DE102006004572B4 - Drive a vibration system - Google Patents

Abstract

Drive a vibration system, the sheet transported to a feed drum (8), which together with at least one drive cam (19) and at least one torque compensating gear (37) controlling compensating cam (30) on a feed drum shaft (10) is arranged, characterized in that a movement law imprinted on the compensating cam disk (30) is formed in such a way that the sum of the drive torque of the oscillating system (22) and the compensation torque initiated by the torque compensation gear (37) has an alternating course with the period 360 ° provided with a positive and a negative range has a Eintourenwelle and at the sheet transfer to the feed drum (8) acts a slight Verspannmoment.

Description

The invention relates to a drive of a vibration system that transports sheets to a feed drum, which is arranged together with at least one drive cam and at least one compensating cam plate controlling a torque compensating gear on a feed drum shaft.

In sheet-processing machines, it is customary to guide the sheets on a feed table and with the leading edge against can be brought into the path of the sheet leading brands and so align with the leading edge. Subsequently, if necessary, the sheets are aligned to the side edge. Subsequently, the aligned and at rest sheets are detected by the vibrating system and accelerated to feed drum speed and passed to a feed drum. After the sheet transfer, the vibration system is delayed and returned to the feed table to take over the next sheet. Such vibration systems have prevailed for arc acceleration as a transmission type. But they have the disadvantage that always positive and negative drive torques occur whose amplitudes are increasing with increasing speeds and format widths, so that the vibration system is the main vibration exciter in sheet-processing machines. The periodically fluctuating torque requirement leads to oscillations in the sheet feeding system and via the gear train to the printing units, which ultimately leads to registration errors and doubling.

Furthermore, it is disadvantageous that to ensure a permanent flank system in the gear train as Eintriebsstelle the plant printing unit must be selected. However, as the trend of development is towards more and more printing units per machine, but the transmissible torque of the gear train proves to be performance limiting, a center drive would be advantageous in many ways.

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 sinusoidal for the synchronized and the mating section.

The disadvantage is that this type of power compensation requires very specific laws of motion, but in turn allow no rest on the investment table. In addition, it is necessary to drive the oscillator directly from the cam so that there is no distortion of the symmetrical movement.

From Dresig / Holzweißig "Maschinendynamik" 5th edition 2004, p 170 ff it is known to compensate for individual harmonics of the drive torque by the first harmonic is compensated by a circumferential balancing mass and any other harmonic by balancing mechanisms.

Since the drive torque of a sheet-fed press but consists of many harmonics, a counter gear is to install for each harmonic, which can only be realized with great effort and ultimately only leads to a partial power compensation.

The object of the invention is to allow a complete power balance of the overall transmission at any, optimal for the sheet transport movement of the swing system with simple means.

According to the invention the object is achieved by a drive according to the features of claim 1.

By means of the solution according to the invention, it is possible to design the compensation cam of a torque balancing transmission in such a way that an almost complete power compensation takes place independently of the motion law of the vibration system. In addition to a complete power compensation, there is also the possibility of designing the compensation torque in such a way that a targeted residual torque is realized by the sum of the torques, which acts as a low bracing torque, which ensures a permanent tooth flank system.

• 1 eine schematische Darstellung eines Anlagedruckwerks mit einer Schwinganlage in der Seitenansicht,
• 2 eine räumliche Darstellung der Schwinganlage mit einem Momentenausgleichsgetriebe,
• 3 einen Antriebsmomentenverlauf,
• 4 die Überlagerung des Antriebsmomentenverlaufs mit einem durch ein Momentenausgleichsgetriebe initiierten Ausgleichsdrehmomentenverlauf.

In one embodiment, the invention is explained in detail. In the accompanying drawings show

• 1 a schematic representation of a plant printing unit with a vibration system in the side view,
• 2 a spatial representation of the oscillating system with a torque compensation gear,
• 3 a drive torque curve,
• 4 the superposition of the drive torque curve with an initiated by a torque compensation gear compensation torque curve.

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 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 worm 13 meshes, via 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.

On the feed drum shaft 10 are next to the feed drum 8th and the application drum 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 drive cam 20 is a law of motion for the realization of the motion task of a vibration system 22 applied. For this purpose, a main cam roller runs on the main drive cam 20 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 these in the power stroke by a swivel angle ψ is pivoted.

With the feed drum shaft 10 is still a compensation cam 30 connected in the embodiment as Hauptausgleichkurvenscheibe 31 with a secondary compensation cam 32 is trained. At the main compensation cam 31 runs a first cam roller 33 and at the secondary balance cam 32 a second cam follower 34 from. The cam rollers 33 . 34 are in a double swing 42 recorded, the rotation on a balance shaft 35 is stored. With the balance shaft 35 is also a compensation torque 36 connected.

The balance cam 30 , or main compensation cam 31 / Secondary compensation cam 32 and by the cam rollers 33 . 34 operatively connected double rocker 42 form with the compensation torque 36 a torque compensation gear 37 ,

The through the vibration system 22 to be implemented motion task is gem. 3 chosen so that the drive torque curve, measured at the feed drum shaft 10 , mirror-symmetrical to a rotation angle φ = 180 ° designed as Eintourenwelle Anlegtrommelwelle 10 is formed, wherein the movement pattern is divided into four areas, each extending over 90 °. But it is also every other movement history and a resulting drive torque curve conceivable.

The on a feed table 38 aligned and resting arches are by grippers 39 the vibration system 22 in a resting position at the feed table 38 are recorded. At a rotation angle φ of about 10 ° is the vibration system 22 accelerated and at φ = 90 ° of the vibration system 22 held bow to a sheet holder 40 the application drum 8th to hand over. Then the vibration system 22 delayed, goes through φ = 180 ° a reversal point, is accelerated again and at φ = 270 ° delayed starting, so that the vibration system 22 at about φ = 350 ° in its resting position on the feed table 38 to take over a follow-up arc. For this drive torque curve is a through the torque compensation gear 37 to determine to realize balancing torque, which has such a profile, that the sum of the drive torque and the balancing torque has a sinusoidal course with the period φ = 360 ° and in the transfer of the sheet to the feed drum 8th a slight tensioning moment acts.

und $${\text{M}}_{\text{RH}}=\text{J*}\mathrm{\psi }\text{''}*{\left(2\mathrm{\pi }*\text{n}\right)}^2$$

ist. For this purpose, it is assumed from the general contexts that the drive torque of the drive cam 19 or Main drive cam 20 / Nebenantriebskurvenscheibe 21 and with the cam rollers 23 . 24 provided double roller lever 25 existing drive cam gear 41 $$\text{MKU}={\text{M}}_{\text{RH}}*\mathrm{\psi }\text{'}$$

and $${\text{M}}_{\text{RH}}=\text{J *}\mathrm{\psi }\text{''}*{\left(2\mathrm{\pi }*\text{n}\right)}^2$$

is.

J is the reduced mass moment of inertia of the vibration system 22 , of the drive cam gear 41 including paddock 27 and bearing levers 28 on the roller lever shaft 26 and n the speed. Under ψ the first derivative and ψ the second derivative of ψ to φ Understood.

As a law of motion for the torque compensation gear 37 a polynomial with a degree less than 13 is chosen. $$\mathrm{\Psi \; =}{\text{C}}_{\text{0}}+{\text{<figure-callout id="1" label="C" filenames="DE102006004572B4\_0009.png" state="{{state}}">C</figure-callout>}}_1*\mathrm{\phi \; +}{\text{<figure-callout id="2" label="C" filenames="DE102006004572B4\_0009.png,DE102006004572B4\_0012.png" state="{{state}}">C</figure-callout>}}_2*{\mathrm{<figure-callout\; id="2"\; label="\phi "\; filenames="DE102006004572B4\_0009.png,DE102006004572B4\_0012.png"\; state="\{\{state\}\}">\phi </figure-callout>}}^2+{\text{<figure-callout id="3" label="C" filenames="DE102006004572B4\_0009.png" state="{{state}}">C</figure-callout>}}_3*{\mathrm{<figure-callout\; id="3"\; label="\phi "\; filenames="DE102006004572B4\_0009.png"\; state="\{\{state\}\}">\phi </figure-callout>}}^3+...$$

$$\mathrm{\Psi }\text{''}=2{\text{C}}_2+6{\text{C}}_3*\mathrm{\phi +}\dots$$

With that follows: $$\mathrm{\Psi }\text{'}={\text{<figure-callout id="1" label="C" filenames="DE102006004572B4\_0009.png" state="{{state}}">C</figure-callout>}}_1+2{\text{<figure-callout id="2" label="C" filenames="DE102006004572B4\_0009.png,DE102006004572B4\_0012.png" state="{{state}}">C</figure-callout>}}_2*\mathrm{\phi \; +\; 3}{\text{<figure-callout id="3" label="C" filenames="DE102006004572B4\_0009.png" state="{{state}}">C</figure-callout>}}_3*{\mathrm{<figure-callout\; id="2"\; label="\phi "\; filenames="DE102006004572B4\_0009.png,DE102006004572B4\_0012.png"\; state="\{\{state\}\}">\phi </figure-callout>}}^2+...$$

$$\mathrm{\Psi }\text{''}=2{\text{<figure-callout id="2" label="C" filenames="DE102006004572B4\_0009.png,DE102006004572B4\_0012.png" state="{{state}}">C</figure-callout>}}_2+6{\text{<figure-callout id="3" label="C" filenames="DE102006004572B4\_0009.png" state="{{state}}">C</figure-callout>}}_3*\mathrm{\phi \; +}...$$

bzw. $${\text{M}}_{\text{KU}}=\text{J*}\left({\text{C}}_1+2{\text{C}}_2*\mathrm{\phi +3}{\text{C}}_3*{\mathrm{\phi }}^2+\dots \right)*\left(2{\text{C}}_2+6{\text{C}}_3*\mathrm{\phi +}\dots \right)*{\left(2\mathrm{\pi }\text{*n}\right)}^2$$

This calculates the drive torque of the drive cam gear 41 ultimately too $${\text{M}}_{\text{KU}}=\text{J}*\mathrm{\Psi }\text{'}*\mathrm{\Psi }\text{''}{\left(2\mathrm{\pi }*\text{n}\right)}^2$$

respectively. $${\text{M}}_{\text{KU}}=\text{J *}\left({\text{<figure-callout id="1" label="C" filenames="DE102006004572B4\_0009.png" state="{{state}}">C</figure-callout>}}_1+2{\text{<figure-callout id="2" label="C" filenames="DE102006004572B4\_0009.png,DE102006004572B4\_0012.png" state="{{state}}">C</figure-callout>}}_2*\mathrm{\phi \; +\; 3}{\text{<figure-callout id="3" label="C" filenames="DE102006004572B4\_0009.png" state="{{state}}">C</figure-callout>}}_3*{\mathrm{<figure-callout\; id="2"\; label="\phi "\; filenames="DE102006004572B4\_0009.png,DE102006004572B4\_0012.png"\; state="\{\{state\}\}">\phi </figure-callout>}}^2+...\right)*\left(2{\text{<figure-callout id="2" label="C" filenames="DE102006004572B4\_0009.png,DE102006004572B4\_0012.png" state="{{state}}">C</figure-callout>}}_2+6{\text{<figure-callout id="3" label="C" filenames="DE102006004572B4\_0009.png" state="{{state}}">C</figure-callout>}}_3*\mathrm{\phi \; +}...\right)*{\left(2\mathrm{\pi }\text{* n}\right)}^2$$

The qualitative and quantitative course of the drive torque can be determined with knowledge of the oscillator movement with known methods. This negated drive torque of the vibration system 22 including the drive cam gear 41 and its assignment to the oscillator shaft 29 is denoted by -M _SK .

This is $${\text{M}}_{\text{KU}}=-{\text{M}}_{\text{SK}}$$

• - dass die Summe der Momente bei einer Bogenübernahme vom Anlegtisch 38 Null ist,
• - dass bei der Bogenübergabe an die Anlegtrommel 8 ein Verspannmoment realisiert ist und
• - dass der Anfang und das Ende des Kurvenverlaufs einen gleichen Hub aufweisen, können die Variablen I, C₁, C₂, C₃ ... bestimmt werden.

The coefficients can not be determined directly from the given discrete values of M _SK for the overall course from the overdetermined nonlinear system of equations. By a non-linear optimization based on the boundary conditions

• - that the sum of the moments at a sheet transfer from the feed table 38 Zero is,
• - that at the sheet transfer to the feed drum 8th a tensioning moment is realized and
• - that the beginning and the end of the curve have the same stroke, the variables I, C ₁ , C ₂ , C ₃ ... can be determined.

The optimization goal is that M _SK ( φ ) + M _KU ( φ ) sinusoidal and still a slight tensioning moment in the transfer of the bow of the vibrating system 22 to the feed drum 8th occurs and the moment peaks, as z. In 3 are not shown.

In 4 is the result of such a nonlinear optimization shown. It is shown that the drive torque curve with a through the torque compensation gear 37 initiated compensation torque curve (dashed line) is superimposed such that the sum of the two torque curves sinusoidal, so that in the field of sheet transfer to the application drum 8th a maximum and a zero point at the beginning of the movement as well as another zero point in the area of the reversal of motion of the oscillating system 22 occurs.

LIST OF REFERENCE NUMBERS

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

Compensation cam

31

Main compensation cam

32

In addition to compensation cam

33

First cam roller

34

Second cam roller

35

balancer shaft

36

Balancing rotating mass

37

Moment differential

38

feed table

39

grab

40

Sheet holder

41

Drive cam gear

42

double rocker

φ

angle of rotation

ψ

swivel angle

Claims (6)

Drive a vibration system, the sheet transported to a feed drum (8), which together with at least one drive cam (19) and at least one torque compensating gear (37) controlling compensating cam (30) on a feed drum shaft (10) is arranged, characterized in that a movement law imprinted on the compensating cam disk (30) is designed such that the sum of the drive torque of the oscillating system (22) and the compensation torque initiated by the torque compensation gear (37) has an alternating course with the period 360 ° provided with a positive and a negative range has a single-turn shaft and - at the sheet transfer to the feed drum (8) acts a slight Verspannmoment. Drive to Claim 1 , characterized in that the course of the sum has a zero point at the beginning of the movement and a further zero point in the region of the reversal of motion of the oscillating system (22). Drive to Claim 2 , characterized in that the sum has a sinusoidal shape. Drive to Claim 1 , characterized in that the movement law applied to the compensating cam disc (30) by means of a non-linear optimization on the basis of the boundary conditions, - that the sum of the moments at a sheet transfer from the feed table (38) is zero, - that during the sheet transfer to the feed drum ( 8) a Verspannmoment is realized and - that the beginning and the end of the curve have the same stroke, adapted polynomial is realized. Drive to Claim 4 , characterized in that an n-th degree polynomial is provided. Drive to Claim 5 , characterized in that a polynomial is used to the 13th degree.

Images