MXPA01004846A

MXPA01004846A - Device for driving two mold halves of a glass forming machine

Info

Publication number: MXPA01004846A
Application number: MXPA/A/2001/004846A
Authority: MX
Inventors: Hartmann Thomas; Hermening Heinz; Bogert Hermann
Original assignee: Fa Hermann Heye
Priority date: 1999-09-15
Filing date: 2001-05-14
Publication date: 2003-02-17

Abstract

The invention relates to a glass forming machine (5) with brackets (2;3) that are mounted to be pivoted about an axis (4). Every bracket (2;3) is provided with form tool halves (6;7). A first link (10) is articulated to a first articulation point (9) of every bracket (2;3). A second link (12) is articulated to a second articulation point (11) of the first link (10), said second link, in turn, being articulated to a third articulation point (13) of the glass forming machine (5). A rod (14) is articulated to the second articulation point (11), said rod being articulated with its other end to a crank pin (15) of a crank (16). Each of the two cranks (16) is coaxially linked with a gear wheel (17;18). The gear wheels (17;18) arediametrically opposed and engage with an endless screw (21) that is driven by an electric servomotor (29) by means of a transmission (30) to rotate and reciprocate.

Description

- "/ () Device for driving two fasteners with mold means of a vxdrio molding machine F Description of the invention The invention relates to a device according to the preamble of claim 1. In known devices of this type (US 3 066 505 A, US 3 021 644 A, US 2 748 536 A and US 1 974 841 A) each of the hoses are attached to a car that can be moved in a linear fashion in a plane • longitudinal of the glass molding machine. In the first North American patent documents, a rack on the carriage is in engagement with a pinion which is connected to an additional pinion by means of an axle.

The additional pinion is in engagement with an additional rack which can be operated in a reciprocal manner by the common actuator. In the American document 2 748 536 A, the carriage is driven by a piston-cylinder unit and in the document • 20 American 1 974 841 A, this one is driven by a drive roller that runs on a curved zipper. All these devices are expensive, likely to fail and insufficiently precise in their movements for reasons of undesired tolerances.

REF: 128403 In the case of a device that is known per se (US 1 911 119 A, Figures 3, 8 and 19) the two fasteners can rotate on a perpendicular column • common machine. A link bar is articulated at a point of articulation of each fastener in the vicinity of a mold tool means. The other end of the connecting rod is articulated in each case to a stump of a crankshaft. The crankshaft is attached to a respective ee mounted on the machine. The two axes rotationally act in a reciprocal way by • means of a common double acting piston-cylinder unit by means of a lever mechanism. A similar device is known from the document of German patent 1 704 112, FIGS. 2 to 5. The two axes in this case, however, are rotatably driven in a reciprocal manner by a common pneumatic rotary cylinder by means of a reduced straight-wheel apparatus. The object of the invention is to improve and simplify the reciprocal drive of the fasteners. This object is achieved by the features of claim 1.

When molding hollow glass objects, forces arise within the mold tools in both the preform molds of the preform molding station as well as in the finishing molds of the finishing molding station and which try to open the molds. closed mold tools. Any opening is undesirable because when the lines are split then the molten glass can be pressed. Numerous additional devices are known in the art above, with which the mold tools closed • must forcibly be held closed during the molding process. Additional devices for holding closed tools are superfluous in the case of the invention. With the invention the function of closed support of the actuator is supported by the lever mechanism whereby the entire mechanism between the actuator and the fasteners becomes desirably non-linear. The lever mechanisms • cause the closed clamping force that increases when the fasteners, and therefore the mold tools, are in the closed position. The movement of the fasteners can be achieved in a known manner either by rotating or by linear displacement. By means of sprockets and the actuator it is possible to form the device of a way generally simple, cost-effective and with less space, and for the device still produce extremely precise opening and closing movements for the • fasteners. The features of claims 2 to 14 respectively represent the modalities of the device that lead to the advantages during the operation of the device. Each of the characteristics of the claims 15 to 17 provide a stable and compact mode of the device. According to claim 18, a particularly simple and functionally reliable gear wheel mechanism is produced. Straight wheels can be teeth in any convenient manner, for example with straight or inclined teeth. The features of claim 19 allow a highly accurate programmable control of the movements for opening and closing of the fasteners.

In order to achieve sufficient closing clamping forces, the torque of the electric servomotor can remain transversely interchanged during the molding processes. According to claim 20 the mechanism can be placed according to the requirements respective. For example, a small apparatus and / or, for reasons of space, an angular equipment can be used. BRIEF DESCRIPTION OF THE FIGURES • This and other advantages and features of the invention will be explained in more detail herein with the aid of the exemplified embodiments illustrated in the drawings wherein: Figure 1 is a plan view of a first embodiment of the device , partially in section transverse, • Figure 2 is another planar view of the device according to Figure 1, Figure 3 shows the parts of the device according to Figure 1 and 2 in a manner schematic, Figure 4 shows the plan view of an additional embodiment of the device, partially in cross section, Figure 5 shows the parts of the device according to claim 4 in a schematic manner, Figure 6 shows the plan view of a further embodiment of the device and Figure 7 shows another embodiment for the cogwheels and their actuator in a side view.

Figure 1 shows a device 1 for the reciprocal drive of a first fastener 2 and a second fastener 3 which are mounted in such a way that • can rotate on a rotating shaft 4 of a glass molding machine 5 not shown in detail. The first fastener 2 has two first mold tool means 6 and the second fastener 3 has two second mold tool means 7. In the fully closed position of the molds. fasteners 2, 3 shown in Figure 1, the means of • opposite mold tool 6, 7 form a respective mold tool 8, for example a preformed mold or a finishing mold for the production of a hollow glass object. At a first articulation point 9 of each fastener 2, 3 a first connecting rod 10 is articulated, of which Figure 1 shows only that of the second fastener 3. At a distance from the first articulation point 9 a second bar of union 12 se articulates for each first link bar 10 at a second point of articulation 11. Each second link bar 12 is articulated at a third point of articulation 13 of the glass molding machine 5, placed at a distance from the first point of articulation 9 and from the second articulation point 11.

A rod 14 is also articulated at every second point of connection 11 and for its part is articulated to a stump 15 of a crankshaft 16, to a • distance from the second articulation point 11. Each of the two cranks 16 is coaxially joined to a first gear wheel 17 or a second gear wheel 18. The cogwheels 17, 18 are formed in the exemplified embodiments of Figures 1 to 6 as a first worm gear 19 and a second worm gear 20. The gears of • endless screw 19, 20 are in engagement with an endless screw 21 on the diametrically opposite sides. A longitudinal axis 22 of the worm 21 is arranged in a longitudinal plane 23 of the device 1. The longitudinal axis 24 of the crankshafts 16 and the longitudinal axis 25 of the trunnions 15, extend at a right angle to and a distance from the axis 22 longitudinal of the worm 21. An axis 26 of the worm screw 21 is rotatably mounted in a housing 27 of the glass molding machine 5. The shaft 26 is rotatably driven in a reciprocal manner by an actuator 28. The actuator 28 comprises an electric servomotor 29 and a gear mechanism 30, in this case an angular equipment, connected current 25 downstream of the electric servomotor 29 and in connection with drive with the shaft 26. In this way the crankshafts 16 are rotatably driven in a reciprocal manner in opposite directions by means of the common actuator 28. The fasteners 2, 3 then rotate synchronously in a reciprocal manner on the rotating shaft 4 between the fully closed position shown in Figure 1 and the fully open position shown on the left side of Figure 3. Figure 2 shows the additional details of the transmission path for the first fastener • 2. It is explained, with the help of Schematic Figure 3, the operational progress during the operation of the device 1. In this mode exemplified the first articulation point 9 is arranged in the vicinity of the mold tool means 6, 7 (Figure 1) respectively. The second articulation point 11 is arranged in all operating conditions on one side of a line 31 of connection between the first articulation point 9 and the third articulation point 13. This side faces the respective crankshaft 16. In the fully open position of fasteners 2, 3 shown on the left in Figure 3, the longitudinal axes 32 and 33 of the first bar of union 10 and second link bar 12 respectively form an acute angle 34 relative to each other. The angle 34 is, for example, 72 °. In this position • completely open of the fasteners 2, 3, a connection plane 35 connecting the longitudinal axis 25 of the crankshaft journal 15 to the longitudinal axis 24 of the crankshaft 16, is respectively arranged on a first side of a transverse plane 36 of the device 1 that extends through the longitudinal axes 24, 24 of the two crankshafts 16, 16. This first side faces away from • the fasteners 2, 3. In this fully open position of the fasteners 2, 3, the connection plane 35 and the transverse plane 36 form an acute angle 37 between them. This angle 37 is, for example, 20 °. In the fully closed position of the fasteners 2, 3, shown on the right side in Figure 3 and also shown in Figures 1 and 2, the connection plane 35 is respectively arranged on a second side of the transverse plane 36. This second The side faces the fasteners 2, 3. The connecting plane 35 and the transverse plane 36 form an acute angle 39 between them, for example 60 °. At the same time the axes 32, 33 respectively form an obtuse angle 38 between themselves, for example 158 °. ÍS * The mode of the device 1 according to Figures 4 and 5 is similar to that according to Figures 1 to 3. However, the first articulation point 9 is respectively arranged on the rear projection 40 on the fasteners 2, 3 extending beyond the rotary shaft 4. In the fully open position of the fasteners 2, 3 shown on the left side of Figure 5, the longitudinal axes 32, 33 of the tie bars 10, 12 respectively form an angle 41 to each other with at least approximately a right angle. In this fully open position the connection plane 35 and the transverse plane 36 also form an obtuse angle 42, for example 175 ° to each other. In the fully closed position of the fasteners 2, 3 shown to the right of Figure 5, the longitudinal axes 32, 33 of the tie bars 10, 12 respectively form an obtuse angle 43 relative to each other. In this totally closed position of the fasteners 2, 3 the connecting plane 35 and the transverse plane 36 form an acute angle 44 of, for example 82 ° to each other. As also shown in Figure 3, this geometry of the lever mechanism 16, 14, 10, 12 5 also leads in Figure 5 to strengthen the forces clamping devices applied by the electric servomotor 29. The effective length of the connecting bars 10, • 12 between its articulation points 9, 11; 11, 13 is the same. In all the figures of the drawings the same parts of the reference are provided to the same parts. In the mode exemplified according to the Figure 6, device 1 serves for the so-called • open and close parallel of the fasteners 2, 3 in the directions of a double arrow 45. In their trajectories from the open to closed position of the fasteners 2, 3, they are linearly guided in Figure 6 by the guides 46 and 47 of the glass molding machine 5. In Figure 6 the gear mechanism 30 drives the same worm gear 21, 19, • 20 as in the previous figures. The mechanisms of lever 16, 14, 12, 10 in Figure 6, are similar to those of Figures 1 to 3. In the fully open position of the fasteners 2, 3, shown on the left in Figure 6, that the angle 34 is, for example, 60 °. The angle in Figure 6 for example, is approximately 4 °.

In the fully closed position of the fasteners 2, 3, shown on the right in Figure 6, the acute angle 39 is, for example, 60 °. The same • time the longitudinal axes 32, 33 respectively form an obtuse angle 38 of, for example 150 ° to each other. In the embodiment exemplified according to Figure 7 the first sprocket 17 and the second sprocket 18 are formed, as a first straight wheel 47 and a second straight wheel 48 which are in engagement with each other. A shaft 49 of the second straight wheel 48 can be reciprocally rotatably driven by the actuator 28. The actuator 28 could alternatively drive a shaft 50 of the first wheel as well. straight 47.

It is noted that in relation to this date, the best method known to the applicant to carry ^^^ to practice the aforementioned invention, is the conventional for the manufacture of the objects or products to which it refers.

Claims

CLAIMS Having described the invention as above, property is claimed as contained in the following

• claims: 1. The device for actuating a first and a second fastener in a reciprocal manner, wherein each fastener is mounted displaceably in a glass molding machine, wherein each fastener supports at least

10 a mold tool means and a means of

F mold tool of the first fastener cooperates respectively with a second mold tool means of the second fastener to form a mold tool for the production of a glass object

15 hollow, wherein a first link bar is articulated at a first point of articulation of each fastener, wherein a second link bar is articulated

• in a second articulation point of the first bar

20, arranged at a distance from the first articulation point, wherein the second joint bar is articulated at a third articulation point of the glass molding machine, arranged at a distance from the first

point of articulation and the second point of articulation, where a rod is also articulated in the

• second articulation point, and wherein each rod is articulated at a distance from its second articulation point in a stump that can be moved reciprocally by a common actuator, characterized in that each crankpin can

It is driven by a crankshaft, where a crankshaft is coaxially connected to a first sprocket and the other crankshaft is connected coaxially to a second sprocket, and where the sprockets can be operated

15 rotatably by the actuator in opposite directions.
2. The device according to claim 1, characterized in that the first articulation point 20 is arranged in the vicinity of at least one mold tool means, and where the second articulation point is arranged in all operating conditions in a side of a connecting line between the first and third articulation point 25 where the side faces the crankshaft.
3. The device according to claim 2, characterized in that in one position

• fully open of the fasteners, the longitudinal axes of the first and second link bar respectively form an acute angle with each other.
4. The device according to claim 3, characterized in that when the

10 fasteners are in the fully open position, a

The connection plane connecting a longitudinal axis of the crankshaft journal to a longitudinal axis of the crankshaft is respectively disposed on a first side of a transverse plane of the device extending to the crankshaft journal.

15 through the longitudinal axes of the two crankshafts, where the first side faces away from the fasteners.
5. The device according to claim 4, characterized in that the plane of

The connection and the transverse plane form an acute angle between each other.
6. The device according to any of claims 1 to 5, characterized

25 because in a totally closed position of the

Fasteners, the longitudinal ends of the first and second tie bar respectively form an obtuse angle with each other.
7. The device according to claim 6, characterized in that when the fasteners are in the fully closed position, a connection plane connecting a longitudinal axis of the crankshaft journal to a longitudinal axis of the crankshaft,

10 is respectively placed on a second side of a

F transverse plane of the device extending through the longitudinal axes of the two crankshafts, where the second side faces the fasteners.
8. The device according to claim 7, characterized in that the connection plane and the transverse plane form an acute angle with each other. • The device according to claim 1, characterized in that each fastener is mounted to rotate on a rotating shaft of the glass molding machine,
l '# _ mfífeffiftítf ??? B'ih? ^^ M ^ |. ^ faai ^ _ * JMfc¿¿ ^ alft ^^ Mfct¿jBÍ where the first articulation point is respectively arranged on a rear projection on the fastener, extending beyond the rotary axis, and where the second articulation point is arranged in all operating conditions on one side of a connection line between the first and third articulation point, where the side faces away from the crankshaft.
10. The device according to claim 9, characterized in that in a fully open position of the fasteners, the longitudinal axes of the first and second link bar respectively form an angle with each other with at least approximately a right angle.
11. The device according to claim 10, characterized in that in the fully open position of the fasteners, a connection plane extending through a longitudinal axis of the crankshaft journal and a longitudinal axis of the crankshaft, forms an obtuse angle with a transverse plane of the device that extends through the longitudinal axes of the two crankshafts.
12. The device according to any of claims 9 to 11, characterized in that in a totally closed position of the

• fasteners, the longitudinal axes of the first and second link bar respectively form an obtuse angle with each other.
13. The device according to claim 12, characterized in that in the position

10 completely closed fasteners a plane of

• connection extending respectively through a longitudinal axis of the crankshaft journal and a longitudinal axis of the crankshaft, forming an acute angle with a transverse plane of the device extending to

15 through the longitudinal axes of the two crankshafts.
14. The device according to any of claims 1 to 13, characterized in that the effective length of the connecting bars between

20 its points of articulation, is the same.
15. The device according to any of claims 1 to 14, characterized in that the sprockets are formed as a first and a second.

25 second worm gear, 19

and wherein the first and second worm gear are in engagement with a common worm which can be rotationally driven in a reciprocal manner by means of the actuator.
16. The device according to claim 15, characterized in that the worm gears are in engagement with the diametrically opposite sides of the worm. The device according to claim 15 or 16, characterized in that a longitudinal axis of the worm is arranged in a longitudinal plane of the device. 18. The device according to any of claims 1 to 14, characterized in that the sprockets are formed as mutually coupled straight wheels, 20 and where an axis of one of the straight wheels can be rotationally driven in a reciprocal manner by means of the actuator

ivo according to any of claims 1 to 18, characterized in that the actuator comprises an electric servomotor.

F 20. The device according to claim 19, characterized in that the actuator comprises a gear mechanism connected downstream of the electric servomotor.