DE102006008367A1 - Stacking drum for use in e.g. printing device, has vibrating system guiding sheet in drum, where vibrating system and drum are connected with each other, and additional mass senses and compensates static unbalance of vibrating system - Google Patents

Abstract

The drum (8) has a vibrating system (22) for guiding a sheet in the drum, where the system and the drum are connected with each other. An additional mass (33) senses and compensates a static unbalance of the system. Magnitude and phase of the additional mass are determined by the magnitude of the static unbalance of the system and by the connection of the system and the drum at a routing shaft, which circulates with a rotation angle of 360 degree within a machine cycle.

Description

The The invention relates to a feed drum with a bow to the feed drum leading Vibration system, wherein the vibration system and the feed drum geared to each other are connected.

In sheet-processing machines it is common to bend the bow to one Anlegeisch and with the leading edge against in the course of the bow bringable front brands respectively and so to align with the leading edge. The following will be the bows aligned to the side edge. Then be the aligned and resting bow of the vibration system recorded and accelerated to feed drum speed and on handed over a feed drum. In this case, the feed drum within a work cycle steadily or rotate periodically. After the sheet transfer, the vibration system delayed as well as to the landing table for takeover the subsequent arc returned. such Vibration systems have become the arc acceleration as a transmission type enforced. But they have the disadvantage that always positive and negative drive torques occur whose amplitudes increase with Speeds and format widths are getting bigger, so the vibration system represents the main vibrator in sheet-processing machines. The periodically fluctuating torque requirement leads to oscillations in the sheet feeding system and over the gear train to the printing units, which ultimately leads to registration errors and duplication leads.

To eliminate these disadvantages, a power balance of the oscillating system is required. This was in the DD 266 784 B5 proposed to realize in a generic vibration system drive the course of movement of the balance cam with the help of at least one jerk and shock-free sine curve for the synchronizing and the mating section. But this can only be compensated for the dynamic drive torque of vibration systems.

Around the raised It is it to meet the accuracy requirements of the final product also common Drums and cylinders in sheet-fed rotary presses at least statically, usually also dynamically balance. Naturally, a vibration system is strong unbalanced, a balancing of the oscillating system prohibits but because of the resulting high moment of inertia and the associated high drive torque.

task The invention is, with simple means that from the static Imbalance of the vibration system resulting static drive torque to minimize and thus improve the concentricity of the entire machine.

According to the invention Task by a feed drum according to the features of the claim 1 solved.

The Solution according to the invention allowed it, with simple means the existing imbalance of the vibration system strongly due to a defined position of the imbalance of the feed drum reduce and thus improve the concentricity of the entire machine.

At an embodiment the invention will be closer explained. In the associated Drawings show

1 a schematic representation of a plant printing unit with a vibration system in the side view,

2 a possibility of driving a vibration system in a spatial representation,

3 the torque curve of an unbalanced application drum and the vibration system,

4 the moment course after 3 with the specifically provided with an unbalanced feed drum,

5 a schematic representation of the oscillating system and the application drum.

In the 1 is a plant printing unit 1 with a printing cylinder 2 a rubber cylinder 3 and a plate cylinder 4 shown. From the cylinders 2 . 3 and 4 each is a Druckzylinderrad 5 , a rubber cylinder wheel 6 and a plate cylinder wheel 7 shown. The impression cylinder wheel 5 combs with a dresser 8th associated application drum 9 , feed drum 8th and application drum wheel 9 are on a feed drum shaft 10 arranged. The feed drum shaft 10 is designed as single-speed shaft and runs with a rotation angle φ = 360 ° within a working cycle. The printing cylinder 2 and the impression cylinder wheel 5 are with a drive wheel 11 on a printing cylinder shaft 12 stored, with the Eintriebsrad 11 a snail 13 meshes, which has a drive shaft 14 and a belt drive 15 with a main engine 16 connected is. With the printing cylinder wheel 5 Also combs a transfer cylinder wheel 18 that with a transfer cylinder 17 connected is. Through the transfer cylinder wheel 18 downstream units of the printing press are driven.

In the embodiment are on the feed drum shaft 10 next to the feed drum 8th and the feed drum wheel 9 , as in 2 shown a drive cam 19 acting as the main drive cam 20 and PTO cam 21 is formed, provided. On the main engine cam profile 20 is a law of motion for Realisie tion of the motion task of a vibration system 22 applied. To do this, run on the main drive cam 20 a major curve role 23 and on the PTO cam 21 a secondary curve role 24 from. The cam rollers 23 . 24 are in a double roller lever 25 stored on a roller lever shaft 26 is arranged. For clearance compensation z. B. a main curve role 23 double roller lever carrying arm 25 be formed elastic than a Nebenkurvenrolle 24 carrying arm. The double roller lever 25 is through a paddock 27 with a bearing lever 28 connected, the non-rotatably on a vibration system 22 carrying swinging shaft 29 is arranged so that it is pivoted in the power stroke by a swivel angle ψ.

The drive of the vibration system 22 can also be done in another way, always between the feed drum 8th and the vibration system 22 a geared connection is provided.

The on a feed table 30 aligned and resting arches are by grippers 31 the vibration system 22 in a resting position at the feed table 30 are recorded. At a rotation angle φ of about 10 °, the vibration system 22 accelerated and at φ = 90 ° of the vibration system 22 held bow to a sheet holder 32 the application drum 8th to hand over. Then the vibration system 22 delayed, passes through at φ = 180 ° a reversal point, is accelerated again and delayed starting at φ = 270 °, so that the oscillating system 22 at about φ = 350 ° in their rest position on the feed table 30 to take over a follow-up arc. But it is also possible, every other movement of the vibration system 22 to realize. In the described sequence of movements, which is mirror-symmetrical to φ = 180 ° and divided into four ranges of φ = 90 °, resulting in an unweighted application drum 8th , their imbalance in particular by the eccentrically arranged sheet holding system 32 is determined, a static drive torque MAT and for the vibration system 22 a static drive torque MSA ( 3 ).

The 3 shows that the addition of the moments MSA and MAT results in a sum sum curve MSU, which in the maximum values is considerably higher than those of the individual curves MAT and MSA. Will now be the feed drum 8th , starting from the torque curve MSA, targeted by phase, ie in dependence on the rotation angle φ of z. B. trained as one-turn shaft application drum shaft 10 , and size in addition with an imbalance additional mass 33 provided, a torque curve MATZ, so the static torque curve MAT targeted influenced by the additional mass 33 , are influenced in such a way that the extreme values of the course of the momentum sum MSU are minimized. In 4 is shown, wherein the drive torque curve MSA as in 3 is shown and by a targeted attachment of an imbalance of the drive torque curve MATZ was designed so that the sum of momentum curve MSU has low extremes and have the negative and positive extremes small amounts.

In 5 are in principle the oscillating system 22 with the feed drum 8th that with the additional mass 33 is provided, shown. The resultant of the mass m _{AT of} the application drum 8th including the additional mass 33 engages in the center of gravity S _{AT of} the feed drum 8th at the distance R _AT from the axis of the feed drum shaft 10 is removed. The resultant of the mass m _{SA of} the vibration system 22 engages in the center of gravity S _{SA of} the vibration system 22 at the distance R _SA to the axis of the oscillator shaft 29 is arranged. This leaves out of the relationship for this position m AT · G · R AT = m · g · ψ '· R SA . where the static drive torque MSA the vibration system 22 known as well as exactly determinable and ψ 'is the first derivative to φ, the phase and size of the additional mass 33 determine approximately.

1

Plant printing unit

2

pressure cylinder

3

rubber cylinder

4

plate cylinder

5

Druckzylinderrad

6

Gummizylinderrad

7

Plattenzylinderrad

8th

feed drum

9

Anlegtrommelrad

10

Anlegtrommelwelle

11

Eintriebsrad

12

Pressure cylinder shaft

13

slug

14

drive shaft

15

belt drive

16

main engine

17

Transfer cylinder

18

Übergabezylinderrad

19

Operating cam

20

Main drive cam

21

PTO cam

22

swing feeder

23

Main follower

24

Besides follower

25

Double roller lever

26

Roller lever shaft

27

paddock

28

bearing lever

29

swing shaft

30

feed table

31

grab

32

Sheet holder

33

additional mass

φ

angle of rotation

ψ

swivel angle

MAT

static Drive torque feed drum

MATZ

static Drive torque feed drum with additional mass

MSA

unbalanced static drive moment oscillation system

MSU

moment sum

m _SA

Dimensions swing feeder

_AT

Dimensions feed drum

_SA

main emphasis swing feeder

S _AT

main emphasis feed drum

R _AT

Distance S _AT from the axis of the feed drum

R _SA

Distance S _SA from the axis of the vibration system

Claims (2)

Anfetrommel with a bow leading to the application drum oscillating system, wherein the oscillating system and the feed drum are geared to each other, characterized in that the feed drum ( 8th ) with a imbalance realizing, the static imbalance of the oscillating system ( 22 ) compensating additional mass ( 33 ) is provided. Feed drum according to claim 1, characterized in that the additional mass ( 33 ) in its size and phase to a rotating with a rotation angle φ = 360 ° within a machine cycle Eintourenwelle by the size of the static imbalance of the oscillating system ( 22 ) and is determined by the geared connection.