Patent Application
20180345614
The invention relates to a path-controlled or mechanical press according to the preamble of claim 1.
DE-OS-1 627 435 describes a forging press, in which an eccentric of a drive shaft engages in an opening of a sliding block. The sliding block is braced by an upper, convex side and by a lower, convex side, respectively, against a corresponding concavely shaped surface of a slide guide. In the course of one revolution of the drive shaft, the sliding block swings about a pendulum axis that extends through a lower region of the sliding block.
WO 2007/091935 A1 describes a drive system for a press, in which a first motor drives a flywheel that can be coupled to the press, and in which a second motor is also provided for the drive system of the press.
The object of the invention is to indicate a path-controlled press in which a drive unit takes up little structural space.
This object is achieved according to the invention for an above-mentioned path-controlled press with the characterizing features of claim 1.
Such an embodiment of the press drive enables an especially low design of the drive, wherein, for example, relatively small flywheel diameters can be used. This allows an ideal combination with a force transmission by means of a sliding block, since such force transmission can likewise be realized with low structural height.
The first motor serves substantially to drive the flywheel and to follow up at least some of the energy removed from the flywheel.
The second motor serves essentially to speed up and/or slow down the drive shaft decoupled from the flywheel in a state decoupled from the flywheel. Furthermore, the second motor may serve to bring in additional drive energy even in the decoupled state. The energy of deceleration occurring upon deceleration may be fed by way of the converter to the first motor in one possible detail design. By motors in the sense of the present invention is meant electric motors in each case.
By a sliding block is meant in the sense of the invention an element which can move in forcible guidance with respect to a slide guide surface. The slide guide surface comprises in particular the pressure-input-side surface and the pressure-output-side surface for the guidance of the sliding block.
By a driver is meant in the sense of the invention, for example, an eccentric or a crank pin. In the interest of a large force transmission, the driver is preferably an eccentric of the drive shaft, which runs for example with a circular circumference in an opening of the sliding block.
By a slide guide is meant in the sense of the invention a movable component of the press, which takes up a working pressure from the sliding block during a pressure stroke or reshaping process and passes it on. In principle, the slide guide may be formed as a common structural component with a ram of the press. In other embodiments, however, another mechanism of any structural kind, for example, a wedge deflection, may be provided between the slide guide and the ram. In the region of the force uptake in the pressing direction, the slide guide preferably has a pressure piece that has optimized material properties for abutment against the sliding block.
A press in the sense of the invention generally involves a press for forging, punching, deep drawing, or any other reshaping process for which path-controlled presses are used.
In a preferred enhancement, the coupling is engaged in a normal operating mode when a drive-side and an output-side 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. This allows a substantial reduction of wear on the coupling.
In the interest of a simple and space-saving design, the first motor and the flywheel may be arranged coaxially to one another. Preferably, they are integrated as a structural unit in a flywheel motor. Such a flywheel motor advantageously dispenses with a bulky belt drive plus an additional motor bracket. In another possible embodiment, the motor and the flywheel are arranged coaxially to one another and they are preferably joined together by a gearing, preferably a planetary gearing, so that depending on the requirements it is also possible to realize up-gearing. This can make possible especially small flywheel masses.
It is generally advantageous that the flywheel can be coupled to the drive shaft without gearing up, wherein the flywheel is arranged, in particular, concentric to the drive shaft. Such a simple design with no countershaft can be especially advantageously integrated when the flywheel can be designed with sufficiently small diameter. This, in turn, is made possible by the drive concept according to the invention.
To avoid expensive gearings and in the interest of a compact design, in a preferred embodiment, the second motor is designed as a torque motor arranged concentric to the drive shaft. By a torque motor is meant generally and in the sense of the invention a heavy-torque, high-pole motor, generally running by way of a hollow shaft. Torque motors furthermore have a high torque even from standstill.
Especially advantageously, a brake of the drive shaft may be provided, concentric to the torque motor and overlapping in the axial direction with the torque motor. In particular, in this case, the brake may be placed in the region of a hollow shaft of the torque motor, so as to also utilize this structural space. The brake may be a mechanical brake for generating heat of friction or also an electrical regenerative brake.
The brake may be a holding brake to secure a standstill when the press is not in operation. More preferably, it may be a spring-loaded brake, which can be pneumatically released and hydraulically and/or electromagnetically engaged.
In general, it is advantageously provided that the drive shaft, starting from a resting start position, passes through an angle of rotation of more than 360° by way of the pressure stroke, up to a resting stop position. Preferably, the angle of rotation is between 370° and 450°. This enables a larger acceleration path before the actual pressing process or a larger braking path after the actual pressing process, so that the corresponding motors and brakes may be dimensioned accordingly smaller. This particularly applies to the second motor.
On the whole, a drive as described above makes possible a high power. In this way, with a given charging time, a large drop in rotational speed can be recharged. A high permissible drop in rotational speed permits a small flywheel, which is of advantage.
In order to avoid contamination of a work zone with lubricating grease, it may be advantageous to lubricate a main bearing site of the drive shaft by means of a circulating oil lubrication.
In a generally preferred embodiment of the invention, it is proposed that the pressure-input-side sliding surface on the sliding block and/or the pressure-output-side sliding surface of the sliding block are straight in configuration. Thanks to the straight shape of a pressure-input-side sliding surface or both pressure-input-side sliding surfaces, a simple fabrication of the sliding block is possible.
In a generally preferred embodiment of the invention, it is proposed that the 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 in each case has the other concave or convex curvature, respectively. Thanks to the concave or convex shaping of the pressure-input-side sliding surface, a force transmission by the sliding block can be achieved in a simple way, corresponding to a slider-crank mechanism. At the same time, a large bearing surface is achieved in the region of the sliding surface, so that a design for large pressing forces can be achieved in a simple way. On the whole, this gives an optimized force vs. path curve.
In particular, the pressure-input side, concave curvature and the pressure-output side, convex curvature may each be formed as a circular arc. The curvatures are preferably arranged concentrically about the same point, through which also runs a pendulum axis of the sliding block. The two sliding surfaces thus form forcibly guiding slide guide surfaces of a slide guide mechanism for the sliding block.
In a first variant of the invention, the sliding block has the concave sliding surface on the pressure-input side and the convex sliding surface on the pressure-output side.
This corresponds to the kinematics of a slider-crank mechanism, in which the dead center of a working stroke or pressing process is present in an extended position of the slider-crank mechanism.
In a second variant of the invention, the sliding block has the convex sliding surface on the pressure-input side and the concave sliding surface on the pressure-output side. This corresponds to the kinematics of a slider-crank mechanism, in which the dead center of a working stroke or pressing process is present in a coincident position of the slider-crank mechanism.
The design of a path-controlled press according to the invention generally makes possible a low structural height. This results in shorter spring lengths for the uprights, ram, and/or slide guide of the press. In this way, the rigidity is improved when compared to traditional eccentric presses with the same upright design.
Moreover, the design according to the invention makes possible an especially long length of a rigid unit composed of slide guide and ram for a given structural height of the press. This allows an especially good lateral guidance of the ram and the rigid unit, even under large pressing forces.
In general, it is advantageously provided that the sliding block executes a pendulum movement about a pendulum axis, wherein the pendulum axis is situated outside the sliding block. In general, the pendulum axis is preferably disposed fixed in place relative to the slide guide. Assuming a linear forced guidance of the slide guide, the sliding block then provides a transfer of motion relative to the pendulum axis or relative to the slide guide in the manner of a slider-crank mechanism. In the sense of the invention, depending on the requirements, another forced guidance of the slide guide is also conceivable, so that the kinematics of a slider-crank mechanism is only one of various possible transfers of motion. The invention is not limited to the specifically described variants of slider-crank mechanisms.
In a preferred enhancement, it is proposed here that the driver travels about an eccentric axis in the sliding block, wherein the eccentric axis has a spacing R relative to the shaft axis, while the eccentric axis has a spacing L relative to the pendulum axis, and wherein: L:R>=4. Furthermore, especially preferably, 12>=L:R>=5 also applies. For a linear guidance of the slide guide, accordingly, the quantities R and L denote the characterizing quantities of the push rods of an analogous slider-crank mechanism, and, in an analogous slider-crank mechanism, the quotient R:L corresponds to the push rod ratio lambda (or L:R=1/lambda). Such a design of the mechanism of the press according to the invention allows a large ratio between a pressing force acting in a guiding direction of the pressure piece and a normal force acting perpendicular thereto. A certain normal force is desirable in this case in order to assure a good abutment of the slide guide and/or the ram at a lateral guide. By combination with the use of a sliding block, a large inverse push rod ratio 1/lambda is made possible, without the need for the structural height of the press to become larger. Thanks to the above-mentioned features, even with low structural height and correspondingly good rigidity, one may achieve similar pressure dwell times (characteristic: lambda) to those of traditional eccentric presses with push rods.
In the first variant, analogous to the extended position of a slider-crank mechanism, the pendulum axis is situated on the side of the pressure-input direction relative to the shaft axis. The pressure dwell time here, for the same cycle time, is equal to that of traditional presses with push rods. In the second variant, similar to the coincident position of a slider-crank mechanism, the pendulum axis is situated on the side of the pressure-output direction relative to the shaft axis. In this case, the pressure dwell time for the same cycle time is longer than that of traditional presses with push rods, but this may be of advantage in the case of special reshaping methods or materials.
In a generally preferred enhancement of the invention, an adjusting element, especially one in the form of an adjustably rotatable eccentric ring, is arranged between the driver and the sliding block. Such an adjusting element may be used, for example, to adjust the height of a ram.
In one preferred embodiment of the invention, the slide guide is moved during the pressure stroke essentially in a line with a ram of the press. This corresponds to a linear and direct transmission of the pressing force.
In an alternative embodiment of a press according to the invention, a force deflection occurs between the slide guide and a ram of the press. Preferably, the force deflection may occur by means of a wedge. In this way, the general advantages of a wedge press may be combined with the advantages of a press according to the invention.
In a generally advantageous enhancement of the invention, there is provided an ejecting mechanism which is stationary relative to the slide guide and has an ejector which is movable relative to the slide guide and acts on a workpiece, wherein the ejecting mechanism is activated by the movement of the sliding block. This permits a simple and effective ejecting of a workpiece after a pressing process. More preferably, such an ejecting mechanism is combined with a sliding block of the second embodiment, in which a convex sliding surface is present at the pressure-input side. This means, for otherwise the same dimensioning, a longer path of the sliding block in the region of the pressure-input-side sliding surface, which allows an especially simple and effective transfer of motion to the ejector. The activating of the ejector may occur, for example, by a ramp, cam, or similar structure formed on the sliding block, which activates the ejector upon reaching a corresponding position of the drive shaft against a restoring spring force.
In a preferred detail configuration, a mechanism may be arranged between the sliding block and the ejector, so that the force and motion sequence of the ejector are further optimized. In particular, the mechanism may be, for example, a steering mechanism, a deflecting lever or the like.
Further advantages and features will emerge from the exemplary embodiments described below as well as from the dependent claims.
Preferred exemplary embodiments of the invention shall now be described and explained in more detail based on the appended drawings.
The path-controlled press of the invention according to the exemplary embodiment of
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.
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.
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.
The sliding block 5 has a pressure-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.
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.
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.
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
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.
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.
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.
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.
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).
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.
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.
The above described mounting and movement of the sliding block are further explained in
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.
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
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.
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.
A drive of a press according to the invention will be described below.
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.
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.
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.
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.
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.
In particular, the view of
Now, the above described drive system functions as follows:
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.
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.
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.
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°.
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.
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.
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.
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.
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
In the exemplary embodiment of the invention shown in
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
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.
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.
Of course, other kinematics are also conceivable, such as eccentric slider crank mechanisms with a configuration of the sliding block according to the invention.
In the exemplary embodiment shown in
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.
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.
After moving through the working stroke or the pressing process, the ramp 27 begins to press the ejector 24 in via the sphere 28.
After this, the sliding block 5 moves further to the left in the representation of
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.
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.
The example of
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.
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.
Of course, the specific features of the preceding exemplary embodiments may be combined with each other as required.
WF Angle between Fs and Fp
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2015 222 994.7 | Nov 2015 | DE | national |
| 10 2015 222 995.5 | Nov 2015 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2016/077224 | 11/10/2016 | WO | 00 |
