et/ou réalisée de telle sorte que de l'air de refroidissement est introduit en inclinaison par le haut dans le canal de transport (3) dans la zone de la deuxième extrémité (7).
  3. Refroidisseur hélicoïdal selon la revendication 1 ou 2, caractérisé en ce que le dispositif d'entrée d'air (4) est raccordé au canal de transport (3) dans la zone de la deuxième extrémité (7) et le dispositif de sortie d'air (5) est raccordé au canal de transport (3) dans la zone de la première extrémité (6), pour pouvoir refroidir les pièces à usiner (2) à contre-courant.
  4. Refroidisseur hélicoïdal selon l'une quelconque des revendications précédentes, caractérisé en ce que le refroidisseur hélicoïdal (1) est réalisé de telle sorte que l'on introduit de l'air ambiant conjointement avec l'air de refroidissement dans la deuxième extrémité (7), en particulier par aspiration à l'intervention d'un injecteur.
  5. Refroidisseur hélicoïdal selon l'une quelconque des revendications précédentes, caractérisé en ce que, dans la zone de la deuxième extrémité (7), est disposé un capteur pour enregistrer la pression régnant dans le canal de transport (3) et/ou le courant d'air ambiant introduit respectivement aspiré, en particulier pour commander ou pour régler le ventilateur (9).
  6. Refroidisseur hélicoïdal selon l'une quelconque des revendications précédentes, caractérisé en ce que, entre l'aspiration et la première extrémité (6), est disposé, dans le canal de transport (3), un dispositif de tamisage (14), en particulier pour séparer le sable ou d'autres particules du canal de transport (3).
  7. Refroidisseur hélicoïdal selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un générateur de vibrations (11) est attribué au refroidisseur hélicoïdal (1) pour transporter les pièces à usiner (2) en faisant vibrer le transporteur hélicoïdal (1) entre la première et la deuxième extrémité (7) dans le canal de transport (3).
  8. Procédé pour le refroidissement de pièces à usiner (2) au moyen d'air de refroidissement dans un refroidisseur hélicoïdal (1) comprenant un canal de transport (3), les pièces à usiner (2) étant introduites à une première extrémité (6) dans le canal de transport (3) et étant évacuées à l'autre extrémité, à savoir la deuxième extrémité (7) du canal de transport (3), caractérisé en ce qu'on aspire, avant la première extrémité (6), un courant partiel d'air de refroidissement hors du canal de transport (3) en particulier au moyen d'un ventilateur (9) et on le réintroduit à une vitesse supérieure dans le canal de transport (3) à proximité de la première extrémité (6), approximativement à une spire de vis avant la première extrémité (6), entre l'aspiration et la première extrémité (6), si bien qu'avant l'aspiration, on génère un vide dans le canal de transport (3).
  9. Procédé selon la revendication 8, caractérisé en ce qu'on introduit de l'air de refroidissement dans le canal de transport (3) dans la zone de la deuxième extrémité (7) et on l'évacue hors du canal de transport (3) dans la zone de la première extrémité (6), si bien que les pièces à usiner (2) sont refroidies par l'air de refroidissement à contre-courant.
  10. Procédé selon la revendication 8 ou 9, caractérisé en ce qu'on guide à titre exclusif, à la deuxième extrémité (7) de l'air de refroidissement à partir d'un dispositif d'entrée d'air (4), et/ou de l'air ambiant dans le canal de transport (3).
  11. Procédé selon l'une quelconque des revendications 8 à 10, caractérisé en ce qu'on introduit de l'air ambiant conjointement avec de l'air de refroidissement dans le canal de transport (3) dans la zone de la deuxième extrémité (7), la fraction de l'air ambiant représentant de 10 % à 70 % du courant total dans le canal de transport (3), et/ou dans lequel la fraction de l'air ambiant dans le courant total dans le canal de transport (3) est commandée ou réglée.
  12. Procédé selon l'une quelconque des revendications 8 à 11, caractérisé en ce que le courant partiel représente au moins 50 % du courant total d'air de refroidissement dans le canal de transport (3) et/ou en ce qu'on génère un vide d'au moins 2000 Pa dans la zone située avant l'aspiration dans le canal de transport (3).
  13. Procédé selon l'une quelconque des revendications 8 à 12, caractérisé en ce que la vitesse supérieure est supérieure, au moins du facteur 2, à la vitesse d'écoulement de l'air de refroidissement dans le canal de transport (3) avant l'aspiration.
  14. Procédé selon l'une quelconque des revendications 8 à 12, caractérisé en ce que le courant partiel, en particulier la vitesse de rotation du ventilateur (9), est utilisé comme valeur de commande ou de réglage pour commander ou pour régler le vide dans le canal de transport (3) dans la zone de la deuxième extrémité (7) et/ou l'aspiration de l'air ambiant dans la zone de la deuxième extrémité (7).
  15. Procédé selon l'une quelconque des revendications 8 à 13, caractérisé en ce la vitesse d'écoulement de l'air de refroidissement dans le canal de transport (3) s'élève à au moins 10 m/s, et/ou en ce que des particules telles que du sable sont séparées par tamisage, au moins dans certaines zones dans le canal de transport (3), et sont évacuées du canal de transport (3).
EP06005685A 2005-03-18 2006-03-20 Refroidisseur en forme de spirale Not-in-force EP1702699B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005013055A DE102005013055B4 (de) 2005-03-18 2005-03-18 Wendelkühler

Publications (2)

Publication Number Publication Date
EP1702699A1 EP1702699A1 (fr) 2006-09-20
EP1702699B1 true EP1702699B1 (fr) 2010-08-25

Family

ID=34716862

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06005685A Not-in-force EP1702699B1 (fr) 2005-03-18 2006-03-20 Refroidisseur en forme de spirale

Country Status (5)

Country Link
US (1) US20070125117A1 (fr)
EP (1) EP1702699B1 (fr)
AT (1) ATE478746T1 (fr)
DE (3) DE102005013055B4 (fr)
ES (1) ES2351049T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2493515C1 (ru) * 2012-03-07 2013-09-20 Федеральное Государственное бюджетное образовательное учреждение высшего профессионального образования "Воронежский государственный университет инженерных технологий" ("ВГУИТ") Комбинированная свч-конвективная сушилка
RU2806546C1 (ru) * 2022-08-23 2023-11-01 Федеральное государственное бюджетное образовательное учреждение высшего образования "Нижегородский государственный агротехнологический университет" (ФГБОУ ВО Нижегородский ГАТУ) Свч-конвективная сушилка сырья с поярусно расположенными тороидальными резонаторами

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130167562A1 (en) * 2011-12-31 2013-07-04 Air Liquide Industrial U.S. Lp Cryogenic spiral freezer
US20220170686A1 (en) * 2020-12-01 2022-06-02 Kps Global Llc Cooling system

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US2688807A (en) * 1952-06-13 1954-09-14 Ferro Corp Conveyer-drier
US3879857A (en) * 1974-02-27 1975-04-29 Amf Inc Spiral moisture equaliser and method of using same
CA1027799A (fr) * 1975-05-07 1978-03-14 Charles H. Staff Procede pour retarder la croissance des moisissures dans les pates de pizza partiellement cuites et les articles fabriques avec ces pates
US4775284A (en) * 1986-12-02 1988-10-04 General Kinematics Corporation Vertical mass flow conveyor
DE4106712C1 (en) * 1991-03-02 1992-06-25 Joest Gmbh + Co Kg, 4408 Duelmen, De Spiral conveyor with vibration drive - has tubular guide above conveyed material, whose gas outlets forming slit, pointing downwards to material
DE4228543C1 (de) * 1992-08-27 1993-11-25 Joest Gmbh & Co Kg Mittels eines Schwingantriebes angetriebener Wendelförderer
BR0317620B1 (pt) * 2002-12-23 2011-10-18 transportador espiral vibratório para transportar um objeto.

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2493515C1 (ru) * 2012-03-07 2013-09-20 Федеральное Государственное бюджетное образовательное учреждение высшего профессионального образования "Воронежский государственный университет инженерных технологий" ("ВГУИТ") Комбинированная свч-конвективная сушилка
RU2806546C1 (ru) * 2022-08-23 2023-11-01 Федеральное государственное бюджетное образовательное учреждение высшего образования "Нижегородский государственный агротехнологический университет" (ФГБОУ ВО Нижегородский ГАТУ) Свч-конвективная сушилка сырья с поярусно расположенными тороидальными резонаторами
RU2820685C1 (ru) * 2023-12-13 2024-06-07 Государственное бюджетное образовательное учреждение высшего образования Нижегородский государственный инженерно-экономический университет (НГИЭУ) Сушилка мясных отходов с СВЧ-энергоподводом в электроприводной цилиндрический ситовый резонатор

Also Published As

Publication number Publication date
DE502006007712D1 (de) 2010-10-07
EP1702699A1 (fr) 2006-09-20
DE202005005644U1 (de) 2005-06-30
DE102005013055A1 (de) 2006-09-28
US20070125117A1 (en) 2007-06-07
ATE478746T1 (de) 2010-09-15
ES2351049T3 (es) 2011-01-31
DE102005013055B4 (de) 2007-02-08

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