EP4573035A1 - Ensemble rouleau de thermorégulation - Google Patents

Ensemble rouleau de thermorégulation

Info

Publication number
EP4573035A1
EP4573035A1 EP23797724.4A EP23797724A EP4573035A1 EP 4573035 A1 EP4573035 A1 EP 4573035A1 EP 23797724 A EP23797724 A EP 23797724A EP 4573035 A1 EP4573035 A1 EP 4573035A1
Authority
EP
European Patent Office
Prior art keywords
roller
tempering
rotary drive
arrangement according
fluid
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.)
Pending
Application number
EP23797724.4A
Other languages
German (de)
English (en)
Inventor
Christoph Dütsch
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.)
BHS Corrugated Maschinen und Anlagenbau GmbH
Original Assignee
BHS Corrugated Maschinen und Anlagenbau 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 BHS Corrugated Maschinen und Anlagenbau GmbH filed Critical BHS Corrugated Maschinen und Anlagenbau GmbH
Publication of EP4573035A1 publication Critical patent/EP4573035A1/fr
Pending legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H27/00—Special constructions, e.g. surface features, of feed or guide rollers for webs
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F23/00—Devices for treating the surfaces of sheets, webs, or other articles in connection with printing
    • B41F23/04—Devices for treating the surfaces of sheets, webs, or other articles in connection with printing by heat drying, by cooling, by applying powders
    • B41F23/0476—Cooling
    • B41F23/0479—Cooling using chill rolls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F31/00—Inking arrangements or devices
    • B41F31/002—Heating or cooling of ink or ink rollers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2301/00—Handling processes for sheets or webs
    • B65H2301/50—Auxiliary process performed during handling process
    • B65H2301/51—Modifying a characteristic of handled material
    • B65H2301/514—Modifying physical properties
    • B65H2301/5143—Warming
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2301/00—Handling processes for sheets or webs
    • B65H2301/50—Auxiliary process performed during handling process
    • B65H2301/51—Modifying a characteristic of handled material
    • B65H2301/514—Modifying physical properties
    • B65H2301/5144—Cooling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2403/00—Power transmission; Driving means
    • B65H2403/90—Machine drive
    • B65H2403/92—Electric drive
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/13—Details of longitudinal profile
    • B65H2404/136—Details of longitudinal profile with canals
    • B65H2404/1361—Details of longitudinal profile with canals with cooling/heating system
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2511/00—Dimensions; Position; Numbers; Identification; Occurrences
    • B65H2511/20—Location in space
    • B65H2511/21—Angle
    • B65H2511/212—Rotary position

Definitions

  • the invention relates to a tempering roller arrangement for tempering a moving material web.
  • the invention is also directed to a printing system with at least one such tempering roller arrangement.
  • the invention is based on the object of eliminating the disadvantages of the prior art.
  • a tempering roller arrangement is to be created which is particularly powerful in operation, i.e. has an extremely high tempering capacity. Furthermore, the tempering roller arrangement is to be particularly economical in operation.
  • a corresponding printing system is also to be supplied.
  • the material web is made of paper or cardboard. It can be single-layered or multi-layered.
  • the material web is preferably conveyed during operation, in particular continuously. It is, for example, a printing web, a printed web or a printable web. It is advantageous if it is a corrugated cardboard web or if a corrugated cardboard (web) can be made from it.
  • the roll necks preferably form a bearing axis, preferably horizontal.
  • the roll necks and the roll body are, for example, connected to one another in one piece. Alternatively, they are originally designed separately.
  • the rotary drive is designed as an electric rotary drive and is able to convert electrical power into a rotational or rotary movement. It is preferably gearless. Due to the rotary drive of the tempering roller, the tempering roller preferably forms a material web transport roller during operation. The tempering roller is advantageously able to transport or move the material web. It preferably allows the material web to be guided. It is able, for example, to redirect or deflect the material web.
  • the at least one tempering fluid inlet channel according to the dependent claim 2 preferably runs straight in the first roll neck, which is advantageous in terms of flow and allows a particularly large tempering fluid flow. Pressure losses are comparatively small. It is preferably closed on the circumference and advantageously circular in cross-section. A transverse dimension of the at least one tempering fluid inlet channel is preferably constant. It is expedient if the at least one tempering fluid inlet channel extends centrally axially in the first roll neck. Preferably only a single tempering fluid Inlet channel is present. A diameter of the tempering fluid inlet channel is preferably between 30% and 80% of an outer diameter of the first shaft journal.
  • the first roller journal is preferably (essentially) hollow-cylindrical.
  • the design according to subclaim 5 leads to a rotary drive that leaves the tempering fluid flow in the adjacent roll neck unaffected.
  • the rotary drive does not stand in the way as in tempering roller arrangements of the prior art and does not hinder or restrict the tempering fluid guide. It is expedient if the Rotor is arranged directly on the first or second roller journal and is connected thereto in a rotationally fixed manner for driving the tempering roller in rotation.
  • the tempering roller can advantageously be driven directly in rotation.
  • the rotary drive is preferably a direct drive.
  • the rotor and stator are each (essentially) hollow cylindrical.
  • the rotor is preferably designed as an internal rotor. It is expedient if it comprises a large number of rotor lamellas, in particular made of sheet metal.
  • the angle of rotation sensor according to subclaim 9 is preferably ring-shaped and runs around the roll neck carrying the rotary drive. During operation, the tempering fluid flows through the angle of rotation sensor and is preferably able to temper it. This is especially the case if the tempering fluid is a cooling fluid.
  • the bearing arrangement according to subclaim 10 is preferably designed as a rolling bearing arrangement, in particular a ball bearing arrangement, and comprises at least one bearing. It conveniently rotates around the roll journal carrying the rotary drive.
  • the bearing arrangement is preferably designed as a fixed bearing arrangement or a floating bearing arrangement. It is advantageous if the tempering fluid flows through the bearing arrangement during operation and is able to temper it. This is especially the case if the tempering fluid is a cooling fluid.
  • the tempering roller arrangement has at least one further bearing arrangement for supporting the tempering roller.
  • the at least one further bearing arrangement is preferably assigned to the other roller journal and preferably rotates around it. It is advantageously designed as a rolling bearing arrangement, in particular a ball bearing arrangement, and comprises at least one bearing. It is expedient if the tempering fluid flows through the further bearing arrangement during operation and is capable of tempering them. This is especially the case if the tempering fluid is a cooling fluid.
  • the design according to subclaim 11 is particularly space-saving. Furthermore, a particularly rigid connection is possible.
  • the housing protects, for example, the rotary drive, the bearing arrangement and the angle of rotation sensor. It is advantageously dimensionally stable and consists, for example, of metal, plastic or the like.
  • the housing can preferably be opened, for example for maintenance or assembly/dismantling work.
  • the design according to subclaim 13 allows a particularly high tempering fluid flow, which in turn leads to a particularly powerful tempering roller arrangement with regard to tempering.
  • Fig. 1 is a perspective partial sectional view of a tempering roller arrangement according to the invention
  • Fig. 2 essentially a longitudinal section through the rotary drive illustrated in Fig. 2, rotation angle sensor and the bearing arrangement of the tempering roller arrangement according to Fig. 1,
  • Fig. 3 is a view showing the illustrated tempering roller arrangement in its entirety in a tempering fluid circuit
  • Fig. 4 a simplified printing system with tempering rollers shown
  • a tempering roller arrangement 1 comprises a tempering roller 2 and a rotary drive 3 for driving the tempering roller 2 in rotation during operation, i.e. in particular during processing of a material web.
  • the tempering roller arrangement 1 also has a frame with a first wall 4, such as a side wall, and a second wall 5, such as a side wall.
  • the walls 4, 5 extend parallel to one another and vertically. They are arranged at a distance from one another and are supported against a floor (not shown), such as a hall floor.
  • the tempering roller 2 has a roller body 6. It also comprises a first roller neck 7 and a second roller neck 8, which are connected to the roller body 6, for example in one piece, and protrude from it in opposite directions.
  • the first roller neck 7 is (essentially) hollow cylindrical.
  • the second roller neck 8 is also (essentially) hollow cylindrical.
  • the roller necks 7, 8 are aligned with one another.
  • the roller body 6 and the roller necks 7, 8 form a longitudinal central axis 9, which also forms an axis of rotation of the tempering roller 2.
  • the roller body 6 in turn has a roller shell 10 which is circular in cross section and extends around the longitudinal center axis 9.
  • the roller shell 10 is hollow cylindrical and has a material web contact surface or material web guide surface for the material web on the outside.
  • the roller body 6 also comprises a first end part 11 and a second end part 12, which are each (essentially) circular disk-shaped and run parallel to one another.
  • the first end part 11 adjoins the end of the first roller journal 7 and the roller shell 10 and is connected to them, for example, as a one-piece.
  • the second end part 12 adjoins the end of the second roller journal 8 and the roller shell 10 and is connected to them, for example, as a one-piece.
  • the end parts 11, 12 and the roller shell 10 spatially delimit an interior space 13 radially outward and in the direction of the longitudinal center axis 9, which is cylindrical. Furthermore, the tempering roller 2 has an internal channel system for a tempering fluid.
  • an inlet channel 14 is formed in the first roll neck 7, which is circular in cross-section.
  • the inlet channel 14 extends straight along the longitudinal center axis 9 and around it. It is arranged centrally in the first roll neck 7 and is limited radially outward or circumferentially.
  • the inlet channel 14 forms an inlet or an inlet opening 15, which faces away from the first end part 11.
  • the inlet 15 is formed in a free end face of the first roll neck 7.
  • the inlet channel 14 extends into the first end part 11.
  • first radial channels 16 are arranged, which adjoin the first inlet channel 14 and run from there or opposite the longitudinal center axis 9 straight radially outwards. They are preferably circular in cross-section and, for example, arranged at a uniform angular distance from one another. They are limited on the circumference.
  • axial channels 18 are arranged, which are preferably arranged circumferentially at equal distances from one another around the longitudinal center axis 9.
  • the axial channels 18 extend parallel to the longitudinal center axis 9 and at a distance from it. They run straight and are in direct or indirect flow connection with the first radial channels 16. It is expedient if each axial channel 18 has a circular cross-section and is limited on the circumference. For example, the number of axial channels 18 and first radial channels 16 is identical.
  • a plurality of second radial channels 19 are arranged, which are in direct or indirect flow connection with the axial channels 18.
  • the second radial channels 19 extend straight and radially in relation to the longitudinal center axis 9. They are preferably circular in cross-section and limited on the circumference. For example, the number of axial channels 18 and second radial channels 19 is identical.
  • An outlet channel 20 is formed in the second roll neck 8, into which the second radial channels 19 open.
  • the outlet channel 20 is circular in cross-section. It extends straight along the longitudinal center axis 9 and around this.
  • the outlet channel 20 is arranged centrally in the second roll neck 8 and is limited radially outwards.
  • the outlet channel 20 forms an outlet 21 or an outlet opening.
  • the outlet 21 faces away from the second end part 12 and the inlet 15. It is formed in a free front side of the second roll neck 8.
  • the outlet 21 and inlet 15 are arranged at a distance from one another. They are arranged in different roll necks 7, 8.
  • the inlet channel 14 and outlet channel 20 are also arranged in different roll necks 7, 8.
  • the inlet channel 14 and outlet channel 20 are aligned with one another.
  • a tempering fluid such as water
  • the tempering fluid flows via the inlet channel 14 in the first roll neck 7 into the first end part 11.
  • it is deflected, preferably by (approx.) 90°, and then flows in the first end part 11 in the first radial channels 16 radially outwards, ie away from the longitudinal center axis 9.
  • the tempering fluid is then Transition region between the first radial channels 16 and the axial channels 18, preferably by (approx.) 90°, and then flows in the roll shell 10 in the axial channels 18 in the direction of the second end part 12.
  • the tempering fluid is then deflected in a third transition region between the axial channels 18 and the second radial channels 19, preferably by (approx.) 90°, and flows in the second end part 12 in the second radial channels 19 in the direction of the outlet channel 20 or the longitudinal center axis 9.
  • the tempering fluid is deflected, preferably by (approx.) 90°, and flows in the outlet channel 20 in the second roll neck 8 to the outlet 21, i.e. away from the inlet 15. There, the tempering fluid leaves the tempering roller 2.
  • the rotary drive 3 which is designed as an electric rotary drive, is arranged on the first roller journal 7 at a distance from the first end part 11. It extends (essentially) from the inlet 15 in the direction of the first end part 11.
  • the rotary drive 3 has an inner rotor 22, which is connected directly to the first roller journal 7 on the circumference or outside and is connected to it in a rotationally fixed manner, for example via a positive and/or non-positive connection, such as a screw connection, tongue and groove connection or the like.
  • the rotor 22 is hollow cylindrical and extends around the longitudinal center axis 9.
  • the rotary drive 3 also has an outer stator 23, which extends around the rotor 22 and rotates around it on the circumference.
  • the stator 23 is hollow cylindrical. There is a particularly high rigidity or rigid connection between the rotary drive 3 and the tempering roller 2, so that unwanted vibrations and target position deviations of the roller shell 6 during operation, for example in a printing operation, are prevented or reduced.
  • the tempering roller arrangement 1 comprises a housing 24 which is supported by the first wall 4 and arranged on the latter.
  • the housing 24 protrudes from the first wall 4 on both sides along the longitudinal central axis 9 and is closed during operation adjacent to the inlet 15 by a preferably removable cover 25 which is annular.
  • the housing 24 On the side facing the first end part 11, the housing 24 has an annular wall 26.
  • the housing 24 surrounds the first roller neck 7 at least in part on the circumference.
  • the rotary drive 3 is housed in the housing 24.
  • the stator 23 is carried by the housing 24. It is connected to the housing 24 on the inside, directly or indirectly, and is stationary.
  • the housing 24 also houses a (first) bearing arrangement 27, which is located between the first end part 11 and the rotary drive 3.
  • the bearing arrangement 27 is designed as a fixed bearing arrangement. It comprises a first ball bearing 28 and a second ball bearing 29, which are arranged adjacent to one another and, for example, abut against one another at the end. It is advantageous if the ball bearings 28, 29 are designed as angular contact ball bearings.
  • the bearing arrangement 27 is arranged adjacent to the first wall 4.
  • Each ball bearing 28, 29 has an inner ring 30 or 31, which sits on the first roller journal 7 and is connected to it in a rotationally fixed manner. ner, each ball bearing 28, 29 has an outer ring 32 or 33 or a bearing housing which extends around the respective inner ring 30 or 31 and is held by the housing 24. Each ball bearing 28, 29 also comprises a plurality of bearing balls 34 or 35 which are arranged between the inner ring 30 or 31 and outer ring 32 or 33 of the respective ball bearing 28 or 29 and are held by a corresponding cage.
  • the rotation angle sensor 36 is arranged adjacent to the bearing arrangement 27 and at a distance from the first end part 11.
  • the rotation angle sensor 36 sits on the first roller neck 7 and rotates around it. It is also housed in the housing 24 and extends adjacent to the wall 26.
  • the rotation angle sensor 36 has a stationary reading head which is advantageously firmly connected to the bearing housing of the adjacent ball bearing 29. It preferably also comprises a graduation carrier which is arranged adjacent to the reading head and is in a rotationally fixed connection with the first roller neck 7. For example, a further reading head is present or the rotation angle sensor 36 has a further reading head in order to compensate for concentricity tolerances of the first roller neck 7.
  • the rotary drive 3, the bearing arrangement 27 and the rotation angle sensor 36 are arranged along the longitudinal center axis 9 on/at the first roll neck 7.
  • a further (second) bearing arrangement 37 which is designed as a ball bearing, is seated on the second roll neck 8.
  • the further bearing arrangement 37 has an inner ring 38 and an outer ring 39 as well as between these arranged bearing balls 40.
  • the inner ring 38 sits on the second roll neck 8 and is connected to it in a rotationally fixed manner.
  • the outer ring 39 is carried by the second wall 5.
  • the bearing balls 40 are held by a cage.
  • the further bearing arrangement 37 is arranged adjacent to the second wall 5 and the outlet 21. It is designed as a floating bearing.
  • tempering roller arrangement 1 does not require a gear or coupling, this leads to a particularly high (system) rigidity.
  • system rigidity
  • first roller pin 7 is only responsible for supplying the tempering fluid and the second roller pin 8 is only responsible for discharging the tempering fluid, particularly large flow cross-sections are available for the tempering fluid, which allows extremely efficient energy transfer during operation.
  • the tempering roller arrangement 1 is integrated into a tempering fluid circuit in which there is at least one heat exchanger 41, preferably several, such as two, heat exchangers, and the tempering fluid flows during operation.
  • the outlet 21 is in flow connection with a heat exchanger inlet of the at least one heat exchanger 41, directly or indirectly.
  • a heat exchanger outlet of the at least one heat exchanger 41 is in flow connection with the inlet 15, directly or indirectly.
  • the operation of the tempering roller arrangement 1 is described below.
  • the stator 23 generates a magnetic field during operation.
  • the associated rotor 22 is thus driven in rotation and rotates within the stator 23 about the longitudinal center axis 9, which leads to a corresponding rotary drive of the tempering roller 2 about the longitudinal center axis 9.
  • the tempering fluid enters the first roller neck 7 via the inlet 15 and flows in the inlet channel 14 in the direction of the first radial channels 16.
  • the tempering roller 2 rotates in the process. It can be driven in rotation and at the same time can be flowed through.
  • the tempering fluid flows through the rotary drive 3, in particular its rotor 22 or stator 23, the bearing arrangement 27 and the angle of rotation sensor 36. It flows via the roller body 6 into the second roller neck 8, where it flows through the further bearing arrangement 37.
  • the tempering fluid then leaves the tempering roller 2 and flows back to the inlet 15 via the at least one heat exchanger 41.
  • the graduation carrier rotates around the longitudinal center axis 9 and moves past the reading head.
  • the rotational position of the first roll neck 7 or the tempering roller 2 or the rotor 22 is determined via the rotation angle sensor 36.
  • This current position of the first roll neck 7 or the tempering roller 2 or the rotor 22 is transmitted, preferably continuously, to a servo control device.
  • the current position of the first roll neck 7 or the tempering roller 2 or the rotor 22 is then preferably compared with a corresponding target position and adjusted if necessary. If the tempering roller arrangement 1 is designed as a cooling roller arrangement, cooling water preferably forms the tempering fluid.
  • the cooling water is able to flow through the rotary drive 3, in particular the rotor 22 and stator 23, and the bearing arrangement 27 and, advantageously, also the angle of rotation sensor 36 and to cool them, in particular from the radial inside, which increases their service life.
  • the cooling water also flows through and cools the roller shell 10, which leads to cooling of the material web guided around the roller shell 10 or lying on the outside of it.
  • the tempering roller 2 provides a constant temperature profile on its outside.
  • the external cooling leads to a particularly long service life.
  • the cooling water preferably also flows through and cools the further bearing arrangement 37.
  • the cooling water absorbs thermal energy from the part to be cooled or cooled and is heated.
  • the cooling water is cooled again in the at least one heat exchanger 41.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Abstract

L'invention concerne un ensemble rouleau de thermorégulation comprenant un rouleau de thermorégulation (2) pour thermoréguler une bande de matériau (42) en mouvement. Le rouleau de thermorégulation (2) comporte un corps de rouleau (6), un premier tourillon de rouleau (7) en liaison avec le corps de rouleau (6) et un deuxième tourillon de rouleau (8) pour loger le corps de rouleau (6), au moins une entrée de fluide de thermorégulation (15) pour un fluide de thermorégulation sur un premier côté du rouleau de thermorégulation (2) et au moins une sortie de fluide de thermorégulation (21) en liaison d'écoulement avec l'entrée ou les entrées de fluide de thermorégulation (15) pour le fluide de thermorégulation sur un deuxième côté du rouleau de thermorégulation (2) qui est opposé au premier côté. L'ensemble rouleau de thermorégulation comprend en outre un entraînement rotatif (3) en liaison d'entraînement avec le rouleau de thermorégulation (2) et comportant un rotor (22) pour entraîner en rotation le rouleau de thermorégulation (2).
EP23797724.4A 2022-10-27 2023-10-23 Ensemble rouleau de thermorégulation Pending EP4573035A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022211429.9A DE102022211429A1 (de) 2022-10-27 2022-10-27 Temperierwalzen-Anordnung
PCT/EP2023/079465 WO2024088959A1 (fr) 2022-10-27 2023-10-23 Ensemble rouleau de thermorégulation

Publications (1)

Publication Number Publication Date
EP4573035A1 true EP4573035A1 (fr) 2025-06-25

Family

ID=88585377

Family Applications (1)

Application Number Title Priority Date Filing Date
EP23797724.4A Pending EP4573035A1 (fr) 2022-10-27 2023-10-23 Ensemble rouleau de thermorégulation

Country Status (4)

Country Link
EP (1) EP4573035A1 (fr)
CN (1) CN119947970A (fr)
DE (1) DE102022211429A1 (fr)
WO (1) WO2024088959A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022211429A1 (de) 2022-10-27 2024-05-02 Bhs Corrugated Maschinen- Und Anlagenbau Gmbh Temperierwalzen-Anordnung

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE68910193T2 (de) * 1988-06-07 1994-02-17 Grace W R & Co Kühlwalze.
DE10305316B4 (de) 2002-03-13 2011-06-16 Goss Contiweb B.V. Kühlwalze mit einem im Wesentlichen hohlen Innenraum
DE10342739A1 (de) 2002-10-16 2004-04-29 Heidelberger Druckmaschinen Ag Antriebsmotor mit integriertem Überträger für Bedruckstoffe verarbeitende Maschinen
DE10250690B4 (de) * 2002-10-31 2006-03-02 Koenig & Bauer Ag Rotationskörper einer Druckmaschine mit einem Ballen
DE102006005151A1 (de) 2006-02-04 2007-08-09 Man Roland Druckmaschinen Ag Vorrichtung und Verfahren zum Temperieren eines Rotationskörpers
DE102015208190B4 (de) 2015-05-04 2019-02-28 Koenig & Bauer Ag Verfahren zum Betreiben zumindest eines Druckaggregats
EP3921161B1 (fr) * 2019-02-05 2023-03-15 Koenig & Bauer AG Unités d'impression en creux pour imprimer des substrats selon un procédé d'impression en creux
CN214083392U (zh) 2020-09-11 2021-08-31 胡永宏 一种印刷机加工用冷却装置
DE102022211429A1 (de) 2022-10-27 2024-05-02 Bhs Corrugated Maschinen- Und Anlagenbau Gmbh Temperierwalzen-Anordnung

Also Published As

Publication number Publication date
CN119947970A (zh) 2025-05-06
DE102022211429A1 (de) 2024-05-02
WO2024088959A1 (fr) 2024-05-02

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