EP0627308B1 - Dispositif pour équilibrer la température des éléments rotatifs dans des groupes imprimants - Google Patents

Dispositif pour équilibrer la température des éléments rotatifs dans des groupes imprimants Download PDF

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Publication number
EP0627308B1
EP0627308B1 EP94101700A EP94101700A EP0627308B1 EP 0627308 B1 EP0627308 B1 EP 0627308B1 EP 94101700 A EP94101700 A EP 94101700A EP 94101700 A EP94101700 A EP 94101700A EP 0627308 B1 EP0627308 B1 EP 0627308B1
Authority
EP
European Patent Office
Prior art keywords
cold air
temperature
blower
control device
air
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.)
Expired - Lifetime
Application number
EP94101700A
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German (de)
English (en)
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EP0627308A2 (fr
EP0627308A3 (fr
Inventor
Hans-Joachim Kurz
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.)
Baldwin Gegenheimer GmbH
Original Assignee
Baldwin Gegenheimer GmbH
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 Baldwin Gegenheimer GmbH filed Critical Baldwin Gegenheimer GmbH
Publication of EP0627308A2 publication Critical patent/EP0627308A2/fr
Publication of EP0627308A3 publication Critical patent/EP0627308A3/fr
Application granted granted Critical
Publication of EP0627308B1 publication Critical patent/EP0627308B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/22—Means for cooling or heating forme or impression cylinders

Definitions

  • the invention relates to a temperature control device for rotary bodies in printing units according to the preamble of claim 1.
  • Such a temperature control device is known from Japanese Patent Application No. S 55-31915, Publication No. S 56-127 457 known.
  • the known temperature control device is used to cool inking rollers in printing machines for waterless offset printing. Cooling air supplied by a cooling unit is blown from a blow box onto one or more inking rollers.
  • the blow box is open on its side assigned to the inking roller and is provided with suction openings along the inside of its edge. Blown-out cold air is extracted via the suction openings and circulated through the cooling unit.
  • EP-A1-0 480 230 discloses a thermal controller for a printing form placed around a printing form cylinder for waterless offset printing.
  • a blow box is provided for blowing the printing form with tempered air. Inside the blow box there is a fan and a cooler for cooling the blown air generated by the fan. The cooler is supplied with coolant from a refrigeration system arranged externally from the blow box.
  • a controller is also provided, which controls the cooling of the cooler as a function of a temperature.
  • a plate cylinder temperature control device which consists of heat exchangers and fans through which cold water flows and which cools the air onto the pressure plate to be cooled blow.
  • the somewhat warmed cooling air which is formed in the area of the plate surface by the mixture of cold blown air and warm printing unit ambient air, is sucked back again.
  • the invention is intended to achieve the object of providing a temperature control device for rotary bodies, in particular printing cylinders or inking unit rollers or blanket cylinders of a printing unit, which requires less energy to generate the cold air and, at the same time, smaller tubes or hoses in diameter for supplying the cold air from the cold air generator to the blowing device than the known temperature control device, which is mentioned at the beginning.
  • Blown-out cold air is also sucked off in the known device, but is not returned to the blowing device, but to the cold air generator for renewed cooling.
  • the known device also has the disadvantage that the air returned to the cold air generator is heated on a relatively long flow path through the outside atmosphere or requires well-insulated lines.
  • the air deflected by the rotating body gets back into the blowing device in a very short way.
  • the vacuum required for the extraction of the blown-out air is generated according to the invention by a vacuum region formed in the blowing device.
  • the vacuum area can be generated by a blower contained in the blowing device, which accelerates the fresh cold air flow in the direction of the outer surface of the rotating body to be cooled.
  • a venturi canal in the blowing device be formed, through which the cold air flows and thereby creates a vacuum according to the Venturi principle. This negative pressure sucks in the blown-out cold air, which is deflected by the rotating body, and leads it back through the negative pressure area of the venturi channel into the cold air inflow.
  • the cold air generator generates cold air at a temperature that is dependent on another temperature or a setpoint.
  • the cold air is thus cooled to a specific cold air value by temperature control of ambient air, which can also be referred to as temperature control.
  • temperature control of ambient air
  • the relevant rotary body, onto which the cold air is blown can have a lower temperature than the cold air, as long as the printing unit has not yet reached its operating temperature. In this case the cold air heats up the rotating body in question.
  • the best printing results are achieved when the operating temperature of the printing form, which is located on the circumference of a printing cylinder, is 25 ° C or below.
  • the temperature control device according to the invention is particularly suitable for temperature control or cooling of printing cylinders in waterless offset printing.
  • the temperature control device according to the invention can also be used in wet printing for additional cooling of the printing cylinder or of rollers in the inking unit of a printing unit or for cooling a blanket cylinder.
  • the temperature control device according to the invention it is possible according to the invention, the temperature control device according to the invention to be used in addition to other cooling systems in a printing unit in order to be able to use the various temperature control or cooling systems alternatively or simultaneously, without the printing unit or parts thereof having to be converted when changing from one operating mode to another operating mode.
  • Each rotating body 6 is assigned a blowing device 8, which blows cold air 9 onto the outer surface 10 of the rotating body 6.
  • the cold air is generated by a cold air generator 12 and supplied to the blowing devices 8 via cold air supply lines 13 and 14.
  • the cold air supply lines consist of a distributor line 13 and branch lines 14 branching therefrom.
  • the cold air generator 12 contains an air inlet 16 in succession in the air flow direction with a filter 17 for sucking in and filtering fresh air 18, a unit 20 consisting of a cooler as a heat exchanger and a refrigeration system for supplying the cooler or heat exchanger with coolant, and a blower 22 for conveying the cold air via the cold air supply lines 13 and 14 to the blower device 8.
  • the cooling effect of the cold air 9 on the outer surface 10 of the rotary body 6 can be changed by changing the temperature of the Cold air and / or can be controlled or regulated by changing the conveying speed of the cold air as a function of a setpoint.
  • the setpoint value can be a temperature, for example, of the outer surface 10 of the rotating body 6 or of the cold air or of the refrigerant, which is used to cool the cold air.
  • the target value can be a variable value, which is stored, for example, in the form of a control curve in a computer control system.
  • the conveying speed of the cold air can be generated and changed by the blower 22 of the cold air generator 12 and / or a blower 24 which is located in the blowing device 8.
  • FIG. 3 A further developed embodiment of the blowing device 8 of FIG. 1 is shown in FIG. 3 and there designated 8/1.
  • the blowing device 8/1 or 8 has the shape of a box, which extends essentially over the entire length of the rotary body 6, is open to the rotary body 6 and has a narrow spacing gap at its edges 26 28 forms with the lateral surface 10 of the rotary body 6.
  • the blowing device 8 can, according to FIG. 4, contain several blowers 11 distributed over the length of the rotating body 6. Each blower 11 is distributed over the length of the blowing device 8 and thus also over the length of the rotary body 6 in different cooling zones 31, 32 and 33. In each cooling zone, the cooling effect of the cold air is changed by changing the flow rate of this cold air or by changing the temperature of the Cold air individually adjustable.
  • the flow rate can be adjusted individually by adjusting the speed of the blowers 11 or by adjusting adjustable flow restrictors 34, 35, 36.
  • the flow restrictors 34, 35 and 36 are located in cooling zone supply lines 37, 38 and 39, which lead from the branch line 14 to the cooling zones 31, 32 and 33.
  • a pressure regulator 40 can be located in the associated branch line 14.
  • the cooling effect can be regulated or controlled individually by changing the temperature of the cold air for the individual zones.
  • the blown air device 8/1 preferably consists of a box 42, in which a blown air duct 44 is formed radially to the lateral surface 10 of the rotary body 6, in the cold air inlet 46 of which the cold air feed lines 14 according to FIG. 1 or their cooling zone feed lines 37, 38 and 39 open radially to the rotating body 6 according to FIG. 4.
  • the blown air duct 44 has, downstream of its cold air inlet 46, an inlet section 48 which is narrowed in the shape of a nozzle, then an enlarged channel section 49 and subsequently an outlet section 50 which is narrowed in the shape of a nozzle.
  • the nozzle-shaped constricted outlet section 50 accelerates the cold air flow so that it strikes the lateral surface 10 of the rotary body 6 at high speed.
  • the inlet section 48 which is narrowed in the form of a nozzle, likewise produces an acceleration of the cold air flow. This accelerated cold air flow creates a vacuum in the expanded duct section 49 according to the Venturi principle.
  • the blower 11 is expanded Channel section 49 housed and causes a further acceleration of the cold air flow.
  • a first return duct 54/1 and 54/2 is formed separately by an intermediate wall 52 and 53, which together with the blown air duct 44 forms a first air recirculation circuit.
  • the first return channels 54/1 and 54/2 each have an upstream inlet 56 opposite the lateral surface 10 of the rotary body 6, and a downstream outlet 58 into the expanded channel section 49 immediately downstream of the nozzle-shaped inlet section 48, but upstream of the blower 11 of the blown air channel 44.
  • the cold air 60 of the blown air duct 44 is deflected by the outer surface 10 of the rotating body 6.
  • the cold air escapes in the form of leakage flows 62 through the gaps 28 between the lateral surface 10 and the downstream edges 64 of the walls 52 and 53 of the blown air duct 44.
  • a substantial part 65 of the cold air leakage flow 62 is created by the vacuum, which in the expanded duct section 49 after the Venturi principle and generated by the blower 11, sucked through the first return channels 54/1 and 54/2 into this expanded channel section 49 and admixed with the cold air inflow 66.
  • blowing device 8/2 shown in FIG. 5 is of the same design as the embodiment shown in FIG. 3, but has no blower 11. As a result, the entire conveying capacity for conveying the cold air from the blower 22 shown in FIG Cold air generator 12 are generated.
  • the first return channels 54/1 and 54/2 are delimited by outer channel walls 68 and 69, each of which is spaced apart run parallel to the inner channel walls 52 and 53. They have edges 70 which are spaced apart from the lateral surface 10 and form a downstream continuation 28/2 of the gap 28.
  • the part 72 of the cold air leakage stream 62 which is not sucked off through the first return duct 54/1 and 54/2, escapes through the gap sections 28/2 and is largely sucked off into a second return duct 74/1 and 74/2.
  • These second return channels 74/1 and 74/2 are formed on the one hand by the channel walls 68 and 69 of the first return channel 54/1 and 54/2 and also by an upper and lower box wall 76 and have an inlet 78 and are connected in terms of flow at their downstream outlet 80 via a suction line 82 to the air inlet 16 of the cold air generator 12, as is shown in FIG. 2.
  • the vacuum of the second return channels 74/1 and 74/2 required to extract the leakage air flow 72 is generated by the blower 22 of the cold air generator 12.
  • the two second return channels 74/1 and 74/2 are connected to one another in terms of flow by a channel 84. In a modified embodiment, however, a separate suction line 82 could be connected to every second return duct. If several printing units according to FIG. 2 are connected to a common cold air generator 12, the suction lines 82 of each printing unit can be connected individually or according to FIG. 2 via a collecting suction line 86 to the air inlet 16 of the cold air generator 12.
  • the suction effect of the fan 22 can be set so strongly that no cold air can escape from the box 42, but the entire remaining cold air leakage stream 72 is sucked off via the second return channels 74/1 and 74/2.
  • FIG. 2 identically shows the blowing device 8/1 of FIG. 3 in the individual printing units 1, 2, 3 and 4.
  • the outer second air recirculation circuit and the blowing device 8 shown in FIG. 1 are missing therefore has no second return channels 74/1 and 74/2, but only the first return channels 54/1 and 54/2.
  • two blowing devices 8 are provided which are each directed against another rotating body 6/2 and 6/3 and are connected to one another by a wall 90.
  • the two rotating bodies are, for example, printing cylinders of a printing unit. They are both on a common blanket roller 6/4. These three rotating bodies 6/2, 6/3 and 6/4 could also be inking unit rollers of a printing unit. Together with the two blowing devices 8 and their common wall 90, they delimit an intermediate space 92.
  • This intermediate space 92 is connected in terms of flow via at least one outlet opening 93 and a suction line 94 connected thereto to the air inlet 16 of an external cold air generator 12. Functionally, the intermediate space 92 corresponds to the second return duct 74/1 or 74/2 from FIG.
  • coolant flows through the heat exchanger or cooler 20 of the external cold air generator 12, which coolant flows from a refrigeration system 98 through coolant lines 99 to the heat exchanger and then back to the refrigeration system 98.
  • the coolant can be water or refrigerant, which is cooled in the refrigeration system by compression and subsequent expansion. A heat exchange takes place between the coolant and the air in the heat exchanger 20.
  • the blowing device 8, 8/1 or 8/2 can contain baffles or throttle valves for flow regulation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)
  • Electronic Switches (AREA)
  • Heating, Cooling, Or Curing Plastics Or The Like In General (AREA)

Claims (8)

  1. Dispositif pour équilibrer la température de corps rotatifs dans des mécanismes d'impression, notamment destiné à des cylindres d'impression, des cylindres d'encriers et/ou des cylindres à blanchets, comprenant au moins un dispositif d'insufflation (8, 8/1, 8/2) du type caisson, s'étendant le long du corps rotatif considéré (6, 6/2, 6/3, 6/4) et conçu pour projeter de l'air froid sur la surface périphérique (10) du corps rotatif considéré, pour l'essentiel sur toute sa longueur ; et un générateur (12) d'air froid qui est placé à l'extérieur du dispositif d'insufflation, est en liaison par écoulement avec ce dernier par l'intermédiaire d'au moins un conduit (13, 14) d'arrivée d'air froid, est destiné à engendrer l'air froid à une température déterminée, et présente une admission d'air (16) pour de l'air frais et une sortie d'air pour de l'air froid, avec au moins une soufflante (11, 22) pour convoyer l'air froid,
    caractérisé par
    au moins un premier circuit de remise en circulation de l'air, comportant un premier canal de retour (54/1, 54/2) pour évacuer de l'air froid (65), dévié par le corps rotatif, dans l'afflux d'air froid (66) fraîchement introduit dans le dispositif d'insufflation (8, 8/1, 8/2), par l'intermédiaire d'une zone de dépression (49) formée dans ledit dispositif d'insufflation,
    et par
    au moins un second circuit de remise en circulation de l'air, comportant un second canal de retour (74/1, 74/2 ; 93) pour l'évacuation d'une part (72) de l'écoulement de fuite de l'air froid qui s'échappe, en regard du premier canal de retour (54/1, 54/2), le long de la surface périphérique (10) du corps rotatif (6), et pour le renvoi de cette part de fuite (72) de l'air froid vers le côté aspiration du générateur (12) d'air froid.
  2. Dispositif d'équilibrage de température, selon la revendication 1,
    caractérisé par le fait
    que la zone de dépression (49), dans le dispositif d'insufflation, est formée par une soufflante (11) ou par un canal de Venturi (48, 49) par lequel le courant d'air froid (66) fraîchement introduit, circule en engendrant une dépression.
  3. Dispositif d'équilibrage de température, selon l'une des revendications 1 ou 2,
    caractérisé par le fait
    qu'il est prévu des moyens (11) par lesquels l'effet de refroidissement de l'air froid (66) est réglable individuellement par zones, sur la longueur du dispositif d'insufflation (8, 8/1, 8/2), le long du corps rotatif (6).
  4. Dispositif d'équilibrage de température, selon l'une des revendications 1 à 3,
    caractérisé par le fait
    que plusieurs dispositifs d'insufflation (8, 8/1, 8/2) sont en liaison par écoulement avec un générateur commun (12) d'air froid.
  5. Dispositif d'équilibrage de température, selon l'une des revendications 1 à 4,
    caractérisé par le fait
    que le second canal de retour (74/1, 74/2) présente une admission (78) d'évacuation d'air froid disposée, en vis-à-vis du corps rotatif (6), dans une zone du courant d'air froid dévié (62, 72) qui est située davantage en aval qu'une admission d'aspiration (56) du premier canal de retour (54/1, 54/2) par l'intermédiaire de laquelle de l'air froid, semblablement dévié, est évacué de la surface périphérique (10) du corps rotatif (6).
  6. Dispositif d'équilibrage de température, selon l'une des revendications 1 à 5,
    caractérisé par le fait
    que le dispositif d'insufflation (8, 8/1) est muni d'au moins une soufflante (11), en vue de l'accélération de l'air froid dirigé vers le corps rotatif (6).
  7. Dispositif d'équilibrage de température, selon l'une des revendications 1 à 6,
    caractérisé par le fait
    que le dispositif d'insufflation (8, 8/1) présente une zone (50) en forme de buse qui accélère l'air froid, se rétrécit dans la direction de l'écoulement, est dirigée vers le corps rotatif (6) et se trouve directement en vis-à-vis de ce dernier.
  8. Dispositif d'équilibrage de température, selon l'une des revendications 1 à 7,
    caractérisé par le fait
    que le générateur (12) d'air froid est pourvu d'une soufflante (22) pour le convoyage de l'air froid.
EP94101700A 1993-03-11 1994-02-04 Dispositif pour équilibrer la température des éléments rotatifs dans des groupes imprimants Expired - Lifetime EP0627308B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4307732 1993-03-11
DE4307732A DE4307732A1 (de) 1993-03-11 1993-03-11 Temperierungsvorrichtung für Rotationskörper in Druckwerken

Publications (3)

Publication Number Publication Date
EP0627308A2 EP0627308A2 (fr) 1994-12-07
EP0627308A3 EP0627308A3 (fr) 1995-01-18
EP0627308B1 true EP0627308B1 (fr) 1997-04-09

Family

ID=6482533

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Application Number Title Priority Date Filing Date
EP94101700A Expired - Lifetime EP0627308B1 (fr) 1993-03-11 1994-02-04 Dispositif pour équilibrer la température des éléments rotatifs dans des groupes imprimants

Country Status (5)

Country Link
US (1) US5588360A (fr)
EP (1) EP0627308B1 (fr)
JP (1) JP2795802B2 (fr)
AT (1) ATE151345T1 (fr)
DE (2) DE4307732A1 (fr)

Families Citing this family (16)

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DE4335097C2 (de) * 1993-10-14 1999-02-25 Baldwin Grafotec Gmbh Vorrichtung zum Temperieren von Druckmaschinenzylindern und -walzen
DE4440380A1 (de) * 1994-11-11 1996-05-15 Baldwin Gegenheimer Gmbh Geräteschrank zur Bereitstellung von Prozeßwasser
FR2740726B1 (fr) * 1995-11-08 1998-01-23 Heidelberg Harris Sa Dispositif de refroidissement de la surface du blanchet d'un groupe d'impression d'une machine rotative a imprimer
US5791247A (en) * 1995-12-18 1998-08-11 Kolb; Daniel L. Air system for controlling the discharge of printed material from a printing press and ink demulsifier
DE19926749B4 (de) * 1999-06-11 2008-11-20 Heidelberger Druckmaschinen Ag Farbwerk für eine Druckmaschine
DE19942118A1 (de) * 1999-09-03 2001-03-08 Technotrans Ag Verfahren zum Kühlen und Konditionieren von Luft für die Druckmaschinentemperierung sowie diesbezügliche Kühl- und Konditionierungsanordnung
US6851359B2 (en) * 2001-06-22 2005-02-08 Sparflex Offset printing method and device
DE10152593A1 (de) * 2001-10-24 2003-05-08 Koenig & Bauer Ag Einrichtung zur Bedruckstoff- und Druckwerkskühlung mittels gekühlter Blasluft an Bogenrotationsdruckmaschinen
DE20311534U1 (de) * 2003-07-26 2003-10-09 Roland Man Druckmasch Einrichtung zur Farbwerksabsaugung
DE10334657A1 (de) 2003-07-30 2005-02-17 Koenig & Bauer Ag Verfahren und Einrichtung zur Bedruckstoff- und Druckmaschinenkühlung
JP2006297734A (ja) * 2005-04-20 2006-11-02 Komori Corp 印刷機のエア吹き装置
JP5093086B2 (ja) * 2008-12-16 2012-12-05 パナソニック株式会社 スクリーン印刷機及びスクリーン印刷機の室内温度調節方法
JP6985761B2 (ja) * 2016-07-26 2021-12-22 株式会社富田技研 版胴冷却装置
JP6780841B2 (ja) * 2016-07-26 2020-11-04 株式会社富田技研 版胴冷却装置
JP7319714B2 (ja) * 2016-07-26 2023-08-02 株式会社富田技研 版胴冷却装置
JP6998616B2 (ja) * 2020-04-07 2022-01-18 三郷コンピュータホールディングス株式会社 印刷装置

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Also Published As

Publication number Publication date
ATE151345T1 (de) 1997-04-15
DE4307732A1 (de) 1994-09-15
EP0627308A2 (fr) 1994-12-07
DE59402340D1 (de) 1997-05-15
US5588360A (en) 1996-12-31
JP2795802B2 (ja) 1998-09-10
JPH06316053A (ja) 1994-11-15
EP0627308A3 (fr) 1995-01-18

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