POWDER PRESS HAVING TOGGLE LEVER DRIVE AND ELECTRIC DRIVE

Abstract

The invention relates to a powder press (1) for producing a pressed article from a material that can be pressed, having a press frame (10), an upper and/or lower punch assembly (14) and a die assembly, which define a molding cavity, into which the material that can be pressed can be introduced, and an electric drive unit (12) which is operatively connected to the punch assemblies (14) and/or the die assembly, wherein, in order to mold the pressed article, the punch assemblies (14) and the die assembly can be moved relative to each other along a pressing axis (18) and pressed against each other by means of the electric drive unit (12). Furthermore, the operative connection between the electric drive unit (12) and one of the punch assemblies (14) comprises a toggle lever drive (16) which moves the punch assembly (14) into a pressing end position along the pressing axis (18).

Claims

1. A powder press for producing a pressed article from a material that can be pressed, the powder press comprising: a press frame, an upper and/or lower punch assembly and a die assembly, which define a molding cavity into which the material that can be pressed can be introduced, and an electric drive unit which is operatively connected to the punch assembly(ies) and/or the die assembly, wherein, in order to mold the pressed article, the punch assembly(ies) and the die assembly are adapted to be moved relative to each other along a pressing axis and pressed against each other by means of the electric drive unit, wherein the operative connection between the electric drive unit and one of the punch assembly(ies) comprises a toggle lever drive which moves the one punch assembly into a pressing end position along the pressing axis.

2. The powder press according to claim 1, wherein the toggle lever drive is arranged between the electric drive unit and the one punch assembly, wherein, on a drive train of the electric drive unit, a first lever and a second lever are each swivelably hinged to respective first ends of the first and second levers symmetrically to the pressing axis, and a respective first arm for connection to the press frame of the powder press and a respective second arm for connection to the punch assembly are each swivelably hinged to respective second ends of the first and second levers.

3. The powder press according to claim 1, wherein kinematic dimensions of the toggle lever drive are determined such that a pressing force is produced as a function of a pressing movement in accordance with a predefined compaction curve in order to produce the pressed article.

4. The powder press according to claim 1, wherein the electric drive unit has a spindle drive having a servo motor assembly and sensors for detecting rotation angle, rotational speed and/or torque in order to regulate the servo motor assembly.

5. The powder press according to claim 1, wherein at least one position sensor is arranged in order to detect a position of the punch assembly(ies) to transmit a signal to a control unit which is used to regulate the servo motor assembly.

6. The powder press according to claim 4, wherein the servo motor assembly is a hollow shaft electric motor in order to produce a regulated rotary drive.

7. The powder press according to claim 1, wherein the pressing end position can be set by means of mechanical fixed stops which are height-adjustable and comprise punch carriers configured as cylinders arranged concentrically to each other.

8. The powder press according to claim 7, wherein, in the pressing end position, the cylinders of the mechanical height-adjustable fixed stop having a lower axial end face surface each rest on an upper end face surface of a setting ring which is configured in the form of a single-thread screw face in order to adjust the height of the mechanical fixed stops.

9. The powder press according to claim 8, wherein the lower axial end face surface of the mechanical height-adjustable fixed stop is configured complementarily to the upper end face surface of the setting ring, such that by rotating the setting ring by means of an actuating drive the height of the mechanical fixed stop is adjusted.

10. The powder press according to claim 7, wherein the height of the pressing is adjusted by a synchronized rotating of the setting rings.

11. The powder press according to claim 10, wherein the actuating drive is configured as an electric motor in order to individually and synchronously drive the setting rings.

12. The powder press according to claim 1, wherein the toggle lever drive comprises bearings which are pretensioned by means of hinge elements in such a way in order to reduce play in the bearings.

13. The powder press according to claim 12, wherein the hinge elements are configured as solid-body joints which have bearing receptacles which are connected to each other by means of struts which are arranged in a diamond form.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0036] The invention is explained in greater detail below with reference to the exemplary embodiments depicted in the figures, wherein:

[0037] FIG. 1 shows a schematic depiction of a toggle lever drive which is arranged in a powder press in order to move an upper punch assembly;

[0038] FIG. 2 shows a schematic depiction of the toggle lever drive according to FIG. 1 having solid-body joints;

[0039] FIG. 3 shows a schematic depiction of a solid-body joint of the toggle lever drive according to FIG. 1;

[0040] FIG. 4 shows a schematic depiction of an adjustable fixed stop;

[0041] FIG. 5 shows a graphical depiction of a compaction curve of a powder during the pressing operation and the kinematics of the toggle lever drive.

DETAILED DESCRIPTION OF THE EMBODIMENTS OF THE INVENTION

[0042] FIG. 1 shows a top view of an upper part of a powder press 1. An upper region of a powder press 1 is solely depicted in FIG. 1, wherein a press frame is generally labeled with 10 and also comprises an upper press frame 10. A drive unit 12 which is an electric drive unit 12 is arranged on the upper press frame 10. The powder press 1 comprises, between the upper press frame 10 and an upper punch assembly 14, a toggle lever drive 16 which is arranged in such a way that it is operatively connected, on the one hand, to the drive unit 12 and, on the other hand, to the upper punch assembly 14 in order to move the latter in the direction of a pressing axis 18. A drive train 20 extending from the drive unit 12 in the direction of the upper punch assembly 14 is coupled to the toggle lever drive 16.

[0043] The comprised toggle lever drive 16 realizes, by way of a suitable geometric assembly and formation according to the lever principle and the transmission ratios, that the deflections realized by the actual drive unit 12 are multiplied. Within the framework of the invention, a toggle lever is understood to be a device or respectively an element for transmitting forces and/or transferring forces, which comprises at least two single-arm levers having a common end point (as a rule, configured as a movable pivot point), wherein the free ends of the single-arm levers which are supported against one or more bodies can be moved under the influence of a force acting on the common end.

[0044] The toggle lever drive 16 comprises, symmetrically to the pressing axis 18, at least one first lever 22 and one second lever 24 each, which are each swivelably hinged to a first end of the levers 26 on the drive train 20. A first arm 30 for connection to the upper press frame 10 of the powder press 1 and a second arm 32 for connection to the upper punch assembly 14 are each swivelably hinged to a second end 28 of each lever. Accordingly, a four-bar system is formed, which transmits the movement originating from the drive unit 12 to the upper punch assembly 14 such that the latter is moved along the pressing axis 18. The comprised joints are generally labeled with 34 and are arranged between the arms 30, 32 and levers 22, 24 and to the drive train 20, as well as the articulation points to the upper press frame 10 and the upper punch assembly 14. The joints 34 are preferably roller bearings. To ensure that the movement and the produced pressing force is transmitted directly and free of play to the upper punch assembly 14, it is provided that the bearings are pretensioned by means of solid-body joints 36. Solid-body joints 36 provide a flexible connection between first and second structural components. In FIG. 2, the upper part of a powder press 1 is depicted, from which the assembly of solid-body joints 36 in the toggle lever drive 16 is visible.

[0045] In FIG. 3, the solid-body joints 36 provided in the powder press 1 are individually schematically depicted. In order to realize a highly accurate positioning of an object relative to another object and/or a stationary coordinate system, solid-body joints 36 within the framework of solid-body joint modules are known. A solid-body joint 36 is, in general, understood to be a body which comprises a point having reduced stiffness. The reduced stiffness is, as a rule, realized by a local reduction in the cross-section or by a suitable shaping.

[0046] According to an embodiment depicted in FIG. 3, a solid-body joint 36 is an elongated element which is configured mirror symmetrically to a longitudinal axis 38. At a first end and a second end, bearing receptacles 40 are configured, in which shafts or respectively axes can be received in bearings. In order to produce the required reduced stiffness, struts 42 are provided between the bearing receptacles 40, which struts span between them, for example, an elliptical shape or a diamond shape. Other shapes are conceivable, wherein, on the one hand, a certain flexibility in a region and, on the other hand, a stiffness overall are to be observed such that a plurality of struts having a possibly reinforced central region can also be provided. Thanks to the shaping of the solid-body joint 36, a distance between the bearing receptacles 40 can be modified, in particular can be enlarged, during the pressing together of the struts 42, i.e. during the application of pressure vertically to the longitudinal axis 38.

[0047] In FIG. 4, a fixed stop device 50 is depicted, in order to specify a pressing end position. A pressing position circumscribes a position of the components of the tool used in a press, wherein punches are inserted preferably from both sides into a die opening and compress a material that can be pressed introduced therein. A pressing end position is a position in which the maximum pressing force preferably acts by way of the punches on the material located in the die opening. In the pressing end position, the punch carriers 52 are in particular supported rigidly and in a force-transmitting manner on fixed stops. In particular, the use of height-adjustable fixed stop devices 50 is advantageous.

[0048] A punch assembly, for example the upper punch assembly 14, comprises in general punch carriers 52, to which a punch (not depicted) is in each case affixed. The punch carrier 52 has an attachment surface which is preferably annular such that further inlying punches or respectively elements allocated to these punches can be guided through a central through-opening 56. The assembly is preferably arranged rotationally symmetrically around the pressing axis 18, along which the punches can be moved. In FIG. 4, a setting ring 58 is depicted, which is configured to set the pressing end position. As a result, tool wear can in particular be offset, which otherwise leads to mispresses. The punch carrier 52 rests with a lower axial end face surface 60 on an upper end face surface 62, i.e. a support surface, of the setting ring 58. The upper end face surface 62 for the allocated punch carrier 52 is configured as a helical ramp in the form of a single-thread screw face, and the thread ends 64 and 66 of the screw face, comprising a thread, are connected by a vertical connecting surface 68. The corresponding axial lower end face surface 60 of the punch carrier 52 is configured complementarily. The result of rotating the setting ring 58 is that, depending on the rotational direction, the allocated punch carrier 52 is raised or lowered. As a result, the height of the pressing end position can be modified or respectively set by way of the stroke of the punch carrier 52. In an embodiment of the setting ring 58, this can be operatively connected to an outlying adjustment drive 70 and be made to rotate by means of the latter. For example, the operative connection can be provided by means of corresponding teeth of the setting ring 58 and driving wheel of the adjustment drive 70. A belt drive, spindle drive, direct drive of the setting ring 58 are also conceivable. The adjustment drive 70 can be an electric actuating drive which makes it possible to individually specify the pressing end position. However, multiple adjustment drives 70 can also be coordinated with one another by a provided control unit such that a synchronous height adjustment of multiple punch carriers 52 is achieved.

[0049] FIG. 5 shows a force-path diagram 80 in order to illustrate a pressing operation in the powder press 1. In the force-path diagram, the y-axis which is allocated to the force to be applied is labeled 82. A pressing stroke travel is depicted on the x-axis, labeled with 84. To a large extent, no pressing force is required in the initial phase of a pressing cycle until the upper punch assembly or respectively the tool strikes the material that can be pressed filled in the die assembly. This initial phase should be effected as quickly as possible, since a cycle time can thus be shortened. For the pressing operation, the pressing force increases and shows a progressive pressing force course, wherein the maximum pressing force is achieved in a pressing end position. Accordingly, a large force is to be achieved with a minimum pressing stroke travel in the region of the pressing end position. This course is labeled 88 in the depiction and is dependent, inter alia, on the powder material that can be pressed and the filling height.

[0050] It is precisely this course of a force-path ratio which is fulfilled in a virtually optimum manner by a toggle lever drive 16, as depicted with the curve 90. Thus, this can be moved in an initial phase at high speed and with a great distance at low force up to close to the dead center of the toggle lever mechanism. In the region of the dead center, i.e. at a virtually extended position of the comprised levers or respectively arms, a large pressing force can be transmitted. Here, only the smallest distances are covered, but the transmittable pressing force is virtually maximal. Moreover, the arrangement of the toggle lever mechanism 16 allows movement into or respectively out of the pressing end position at high speed such that the cycle time is shortened overall.

[0051] In FIG. 5, the force-path curve 90 shows a corresponding course of a toggle lever drive with an adapted transmission ratio. By adapting the transmission and the leverage ratios of the toggle lever drive, an approximation to the ideal course of a pressing operation, illustrated by the course 88 of the powder compaction, can be achieved, wherein the optimized force-path curve 90 constantly runs above the powder compression curve 88.