EP0543196A1 - Driving device for cover gumming machine - Google Patents

Abstract

In cover gumming machines (1), the sleeve shafts (8) are connected to a ring gear (24) via pinions (10). In order to keep the rotational speed (nP/K) of the sleeve shafts (8) constant relative to the machine head (5), irrespective of the rotational speed (nK) of the latter, the ring gear (24) in the new driving device is connected to a driving motor (auxiliary motor 27) which can be operated independently of the driving motor (main drive) driving the machine head (5) and preferably with a variable rotational speed (n27). In a preferred embodiment, the connection between the ring gear (24) and the separate driving motor (auxiliary motor 27) is effected via a differential gear unit (28), the revolving housing of which is driven by the separate driving motor (27), one output shaft (pinion 33) of the differential gear unit (28) being connected kinematically to the ring gear (24) and the other output shaft (pinion 32) being connected - indirectly if required - to the first driving motor (main motor). <IMAGE>

Description

The invention relates to a drive arrangement for a cover gumming machine having a machine head driven by a drive motor and rotatable about a vertical axis with a plurality of quill shafts with plates for receiving covers, the quill shafts being rotatably mounted about axes arranged parallel to the vertical axis and each having a pinion , which is in engagement with a ring gear that can be rotated about the vertical axis and relative to the machine head.

A drive for a cover gumming machine is known from US Pat. No. 4,262,629. The lids rotating with the quill shafts are loaded with a lid in one station. During the rotation of the machine head, the quills are raised and the plate presses the cover against a spring-loaded counterholder. After a further rotation of the machine head, a liquid sealing or rubber compound is poured into the edge of the cover from a spray gun that is assigned to each sleeve and rotates with the machine head and is evenly distributed as a result of the rapid rotation of the cover. In the known cover gumming machine, the ring gear with which the pinions of the quill shafts are engaged is now driven by the same main motor as the machine head via a series of drive transmissions. Even if the machine head and the circumferential ring gear have different speeds, they are still rigidly connected to one another in terms of gear, ie their speeds are in a constant ratio. If the machine head due to a malfunction to When it comes to a standstill, the rotating ring gear also stops and the quill shafts can no longer turn. The rubber compound that is placed in a cover when the machine head is braked or when it is at a standstill can no longer run properly, resulting in an unusable cover.

Another disadvantage of the known drive arrangement is that to change the speed of the sleeves relative to the machine head, e.g. when changing the format (changing the cover diameter), at least one gear pair must be replaced in order to change the gear ratio.

The invention has for its object to provide a drive for a cover gumming machine in which the quill shafts responsible for rotating the cover continue to rotate when the machine head is at a standstill, so that the liquid gum mass can still run.

This object is achieved in that the ring gear, with which the pinions of the quill shafts are engaged, is connected to a drive motor (auxiliary motor) separate from the drive motor (main drive).

When the machine head is at a standstill, the sprocket driving the quill shafts can continue to rotate, so that the covers held on the quills also do not come to a standstill and the rubber compound can run. The speed of the sleeves depends not only on the speed of the ring gear but also on the speed of the machine head, whereby a direction of rotation of the machine head that is usually opposite to the rotation of the ring gear increases the speed of the sleeves. In order to also take this component into account, a Further development of the invention provides to drive the ring gear by the separate drive motor (auxiliary motor) in such a way that the speed of the ring gear decreases with increasing speed of the machine head.

Such a speed reduction of the ring gear is advantageously brought about in that the connection between the ring gear and the separate drive motor (auxiliary motor) takes place via a differential gear, the rotating housing of which is driven by the separate drive motor, the one output shaft of the differential gear being geared to the ring gear and the another output shaft is connected to the first drive motor (main drive).

In the case of a differential gear, half the speed of the output shafts is equal to the speed of the rotating housing. If both output shafts rotate at the same speed, their speed is identical to that of the housing. If an output shaft is braked, the speed of the other output shaft increases accordingly while the speed of the housing remains the same. This is used in a further development of the invention. If the speed of the main drive and thus the proportional speed of the machine head is reduced, then the speed of the output shaft of the differential gear connected to the main drive is inevitably reduced and the speed of the output shaft connected to the ring gear is increased accordingly. This compensates for the drop in speed of the quill shafts caused by the machine head or main drive.

In order to keep the speed of the quill shafts in relation to the machine head constant regardless of the speed of the machine head, proposed that the connection of one output shaft of the differential gear to the first drive motor (main drive) via the machine head and that the gear ratio of this output shaft to the machine head is as large as the gear ratio of the other output shaft of the differential gear to the ring gear. Since the regulating influence occurs from the machine head to the differential gear, the condition can also be formulated in such a way that the gear ratio from the machine head to the output shaft of the differential gear connected to it is equal to the reciprocal of the gear ratio from the other output shaft to the ring gear.

In order to keep the quill speed related to the machine head constant, the ring gear can also be driven by the separate drive motor (auxiliary motor) via a fixed transmission ratio if the speed of the separate drive motor is changed via an actuating device depending on the speed of the machine head.

In addition, it is also possible to drive the ring gear from the separate drive motor (auxiliary motor) via a transmission with a variable transmission ratio and to change this transmission ratio as a function of the speed of the machine head.

In a gumming machine according to the invention, the speed of the machine head and thus the output of the machine can be freely selected or predefined and can thus be adapted to the most varied of circumstances. This is of interest, for example, when there is an accumulation section in front of or behind the gumming machine or when the output of an upstream punch press changes. Also a formal change (change of Cover diameter) is not a problem, since the correct rotational speed of the quill shafts for the respective cover diameter and the respective sealing or rubber compound is brought about in a simple manner by changing the rotational speed of the separate drive motor (auxiliary motor).

Fig. 1

eine Deckel-Gummiermaschine in einem senkrechten Längsschnitt,

Fig. 2

die Deckel-Gummiermaschine in einem auszugsweisen waagerechten Querschnitt längs der Linie II-II,

Fig. 3

die getriebemäßige Verknüpfung der Pinolen, des Kopfteils und des Hilfsantriebs in einer prinzipiellen Darstellung und

Fig. 4

eine andere Verknüpfung der Pinolen, des Kopfteils und des Hilfsantriebs in einer prinzipiellen Darstellung.

Embodiments of the invention are shown schematically in the drawing and are explained in more detail below. Show it

Fig. 1

a cover gumming machine in a vertical longitudinal section,

Fig. 2

the lid gumming machine in a partial horizontal cross section along the line II-II,

Fig. 3

the basic connection of the quill, the head part and the auxiliary drive in a basic representation and

Fig. 4

another connection of the quill, the head part and the auxiliary drive in a basic representation.

The gumming machine 1 has a central column 3 with a vertical axis 4 which is firmly connected to the machine frame 2.

On the column 3, a turret or machine head 5 is rotatably mounted with a plurality of through holes 6 arranged parallel to the axis 4. Quill sleeves or bearing sleeves 7 are axially slidably guided in the through bores 6, in which quill sleeves 8 are in turn rotatably mounted. The sleeve shafts 8 carry a plate 9 suitable for receiving a can lid at the top and a gear or pinion 10 below. Both the plate 9 and the pinion 10 are firmly connected to the shaft 8.

On the side facing away from the axis 4, each bearing sleeve 7 has a guide element 11, which is guided in a guide groove 12 of the machine head 5 and prevents rotation of the sleeve with respect to the machine head. On the side facing the axis 4, a roller 13, which runs a control cam 14, is arranged on each sleeve 7. The control cam 14 is embedded on the circumference of a rotary part 15, which e.g. is non-rotatably connected to the column 3 with a wedge connection, not shown. The control cam 14 causes an axial movement of the sleeve sleeve 7 and thus the sleeve shafts 8 and the plate 9 and the pinion 10.

A counter holder 16 and a spray gun 17 are arranged on the rotatable machine head 5 above each plate 9. The counter holder 16 is rotatably supported at the lower end of an axially movable bolt 18. The pin 18 is pressed down by a spring 19. The lowermost position of the counter-holder 16 is determined by a rear stop 20.

At its lower end, the machine head 5 has a ring gear 21, which meshes with a gear wheel 22 (not shown) driven by the main motor.

A sleeve 23 (drive sleeve) is rotatably mounted on the column 3 within the machine head 5, the lower end of the machine head 5 in turn being mounted on the sleeve 23. The sleeve 23 has a ring gear 24 and 25 at the top and bottom. The pinions 10 of the quill shafts 8 are in engagement with the upper ring gear 24. So that the pinions 10 remain securely engaged with the ring gear 24 even with the axial stroke caused by the control cam 14, they have a correspondingly large height or width.

On an auxiliary frame 26 of the machine frame 2, a motor 27 (hereinafter also referred to as an auxiliary motor) and a differential gear 28 are mounted which are independent of the main drive of the cover gumming machine. The differential gear 28 has around its housing, which is rotatable about a vertical axis 29, a toothed ring 30 which is fixedly connected to the housing and which engages with the drive pinion 31 of the auxiliary motor 27. Coaxial with the axle 29, the differential gear 28 has two output pinions 32 (top) and 33 (bottom). The output pinions 32 and 33 are non-rotatably connected within the housing in a known manner with bevel gears which are in engagement with each other again by differential gears mounted in the housing.

The upper output pinion 32, like the gear 22 driven by the main drive, is in engagement with the ring gear 21 of the machine head 5. The lower output pinion 33 is in engagement with the lower ring gear 25 of the sleeve 23 via an intermediate gear 38 (see FIG. 2). .

The speed n _{K of} the turret head 5 corresponding to the output of the cover gumming machine is determined exclusively and directly by the speed of the main drive (gear wheel 22).

The speed n _{P / K} related to the machine head 5 of the sleeve shafts 8 and the plate 9 firmly connected to them about their own axis is determined independently of the speed n _{K of} the machine head 5 exclusively by the speed n₂₇ of the auxiliary motor 27.

• Übersetzungsverhältnis i_27/28 zwischen dem Hilfsmotor 27 und dem Zahnrad 30 des Differentialgetriebes 28:
  i_27/28 = 53/77
• Übersetzungsverhältnis von der Abtriebswelle des Differentialgetriebes 28 mit dem Ritzel 33 zur Antriebshülse 23 bzw. zum Zahnkranz 24:
  i_33/24 = 40/160 = 1/4
• Übersetzungsverhältnis vom Zahnkranz 24 zu den Pinolenritzeln 10:
  i_24/10 = 146/34
• Übersetzungsverhältnis vom Maschinenkopf 5 zu der Abtriebswelle des Differentialgetriebes 28 mit dem Ritzel 32:
  i_5/32 = 120/30 = 4/1.

This is explained below using a specific numerical example, based on the following number of teeth: Pinion 31: 53 Sprocket 30: 77 Output pinion 32: 30th Sprocket 21: 120 Output pinion 33: 40 Sprocket 25: 160 Sprocket 24: 146 Pinion 10: 34
The following values result from these number of teeth for the gear ratios indicated in FIG. 3:

• _Gear ratio i _27/28 between the auxiliary motor 27 and the gear 30 of the differential gear 28:
  i _27/28 = 53/77
• Gear ratio of the output shaft of the differential gear 28 with the pinion 33 to the drive sleeve 23 or to the ring gear 24:
  i _33/24 = 40/160 = 1/4
• Gear ratio from the ring gear 24 to the pinion pinions 10:
  i _24/10 = 146/34
• Gear ratio from the machine head 5 to the output shaft of the differential gear 28 with the pinion 32:
  i _5/32 = 120/30 = 4/1.

Furthermore, the speed n₂₇ of the auxiliary motor 27 or its drive pinion 31 is assumed to be 1400 min⁻¹.

Berücksichtigt man, daß die Drehzahl des Ritzels 33 des Differentialgetriebes 28

$\text{n₃₃ = 2 n₂₈ - n₃₂}$

ist (die Indizes entsprechen jeweils den Bezugszeichen der betreffenden Teile), wobei

${\text{n₃₂ = n}}_{\text{K}}{\text{i}}_{\text{5/32}}$

ist, so ergibt sich durch Einsetzen und Verwandeln für die bezogene Pinolendrehzahl n_P/K:

${\text{n}}_{\text{P/K}}{\text{= (2 n₂₇ · i}}_{\text{27/28}}{\text{· i}}_{\text{33/24}}{\text{+ n}}_{\text{K}}{\text{(1 - i}}_{\text{5/32}}{\text{· i}}_{\text{33/24}}{\text{)) i}}_{\text{24/10}}$

Da das Übersetzungsverhältnis i_5/32 mit 4/1 umgekehrt proportional dem Übersetzungsverhältnis i_33/24 von 1/4 ist, ergibt sich für den Faktor der Drehzahl n_K unabhängig von der Größe des Übersetzungsverhältnisses i_24/10 der Wert Null, d.h. die Drehzahl n_K des Maschinenkopfes 5 geht in die bezogene Pinolendrehzahl n_P/K überhaupt nicht ein. Bei der dem Rechenbeispiel zugrundegelegten Drehzahl n₂₇ des Hilfsmotors 27 ergibt sich somit eine vom Maschinenkopf 5 völlig unabhängige, konstante Pinolendrehzahl

${\text{n}}_{\text{P/K}}{\text{= 2· 1400 · 77/53 · 40/160 · 146/34 n}}_{\text{P/K}}\text{= 2069 min⁻¹.}$

The speed n _{P / K} related to the machine head 5 of the quill shafts 8 with the pinions 10 is dependent on the speed n₂₄ of the ring gear 24 and the speed n _K of the machine head 5 rotating in the opposite direction of rotation

${\text{n}}_{\text{P / K}}{\text{= i}}_{\text{24/10}}{\text{(n₂₄ + n}}_{\text{K}}\text{)}$

Taking into account that the speed of the pinion 33 of the differential gear 28th

$\text{n₃₃ = 2 n₂₈ - n₃₂}$

(the indices correspond to the reference numerals of the relevant parts), where

${\text{n₃₂ = <figure-callout id="5" label="n K i" filenames="imgf0001.png,imgf0002.png" state="{{state}}">n </figure-callout>}}_{\text{K}}{\text{i}}_{}{}_{\text{5/32}}$

by inserting and transforming for the related quill speed n _{P / K} :

${\text{n}}_{\text{P / K}}{\text{= (2 n₂₇ · i}}_{\text{27/28}}{\text{I}}_{\text{33/24}}{\text{+ n}}_{\text{K}}{\text{(1 - <figure-callout id="5" label="i" filenames="imgf0001.png,imgf0002.png" state="{{state}}">i</figure-callout>}}_{\text{5/32}}{\text{I}}_{\text{33/24}}{\text{)) i}}_{\text{24/10}}$

Since the gear ratio i _5/32 with 4/1 is inversely proportional to the gear ratio i _33/24 of 1/4, the value of the speed n _K, regardless of the size of the gear ratio i _24/10 , is zero, ie The speed n _{K of} the machine head 5 is not included in the related quill speed n _{P / K} at all. At the speed n₂₇ of the auxiliary motor 27 on which the calculation example is based, a completely independent, constant quill speed results from the machine head 5

${\text{n}}_{\text{P / K}}{\text{= 2 x 1400 x 77/53 x 40/160 x 146/34 n}}_{\text{P / K}}\text{= 2069 min -1.}$

Um die Drehzahl n_P/K auch bei sich verändernder Drehzahl n_K des Maschinenkopfes 5 konstant zu halten, braucht die Stelleinrichtung 41 lediglich ein Signal abzugeben, das im Hilfsmotor 27 die Drehzahl n₂₇

bewirkt. Dabei ist i_27/24 ein festes Übersetzungsverhältnis vom Hilfsmotor 27 zum Zahnkranz 24. Das Signal der Stelleinrichtung 41 enthält lediglich eine Veränderliche - die Drehzahl n_K des Maschinenkopfes 5 - und ist im übrigen aus eingebbaren konstanten Werten zusammengesetzt.The invention is not limited to the use of a differential gear. For example the machine head 5, as indicated in FIG. 4, can be mechanically coupled to a tachometer generator 40 as a speed sensor. The auxiliary motor 27 is connected to the tachometer generator 40 via a preferably electronic actuating device 41. The quill speed n _{P / K} related to the machine head 5 is - as before -

${\text{n}}_{\text{P / K}}{\text{= i}}_{\text{24/10}}{\text{(n₂₄ + n}}_{\text{K}}\text{)}$

In order to keep the speed n _{P / K} constant even with changing speed n _{K of} the machine head 5, the actuating device 41 only needs to emit a signal that the speed n₂₇ in the auxiliary motor 27

causes. Here i _{27/24 is} a fixed gear ratio from the auxiliary motor 27 to the _ring gear 24. The signal from the actuating device 41 contains only one variable - the speed n _{K of} the machine head 5 - and is otherwise composed of constant values that can be input.

It is also conceivable to keep the speed n₂₇ of the auxiliary motor 27 constant and to change the gear ratio i _{27/24 accordingly} by means of an adjusting _gear as a function of the speed n _{K of} the machine head 5.

Claims (6)

Drive arrangement for a cover gumming machine with machine head driven by a drive motor and rotatable about a vertical axis with a plurality of quill shafts with plates for receiving covers, the quill shafts being rotatably mounted about axes arranged parallel to the vertical axis and each having a pinion gear with a meshes around the vertical axis and a gear ring that can be rotated relative to the machine head,
characterized by
that the ring gear (24), with which the pinions (10) of the quill shafts (8) are engaged, is connected to a drive motor (auxiliary motor 27) separate from the drive motor (main drive). Drive arrangement according to claim 1, characterized in that the toothed ring (24) can be driven by the separate drive motor (auxiliary motor 27) such that the speed (n₂₄) of the toothed ring (24) decreases with increasing speed (n _K ) of the machine head (5) . Drive arrangement according to claim 2, characterized in that the connection between the ring gear (24) and the separate drive motor (auxiliary motor 27) takes place via a differential gear (28), the rotating housing of which is driven by the separate drive motor (27), the one output shaft (Pinion 33) of the differential gear (28) is geared to the ring gear (24) and the other output shaft (pinion 32) is connected to the first drive motor (main drive). Drive arrangement according to claim 3, characterized in that the connection of the one output shaft (pinion 32) of the differential gear (28) to the first drive motor (main drive) takes place via the machine head (5) and that the transmission ratio (i _32/5 ) of this output shaft (32) to the machine head (5) is as large as the transmission ratio (i _33/24 ) from the other output shaft (pinion 33) of the differential gear (28) to the ring gear (24). Drive arrangement according to Claim 2, characterized in that the toothed ring (24) is driven by the separate drive motor (auxiliary motor 27) via a fixed transmission ratio and in that the speed (n₂₇) of the separate drive motor is adjusted via a control device (41) as a function of the speed ( n _K ) of the machine head (5) can be changed. Drive arrangement according to claim 2, characterized in that the toothed ring (24) is driven by the separate drive motor (auxiliary motor 27) via a gear with a variable transmission ratio and that this transmission ratio can be changed as a function of the speed (n _K ) of the machine head (5) .

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