Path-controlled press having a sliding block

Abstract

A path-controlled press, with at least one drive shaft having a driver that is eccentric relative to a shaft axis, and a sliding block, wherein the sliding block is driven by the driver to perform a forcibly actuated movement During the execution of a pressure stroke, the sliding block is guided on at least one sliding surface on the pressure side in relation to a pressure-side surface of a slide guide. The sliding block has a sliding surface on the pulling side opposite the sliding surface on the pressure side, which is guided on a surface of the slide guide on the pulling side. The sliding surface on the pressure side of the sliding block has a concave or convex curvature. The sliding surface on the pulling side of the sliding block has another respective concave or convex curvature.

Claims

1. A path-controlled press, comprising: at least one drive shaft having a driver that is eccentric relative to a shaft axis (W); and a sliding block, wherein the sliding block is driven by the driver to perform a forcibly guided movement, wherein during execution of a pressure stroke, the sliding block is guided on at least one sliding surface on a pressure-input side in relation to a pressure-input-side surface of a slide guide, wherein the sliding block has a sliding surface on a pressure-output side lying opposite the at least one sliding surface on the pressure-input side, the sliding surface on the pressure-output side being guided on a pressure-output-side surface of the slide guide, wherein a drive of the at least one drive shaft comprises a first motor, a flywheel which is drivable by the first motor, and a second motor, wherein the flywheel is detachably connectible to the at least one drive shaft by means of a coupling, and wherein the at least one drive shaft is drivable via the second motor; wherein the first motor and the flywheel are disposed on a first end of the at least one drive shaft and arranged coaxially to one another and to the at least one drive shaft; and wherein the second motor is a torque motor disposed on a second end of the at least one drive shaft opposite the first motor and the flywheel and wherein the second motor is concentric to the at least one drive shaft, wherein an ejecting mechanism is provided in a ram of the press, which has an ejector that is movable within a guide of the ram, and acts on a workpiece, wherein the ejecting mechanism is activated by movement of the sliding block.

2. The path-controlled press as claimed in claim 1, wherein the coupling is configured to engage the flywheel to the at least one drive shaft when a drive shaft and flywheel rotational speed at the coupling are at least approximately equal, wherein an equalizing of the rotational speeds occurs by a targeted actuation of the second motor.

3. The path-controlled press as claimed in claim 1, wherein the first motor and the flywheel are integrated as one structural unit in a flywheel motor.

4. The path-controlled press as claimed in claim 1, wherein the flywheel can be coupled without gearing up to the at least one drive shaft, while the flywheel is arranged concentric to the at least one drive shaft.

5. The path-controlled press as claimed in claim 1, wherein a brake of the at least one drive shaft is provided, being concentric to the torque motor and overlapping the torque motor along the shaft axis.

6. The path-controlled press as claimed in claim 1, wherein the at least one drive shaft starting from a resting start position passes through an angle of rotation between 370° and 450° via the pressure stroke up to a resting stop position.

7. The path-controlled press as claimed in claim 1, wherein the at least one pressure-input-side sliding surface on the sliding block has a concave or convex curvature, wherein the pressure-output-side sliding surface of the sliding block has the other of the concave or convex curvature, respectively.

8. The path-controlled press as claimed in claim 7, wherein the sliding block executes a pendulum movement about a pendulum axis, wherein the pendulum axis is situated outside the sliding block.

9. The path-controlled press as claimed in claim 8, wherein the driver travels about an eccentric axis in the sliding block, wherein the eccentric axis has a spacing R relative to the shaft axis, wherein the eccentric axis has a spacing L relative to the pendulum axis, and wherein: 12>=L:R>=5.

10. The path-controlled press as claimed in claim 1, wherein an adjusting element in the form of an adjustably rotatable eccentric ring, is arranged between the driver and the sliding block.

11. The path-controlled press as claimed in claim 1, wherein a pressure piece is moved during the pressure stroke essentially in a line with the ram of the press.

12. The path-controlled press as claimed in claim 1, wherein a wedge is located between a press frame and the ram of the press.

13. The path-controlled press as claimed in claim 1, wherein gearing is arranged between the sliding block and the ejector.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Preferred exemplary embodiments of the invention shall now be described and explained in more detail based on the appended drawings.

(2) FIG. 1 shows a schematic cross-sectional view of a first exemplary embodiment of a path-controlled press according to the invention, wherein the sectioning plane runs parallel to a drive shaft.

(3) FIG. 2 shows the press from FIG. 1 in a cross-sectional view with sectioning plane along line I-I running perpendicular to the drive shaft.

(4) FIG. 3 shows a cross-sectional view along line II-II of the press from FIG. 1 with an adjusting element.

(5) FIG. 4 shows a sketch of a sliding block drive as a detail of the press from FIG. 1.

(6) FIG. 5 shows a sketch of a second exemplary embodiment of the invention with a sliding block drive and a wedge drive combined with it.

(7) FIG. 6 shows a sketch of a third exemplary embodiment of the invention, wherein another variant of the sliding block is present with convex sliding surface at the pressure-input side.

(8) FIG. 7 shows a sketch of a fourth exemplary embodiment, in which an ejecting mechanism is coupled to a sliding block drive.

(9) FIG. 8 shows a sketch of a fifth exemplary embodiment, in which an ejecting mechanism comprises a gearing.

DETAILED DESCRIPTION

(10) The path-controlled press of the invention according to the exemplary embodiment of FIG. 1 comprises a drive shaft 1 with a shaft axis W, which is rotationally mounted in two main bearings 2 opposite a press frame 3. The main bearings 2 preferably have a circulating oil lubrication.

(11) Between the main bearings 2, the drive shaft 1 has an eccentric driver in the form of an eccentric 4. The eccentric 4, which is circular in cross section has an eccentric axis E, which is set off by a radial spacing R from the shaft axis W.

(12) The eccentric 4 engages through a sliding block 5 in a borehole 6 corresponding to the diameter of the eccentric. For assembly purposes, the sliding block is thus composed of several parts.

(13) For its part, the sliding block 5 is guided in a slide guide 7. The slide guide 7 is formed as a housing that is movable relative to the press frame 3. The slide guide 7 comprises a pressure piece 8 on a pressure-input side, on which a pressure-input-side sliding surface 8a is formed. On an opposite side relative to the sliding block, a pressure-output-side sliding surface 7a is formed on the slide guide.

(14) The sliding block 5 has a pressure-input-side sliding surface 5a, which lies against the sliding surface 8a of the pressure piece 8, as well as a pressure-output-side sliding surface 5b, which lies against the pressure-output-side sliding surface 7a of the slide guide 7.

(15) The pressure-input-side sliding surface 5a is formed concave on the sliding block 5. The pressure-output-side sliding surface 5b is formed convex on the sliding block 5. The sliding surfaces 5a, 5b, 7a, 8a are each formed as sections of a cylinder envelope surface, the cylinder axes running parallel to the shaft axis W. In this case, the sliding surfaces 5a, 5b, 7a, 8a run concentrically about a pendulum axis P of the sliding block 5 which is parallel to the shaft axis W. In other words, the cylinder axes of the cylinder envelope surfaces, of which the sliding surfaces 5a, 5b, 7a, 8a each form sections thereof, coincide with the pendulum axis P.

(16) The pendulum axis P thus lies at the pressure-input side and outside the sliding block in the first variant of the sliding block described here, since the pressure-side sliding surface 5a of the sliding block 5 is formed concave. Upon rotation of the drive shaft 1, there results for the sliding block 5 a forcibly guided pendulum movement about the pendulum axis P.

(17) The pendulum axis P is fixed in space relative to the slide guide 7 or the pressure piece 8. The slide guide 7 and the pressure piece 8 provided on it are taken up via lateral guides 9, in which they each can move in linear manner in a direction perpendicular to the shaft axis W. A pressure stroke is executed by a downward movement relative to the representation in FIG. 2, during which the driving force of the drive shaft 1 acts on the pressure piece 8 by way of the sliding block 5. After a bottom dead center of the movement, the driving force of the drive shaft 1 acts on the pressure-output-side sliding surface 7a of the slide guide 7 by way of the sliding block 5, so that slide guide 7 and pressure piece 8 are brought back counter to the pressure stroke direction.

(18) On a bottom side of the slide guide 7 in the present case, there are arranged clamping devices 7b, by which a ram of the press and/or a tool holder and/or a tool may be attached. These perform correspondingly identical movements to those of the slide guide 7 and the pressure piece 8.

(19) Through the guides 9, the slide guide 7 and the pressure piece 8 (or a ram or tool of the press) execute a movement analogous to that of a slider crank drive. An example of a slider crank drive is the transmission of motion between piston and crankshaft in a traditional internal combustion engine.

(20) In this case, the characterizing quantities for the motion are the radial spacing R, on the one hand, and a spacing L between the pendulum axis P and the eccentric axis E. The ratio R:L corresponds in the case of the traditional slider crank drive to the push rod ratio lambda. Given constant angular velocity of the drive shaft 1, the greatest ram velocity will occur when R and L stand at a right angle to each other.

(21) In the present example, the dead center of the working stroke corresponds to an extended position of an analogous slider crank mechanism. That is, the distances R and L at the lowermost point of the tool are collinear and lie one behind the other. The dead center of the working stroke is also designated as the bottom dead center.

(22) By contrast with a pure sinusoidal drive (e.g., sliding bock sliding horizontally in the slide guide with a flat pressure-input-side sliding surface), a maximum ram velocity occurs only 90° after OT (top dead center).

(23) In the present case, the reciprocal 1/lambda=L:R is used in order to optimize the drive of the press according to the invention. It has been determined that a forging press is designed especially advantageously in a range of L:R=8 in regard to the requirements of the motion sequence as well as the pressing forces occurring on the lateral guides 9. In general, the ratio 4<=L:R should be preferred. Especially preferred, one should have 5<=L:R<=12.

(24) Such relatively large inverse push rod ratios have practically no impact on the structural height of a press of the present kind, since the position of the pendulum axis P is defined only by the movement of the sliding block and no particular shaft or mounting is required in this position.

(25) The above described mounting and movement of the sliding block are further explained in FIG. 4. Force vectors Fs, Fp and Fn are also depicted, having the following meaning:

(26) Fs is the overall pressure force exerted by the sliding block 5. Fs lies on a line which runs perpendicular through the eccentric axis E and the pendulum axis P.

(27) Fp is the force component of Fs, acting in the direction of the pressure stroke and on the workpiece. In the specific model of the press in FIG. 1, it involves the vertical force component.

(28) Fn is the force component of Fs standing perpendicular to Fp and also perpendicular to the guides 9 or to the direction of the pressure stroke. The behavior of the moving parts in the guides 9 is definitively determined by Fn.

(29) Any angle WF between Fp and Fs expresses the crank angle and the ratio L:R. Based on the chosen ratio L:R, the angle WF is relatively small in the present example of a press.

(30) A drive of a press according to the invention will be described below.

(31) A drive of the drive shaft 1 comprises a first motor 10, a flywheel 11 that can be driven by the first motor 10, and a second motor 12. The flywheel 11 may be coupled detachably to the drive shaft 1 via a coupling 13. The second motor 12 drives the drive shaft 1 directly. In one possible operating mode, a deceleration or braking of this drive system occurs, in particular, not via a brake, but via the second motor 12.

(32) In the present case, the flywheel 11 and the first motor 10 are combined into a structural unit in the form of a flywheel motor 14. In this case, the first motor 10 and the flywheel 11 are arranged coaxially to each other and to the shaft axis W of the drive shaft 1. Motor 10 and flywheel 11 are directly joined together. No transmission occurs here, for example, by means of a gearing or a belt drive. In other embodiments, not shown, a transmission may be provided between flywheel and first motor, for example, by means of a planetary gearing.

(33) The coupling 13 is arranged directly on the flywheel motor 14 and is likewise situated in a concentric or coaxial positioning on the shaft axis W. Flywheel motor 14 and coupling 13 are arranged at the same end—of two ends—of the drive shaft 1.

(34) The second motor 12 is arranged at the second end of the drive shaft 1, lying opposite to the main bearing 2. The second motor 12 is also positioned coaxially to the shaft axis W via the drive shaft 1. It drives the drive shaft directly and without transmission. For this, the second motor 12 is designed as a torque motor. The second motor 12 accordingly has a high torque even from standstill.

(35) A brake 15 of the drive system is positioned concentrically and overlapping in axial direction with the second motor 12. In particular, the brake is positioned predominantly in a hollow shaft of the second motor 12, whereby it makes optimal use of the structural space. By means of the brake 15 braced against the press frame, when needed, the drive shaft 1 can be braked with high power and/or be brought to a standstill. The brake may be designed as an electrical regenerative brake and/or as a mechanical brake generating frictional heat. In the present instance, the brake 15 is preferably spring-loaded and serves in one possible operating mode as a safety element during standstill of the press. It may be pneumatically released and hydraulically and/or electromagnetically engaged.

(36) In particular, the view of FIG. 2 makes it clear that the flywheel 11 has a sufficiently small diameter so as not to overlap in height with a work zone 16 of the press. This permits optimal access to the work zone 16.

(37) Now, the above described drive system functions as follows:

(38) In general, the flywheel 11 is maintained permanently by the first motor 10 at a desired rotational speed. The second motor 12 serves to accelerate the drive shaft 1 prior to a pressing run from a resting start position to a rotational speed equal or at least approximately equal to the flywheel, while the coupling 13 is still disengaged. When the rotational speed difference is sufficiently small, the coupling 13 is then engaged or closed, so that accordingly, little or no friction loss occurs on the coupling. Accordingly, the coupling is dimensioned relatively small.

(39) By the following pressure stroke and forming process of a workpiece, the drive shaft 1 is braked and energy is removed from the flywheel 11. At the same time, the first motor 10 and the second motor 12 work together with high power in order to compensate at least partly for the energy removal. In this way, the flywheel is dimensioned relatively small.

(40) After the pressure stroke or reshaping process, the drive shaft 1 is once again decoupled from the flywheel 11. With the aid of the brake 15, possibly also by reversal of the second motor 12, the drive shaft 1 is then brought to a standstill.

(41) Especially preferred, an electronic control system of the press is designed such that, starting from the resting start position, the drive shaft 1 passes through an angle of rotation of more than 360° by way of the pressure stroke/reshaping process up to the resting stop position. Preferably, the angle of rotation is between 370° and 450°.

(42) In the present example, the angle of rotation is approximately 390°. For this purpose, prior to an acceleration in the working direction, the drive shaft is rotated in reverse by the second motor 12 at first by approximately 30° counter to the working direction, i.e., 30° before the top dead center. This still does not cause a collision or impairment of the work zone 16, but it significantly enlarges the available angle of acceleration for the subsequent rotation of the drive shaft in the working direction. Because of this, the second motor 12 can be designed relatively small.

(43) FIG. 3 shows the press of FIG. 1 in a cross-sectional view with sectioning plane II-II running perpendicular to the drive shaft. An adjusting element 17 is provided, by means of which a height of the sliding block 5 can be changed or adjusted. This adjustment can also be carried out during an operation. In one possible operating mode, the adjustment can be conducted stepwise between two consecutive strokes.

(44) The adjusting element 17 comprises an eccentric ring 18, which is arranged between the borehole 6 in the sliding block 5 and the eccentric 4 of the drive shaft 1. The eccentric ring 18 may be rotated in its seat via an actuator 19, so that the borehole accommodating the eccentric 4 changes its position relative to the sliding block 5.

(45) FIG. 2 shows a clamping 17a of the adjusting element 17. The clamping 17a may be hydraulically released. The engaging of the clamping 17a may occur hydraulically or mechanically (self-locking), or by a hydraulic and mechanical combination.

(46) FIG. 5 shows a second embodiment of a press according to the invention. Here, a ram and/or tool of the press is/are not advanced directly by the slide guide 7 in linear manner. Instead, a force deflection is provided between the pressure piece and a ram of the press. In the present case, the force deflection occurs by means of a wedge 20, which can be shifted opposite to a support surface 21 fixed to the frame and inclined with respect to the direction of the pressure stroke. The wedge 20 in the present case is firmly connected to the slide guide 7. A ram 22 of the press lies movably against a side of the wedge 20 lying opposite to the support surface 21.

(47) Viewed analogously to a simple slider crank drive, it must be noted that the pendulum axis P is displaced in the course of the transmission of motion in parallel to the support surface 21. Accordingly, in the sense of the invention, the pressure stroke HP is viewed as running in the direction of this offset.

(48) Accordingly, a movement HS of the ram 22 of the press is deflected in the present instance by around 120° to the pressure stroke HP of the slide guide 7. Through such a wedge drive, a particularly uniform force distribution can be achieved over the width of the ram.

(49) With respect to the design of the drive system of the press or the design and transmission of motion of the sliding block, the second exemplary embodiment has no changes relative to the example of FIG. 1.

(50) In the exemplary embodiment of the invention shown in FIG. 6, the sliding block is shaped according to a second variant. Here, the pressure-input-side sliding surface 5a on the sliding block 5 is convex in shape, distinct from the concave shape in the previously described examples.

(51) The pressure-output-side sliding surface 5b is likewise formed on the sliding block 5 as the reverse of the preceding examples, i.e., concave. The corresponding sliding surfaces 7a, 8a on the slide guide are accordingly likewise curved in the reverse way. The sliding surfaces 5a, 5b, 7a, 8a as in the first variant of FIG. 4 are each formed as sections of a cylinder envelope surface, the cylinder axes running parallel to the shaft axis W. The sliding surfaces 5a, 5b, 7a, 8a in turn run concentrically about a pendulum axis P of the sliding block 5, parallel to the shaft axis W.

(52) Thus, the pendulum axis P likewise lies outside the sliding block 5. Unlike the first variant, the pendulum axis P of the second variant lies on the pressure-output side relative to the sliding block 5. For the sliding block 5, once again a forcibly guided pendulum movement about the pendulum axis P results upon rotation of the drive shaft 1.

(53) The second variant also corresponds to an analogous slider crank mechanism with the characterizing quantities L (distance between pendulum axis P and shaft axis W) and R (distance between eccentric axis E and shaft axis W). Unlike with the first variant, however, the dead center of the working stroke corresponds to a coincident position of an analogous slider crank mechanism. That is, the distances R and L at the lowermost point of the tool lie collinear and one above the other.

(54) Of course, other kinematics are also conceivable, such as eccentric slider crank mechanisms with a configuration of the sliding block according to the invention.

(55) In the exemplary embodiment shown in FIG. 7, an ejecting mechanism 23 is integrated into the press, being activated by means of the motion of the sliding block. The ejecting mechanism comprises an ejector 24, which travels in a guide of the ram 22 able to move in linear fashion and able to press against a workpiece (not shown) at the lower end of the ram.

(56) After a pressing process, the ejector 24 is displaced by means of a mechanical forced guidance against the workpiece, ejecting the workpiece from a tool (not shown). In this way, a reliable change of workpiece is made possible in a simple way.

(57) The activating of the ejector 24 takes place by means of a ramp 27 on the sliding block 5. The ramp 27 lies against a head 28 of the ejector 24, being formed as a sphere in the present instance. The sliding block executes its pendulum movement about the pendulum axis P, sliding along the pressure-input-side sliding surfaces 5a, 8a. In this case, at first the ejector 24 is situated in a retracted position, in which it does not press against the workpiece, by means of a spring 29.

(58) After moving through the working stroke or the pressing process, the ramp 27 begins to press the ejector 24 in via the sphere 28. FIG. 7 shows roughly the starting time of this ejection process, the sliding block 5 being in the middle position and the ram 22 in a bottom dead center.

(59) After this, the sliding block 5 moves further to the left in the representation of FIG. 7 and the ramp 27 moves the ejector 24 relative to the ram 22 or to the slide guide 7 against the workpiece. The ejector 24 in this process executes a movement by a stroke HA against the force of the spring 29.

(60) In the present case, the ejector mechanism is illustrated on the basis of the first variant of the sliding block 5 with pressure-input-side concave sliding surface 5a. Especially preferred, the ejector mechanism may also be combined with the second variant of the sliding block 5 with pressure-input-side convex sliding surface 5a. This has the advantage that the linear path of the sliding block 5 along the sliding surface 5a is greater, with otherwise the same dimensioning of the press, which permits a less rigid design of the ramp 27.

(61) By arranging a hydraulic piston 25 having a piston rod 26 in between, the stroke HA of the mechanical ejector 23, 24 can be increased. This means that the large force needed for the ejecting is provided by the mechanical ejector with the small stroke HA. The hydraulic piston increases the stroke HA by the stroke HH. The hydraulic piston 25 is operated via a valve with hydraulic actuation 34.

(62) The example of FIG. 8 shows an enhancement of the ejector mechanism 23, in which a gearing 30 is arranged between the sliding block 5 and the ejector 24.

(63) In the present instance, the gearing 30 is shaped as a deflecting lever, which is mounted in a rotary bearing or swivel bearing 31 on the slide guide 7. The sliding block 5 is connected in a rotary bearing 32 to the deflecting lever, the pivot point of the rotary bearing 32 being flush with the sliding surface 5a. The rotary bearing 32 may also be fashioned as a cam roller. The swivel movement of the deflecting lever then takes place forcibly controlled via the cam roller 32 through the cassette guide 33 arranged on the sliding block 5.

(64) On the deflecting lever 30, lying opposite to the rotary bearing 32, there is formed a ramp 27, which engages with the ejector 24 as in the previous example. The deflecting lever, in particular, makes possible a longer ramp for better actuation of the ejector 24.

(65) Of course, the specific features of the preceding exemplary embodiments may be combined with each other as required.