Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B30—PRESSES
  • B30B—PRESSES IN GENERAL
  • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
  • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
  • B30B1/266—Drive systems for the cam, eccentric or crank axis
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B30—PRESSES
  • B30B—PRESSES IN GENERAL
  • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
  • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B30—PRESSES
  • B30B—PRESSES IN GENERAL
  • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
  • B30B1/40—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by wedge means
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B30—PRESSES
  • B30B—PRESSES IN GENERAL
  • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
  • B30B15/0029—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height
  • B30B15/0035—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height using an adjustable connection between the press drive means and the press slide
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B30—PRESSES
  • B30B—PRESSES IN GENERAL
  • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
  • B30B15/06—Platens or press rams
  • B30B15/068—Drive connections, e.g. pivotal
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B30—PRESSES
  • B30B—PRESSES IN GENERAL
  • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
  • B30B15/32—Discharging presses

Definitions

• the invention relates to a wegoffe 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 supported with an upper, convex side and with a lower, convex side each against a correspondingly concave surface of a backdrop.
• the sliding block oscillates in the course of a rotation of the drive shaft about a pendulum axis, which extends through a lower portion of the sliding block.
• WO 2007/091935 A1 describes a drive for a press in which a first motor drives a flywheel which can be coupled to the press and in which a second motor is additionally provided for driving the press.
• Such an embodiment of the press drive allows a particularly low design of the drive, for example, relatively small flywheel diameter can be used. This allows an ideal combination with a power transmission by means of a sliding block, since such power transmissions are also feasible with low height.
• the first motor essentially serves to drive the flywheel and at least partially track energy removed from the flywheel.
• the second motor essentially serves to accelerate and / or decelerate the drive shaft decoupled from the flywheel in a state decoupled from the flywheel.
• the second motor can serve to introduce additional drive energy even in the coupled state.
• a sliding block is understood to be an element that can be moved positively in relation to a sliding surface.
• the link surface comprises in particular the pressure-side surface and the karmonye surface for guiding the sliding block.
• a driver is understood in the context of the invention, for example, an eccentric or a crank pin.
• 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.
• a movable component of the press which receives a working pressure during a press stroke or forming operation of the sliding block and passes on.
• the scenery can be designed in principle as a common component with a plunger of the press. In other embodiments, however, a further transmission of any type, for example a wedge deflection, may be provided between the link and the plunger.
• the link In the area of the force absorption in the pressure direction, the link preferably has a pressure piece which has optimized material properties for the contact with the sliding block.
• a press in the context of the invention generally relates to a press for forging, stamping, deep drawing or any other forming operation, are used to the wegjobe presses.
• the clutch is closed in a normal operation when a drive-side and an output-side speed at the clutch are at least approximately equal, with an adjustment of the speeds via a targeted control of the second motor. This allows a considerable reduction in wear of the clutch.
• the first motor and the flywheel may be arranged coaxially with each other.
• they are integrated as a structural unit to a flywheel motor.
• a flywheel motor advantageously dispenses with an expansive belt drive together with additional engine console.
• the engine and the flywheel are arranged coaxially and connected via a transmission, preferably a planetary gear, so that, depending on the requirements, also translations can be realized. This can allow especially small flywheel masses.
• the flywheel can be coupled to the drive shaft without translation, wherein the flywheel is arranged in particular concentrically to the drive shaft.
• Such a simple design without a countershaft is particularly advantageous integratable if the flywheel can be designed with sufficiently small diameter. This is in turn made possible by the drive concept according to the invention.
• the second motor is designed as a torque motor arranged concentrically to the drive shaft in a preferred embodiment.
• a torque motor is general and within the meaning of the invention a strong torque, high-poled motor, which normally runs over a hollow shaft.
• Torque motors also have a high torque even from a standstill.
• a brake of the drive shaft can be provided concentrically with the torque motor and in the axial direction with the torque motor overlapping.
• the brake can be placed in particular in the region of a hollow shaft of the torque motor to use this space.
• the brake may be a mechanical brake for generating frictional heat or an electric recuperation brake.
• the brake can be a holding brake to ensure a standstill when the press is not in operation. It can be particularly preferably a spring-loaded brake, which can be pneumatically opened and closed hydraulically and / or electromagnetically.
• the drive shaft starting from a stationary starting position over the pressing stroke, passes through a rotational angle of more than 360 ° up to a stationary stop position.
• it is a rotation angle between 370 ° and 450 °. This allows a greater acceleration path before the actual pressing process or a greater braking distance after the actual pressing process, so that the corresponding motors and brakes can accordingly be smaller in size. This is especially true for the second engine.
• a high performance is possible with a drive described above. This can be recharged for a given load time a large speed drop.
• a high allowable speed drop allows a small flywheel, which is beneficial.
• a main bearing point of the drive shaft is lubricated by means of an oil circulation lubrication.
• the pressure-side sliding surface on the sliding block and / or the train-side sliding surface of the sliding block is executed straight. The straight shape of a pressure-side sliding surface or both pressure-side sliding surfaces a simple production of the sliding block is possible.
• the pressure-side sliding surface on the sliding block has a concave or convex curvature, wherein the tension-side sliding surface of the sliding block has a respective other, concave or convex, curvature.
• the concave or convex shape of the pressure-side sliding surface can be achieved in a simple manner a power transmission through the sliding block, which corresponds to a sliding crank gear. At the same time a large contact surface is achieved in the sliding surface, so that a design for large pressing forces is easy to achieve. Overall, this gives an optimized force-displacement curve.
• the pressure-side, concave and the zug spicye, convex curvature may each be formed in a circular arc.
• the curvatures are preferably arranged concentrically around the same point through which a pendulum axis of the sliding block runs. Both sliding surfaces form for the sliding block forcing sliding surfaces of a sliding gear.
• the sliding block on the pressure side, the concave sliding surface and Werner are the convex sliding surface. This corresponds to the kinematics of a sliding-crank transmission, in which the dead center of a power stroke or pressing operation is present in an extended position of the sliding-crank mechanism.
• the sliding block on the pressure side, the convex sliding surface and Werner are the concave sliding surface. This corresponds to the kinematics of a sliding-crank transmission, in which the dead center of a power stroke or pressing operation is present in a cover layer of the sliding-crank mechanism.
• the sliding block performs a pendulum motion about a pendulum axis, wherein the pendulum axis is arranged outside of the sliding block.
• the pendulum axis is arranged stationary relative to the backdrop. Assuming a linear positive guidance of the slide causes the sliding block with respect to the pendulum axis or with respect to the backdrop then a motion transmission in the manner of a crank gear.
• a linear positive guidance of the slide causes the sliding block with respect to the pendulum axis or with respect to the backdrop then a motion transmission in the manner of a crank gear.
• another forced guidance of the link is conceivable, so that the kinematics of a sliding-crank mechanism is only one of various possible movement transmissions.
• the invention is not limited to the concretely described variants of sliding-crank transmissions.
• Such a design of the transmission of the press according to the invention allows a high ratio between a force acting in the guide direction of the pressure member pressing force and a normal force acting perpendicular thereto.
• the pendulum axis is located with respect to the shaft axis on the side of the printing direction.
• the pressure contact time with the same circulation time is the same as in conventional presses with push rod.
• the pendulum axis is with respect to the shaft axis on the side of the pulling direction.
• the pusher contact time is the same circulation time higher than conventional presses with push rod, but this can be advantageous in special forming processes or materials.
• an adjustment member preferably in the form of an adjustable rotatable eccentric, is arranged between the driver and the sliding block.
• Such an adjustment member can be used for example for height adjustment of a plunger.
• the link is moved during the pressing stroke substantially in line with a plunger of the press. This corresponds to a linear and immediate transmission of the pressing force.
• a force deflection in an alternative embodiment of a press according to the invention takes place between the gate and a plunger of the press, a force deflection.
• the force deflection can be effected by means of a wedge.
• a relative to the backdrop fixed recorded ejection mechanism is provided with a movable relative to the backdrop and acting on a workpiece ejector, wherein the ejection mechanism is actuated by the movement of the sliding block.
• a movable relative to the backdrop and acting on a workpiece ejector wherein the ejection mechanism is actuated by the movement of the sliding block.
• Such an ejection mechanism is particularly preferably combined with a sliding block of the second embodiment in which there is a convex sliding surface on the pressure side. This means with otherwise the same dimensioning a larger path of the sliding block in the area of the pressure-side sliding surface, which allows a particularly simple and effective motion transmission to the ejector.
• the operation of the ejector can be done for example by a formed on the sliding block ramp, cam or similar structure, which actuates the ejector upon reaching a corresponding position of the drive shaft against a restoring spring force.
• the transmission may in particular be a linkage, a lever or the like.
• Fig. 1 shows a schematic sectional view of a first embodiment of a wegzipen press according to the invention, wherein the cutting plane is parallel to a drive shaft.
• Fig. 2 shows the press of Fig. 1 in a sectional view with perpendicular to the drive shaft extending cutting plane along the line l-l.
• Fig. 3 shows a sectional view taken along the line II-II of the press of Fig. 1 with an adjusting member.
• FIG. 4 shows a sketch of a sliding block drive as a detail of the press from FIG. 1.
• Fig. 5 shows a sketch of a second embodiment of the invention with a sliding block drive and a combined wedge drive.
• Fig. 6 shows a sketch of a third embodiment of the invention, wherein another variant of the sliding block with convex side pressure
• Fig. 7 shows a sketch of a fourth embodiment, in which an ejection mechanism is coupled with a sliding block drive.
• Fig. 8 shows a sketch of a fifth embodiment, in which an ejection mechanism comprises a transmission.
• the inventive wegoffe press according to the embodiment of FIG. 1 comprises a drive shaft 1 with a shaft axis W, in two Main bearings 2 with respect to a press frame 3 is rotatably mounted.
• the main bearings 2 preferably have an oil circulation lubrication.
• the drive shaft 1 has an eccentric driver in the form of an eccentric 4.
• the circular cross-section eccentric 4 has an eccentric axis E, which is offset by a radial distance R relative to the shaft axis W.
• the eccentric 4 passes through a sliding block 5 in a corresponding diameter of the eccentric bore 6.
• the sliding block is constructed of several parts.
• the sliding block 5 is in turn guided in a backdrop 7.
• the gate 7 is formed as a relative to the press frame 3 movable housing.
• the gate 7 comprises on a pressure side a pressure piece 8, on which a pressure-side sliding surface 8a is formed.
• On a relative to the sliding block opposite side of a zugcardi sliding surface 7 a is formed on the backdrop.
• the sliding block 5 has a pressure-side sliding surface 5a, which rests against the sliding surface 8a of the pressure piece 8, and a tension-side sliding surface 5b, which bears against the tension-side sliding surface 7a of the slide 7.
• the pressure-side sliding surface 5 a is formed concave on the sliding block 5.
• the tension-side sliding surface 5b is convexly formed on the sliding block 5.
• the sliding surfaces 5a, 5b, 7a, 8a are each formed as cut-outs of a cylinder jacket surface, the cylinder axes extending parallel to the shaft axis W.
• the sliding surfaces 5a, 5b, 7a, 8a extend concentrically about a parallel to the shaft axis W pendulum axis P of the sliding block 5. In other words, fall the cylinder axes of the cylinder jacket surfaces, to which the Sliding surfaces 5a, 5b, 7a, 8a each form cutouts, with the pendulum axis P together.
• the pendulum axis P is thus in the first variant of the sliding block described here on the pressure side and outside of the sliding block, since the pressure-side sliding surface 5a of the sliding block 5 is concave.
• the pendulum axis P is fixed in space with respect to the slide 7 and the pressure piece 8.
• the slide 7 and provided at her pressure piece 8 are received via lateral guides 9, in which they are each linearly movable in the direction perpendicular to the shaft axis W direction.
• the driving force of the drive shaft 1 via the sliding block 5 acts on the tension-side sliding surface 7a of the link 7, so that link 7 and pressure piece 8 are retrieved against the Presshubides.
• On an underside of the gate 7 clamping devices 7b are presently arranged, with which a plunger of the press and / or a tool holder and / or a tool can be attached. These perform correspondingly identical movements as the slide 7 and the pressure piece 8.
• the slide 7 and the pressure piece 8 (or a plunger or tool of the press) perform a movement analogous to that of a sliding crank drive.
• An example of a slider crank drive is the motion transmission between the piston and the crankshaft in a conventional internal combustion engine.
• the variables characterizing the movement are the radial distance R on the one hand and a distance L between the pendulum axis P and the eccentric axis E.
• the ratio R: L corresponds to the push rod ratio lambda in the case of the conventional push-crank drive. At constant angular velocity of the drive shaft 1, a maximum ram speed is present when R and L are at right angles to each other.
• the dead center of the power stroke corresponds to a stretched position of an analogue crank mechanism. This means that the distances R and L in the lowest point of the tool are collinear and consecutive.
• the dead center of the power stroke is also referred to as bottom dead center.
• a maximum ram speed In contrast to a pure sinusoidal sweep (for example, horizontally in the scenery sliding sliding block with a flat pressure-side sliding surface), a maximum ram speed only occurs after 90 ° after TDC (top dead center).
• Fp is the force component of Fs acting in the direction of the press stroke or on the workpiece.
• Fig. 1 is the vertical force component.
• Fn is the force component of Fs, which is perpendicular to Fp and also perpendicular to the guides 9 and the direction of the pressing stroke. Fn decisively determines the behavior of the moving parts in the guides 9.
• a respective angle WF between Fp and Fs is an expression of the crank angle and the ratio L: R. Due to the chosen ratio L: R, the angle WF in the present example of a press is relatively small.
• a drive of the drive shaft 1 comprises a first motor 10, a flywheel 1 1 which can be driven by the first motor 10 and a second motor 12.
• the flywheel 1 1 can be detachably connected to the drive shaft 1 via a coupling 13.
• the second motor 12 drives the drive shaft 1 directly.
• deceleration or braking in this drive does not take place, in particular, via a brake, but via the second motor 12.
• the flywheel 1 1 and the first motor 10 are combined to form a structural unit in the form of a flywheel motor 14.
• the first motor 10 and the flywheel 1 1 are arranged coaxially with each other and to the shaft axis W of the drive shaft 1.
• Engine 10 and flywheel 1 1 are directly connected.
• a translation for example by means of a gear or a belt drive, does not take place here.
• a translation between the flywheel and the first engine may be provided, for example by means of a planetary gear.
• the clutch 13 is disposed directly on the flywheel motor 14 and is also in concentric or coaxial positioning on the shaft axis W. Flywheel motor 14 and clutch 13 are disposed on the same of two ends of the drive shaft 1.
• the second motor 12 is arranged on the second, with respect to the main bearing 2 opposite end of the drive shaft 1. Also, the second motor 12 is positioned coaxially with the shaft axis W above the drive shaft 1. He drives the drive shaft directly and without translation.
• the second motor 12 is designed as a torque motor.
• the second motor 12 has accordingly a high torque already out of a standstill.
• a brake 15 of the drive is concentric and positioned in the axial direction overlapping the second motor 12.
• the brake is predominantly positioned in a hollow shaft of the second motor 12, whereby this space is used optimally.
• the brake can be designed as an electrical recuperation brake and / or friction heat generating, mechanical brake.
• the brake 15 is preferably spring-loaded and, in a possible operating mode, serves as a security element when the press is at a standstill. she can be pneumatically opened or closed hydraulically and / or electromagnetically.
• the view of Fig. 2 makes it clear that the flywheel 1 1 has a sufficiently small diameter so as not to overlap in height with a working area 16 of the press. This allows optimal access to the work area 16
• the flywheel 1 1 is held by the first motor 10 permanently at a desired speed.
• the second motor 12 serves to accelerate the drive shaft 1 before a pressing operation from a stationary start position to a speed equal to or at least approximately the same to the flywheel, while the clutch 13 is still decoupled. At sufficiently low speed difference, the clutch 13 is then coupled or closed, so that correspondingly little or no loss of friction on the clutch occurs. Accordingly, the coupling is relatively small in size.
• the drive shaft 1 is braked and the flywheel 1 1 energy is removed.
• the first motor 10 and the second motor 12 work together with high power to compensate for the energy extraction at least partially. As a result, the flywheel is relatively small dimensions.
• the drive shaft 1 is decoupled again from the flywheel 1 1. With the aid of the brake 15, possibly also by reversing the second motor 12, the drive shaft 1 is then brought to a standstill.
• an electronic control of the press is designed so that the drive shaft 1, starting from the stationary starting position on the pressing stroke / forming process to the stationary stop position passes through a rotational angle of more than 360 °.
• the angle of rotation is between 370 ° and 450 °.
• the angle of rotation is about 390 °.
• the drive shaft is first rotated back by an acceleration in the working direction by the second motor 12 by about 30 ° counter to the working direction, ie 30 ° before top dead center. This causes no collision or impairment of the working area 16, but increases the available acceleration angle for the subsequent rotation of the drive shaft in the working direction significantly.
• the second motor 12 can be made relatively small.
• Fig. 3 shows the press of Fig. 1 in a sectional view with perpendicular to the drive shaft extending cutting plane II-II.
• an additional adjustment member 17 by means of which a height of the sliding block 5 can be changed adjustable. This setting can also be done during operation. In one possible operating mode, the adjustment between two consecutive strokes can be made gradually.
• the adjusting member 17 includes an eccentric ring 18 which is disposed between the bore 6 in the sliding block 5 and the eccentric 4 of the drive shaft 1.
• the eccentric ring 18 can be rotated via an actuator 19 in its seat, so that the eccentric 4 receiving bore changes its position relative to the sliding block 5.
• Fig. 2 shows a clamping 17a of the adjustment member 17.
• the clamp 17a can be opened hydraulically.
• the closing of the clamp 17a can be hydraulic or mechanically (self-locking) or combined hydraulically and mechanically.
• Fig. 5 shows a second embodiment of a press according to the invention.
• a plunger and / or tool of the press is not moved directly and linearly through the gate 7.
• a force deflection is provided between the pressure piece and a plunger of the press.
• the force deflection takes place by means of a wedge 20, which is displaceable relative to a frame-fixed support surface 21 inclined to the direction of the pressing stroke.
• the wedge 20 is presently firmly connected to the gate 7.
• a plunger 22 of the press is slidably on a side opposite to the support surface 21 of the wedge 20 at.
• the pendulum axis P is displaced parallel to the support surface 21 in the course of the movement transmission. Accordingly, the pressing stroke HP is considered to be in the direction of this offset in the context of the invention. Accordingly, a movement HS of the plunger 22 of the press in the present case is deflected by about 120 ° to the pressing stroke HP of the slide 7.
• a particularly uniform force distribution across the width of the plunger can be achieved.
• the sliding block is formed according to a second variant.
• the pressure side Sliding surface 5a convexly formed on the sliding block 5, in contrast to the concave shape in the examples described above.
• the karmony sliding surface 5b is also on the sliding block 5 inversely with respect to the preceding examples, that is concave shaped.
• the corresponding sliding surfaces 7a, 8a on the slide are accordingly also inversely curved.
• the sliding surfaces 5a, 5b, 7a, 8a are each formed as sections of a cylinder jacket surface, as in the first variant according to FIG. 4, wherein the cylinder axes extend parallel to the shaft axis W.
• the sliding surfaces 5a, 5b, 7a, 8a in turn extend concentrically about a pendulum axis P of the sliding block 5 parallel to the shaft axis W.
• the pendulum axis P in the second variant is on the tension side with respect to the sliding block 5.
• For the sliding block 5 results in rotation of the drive shaft 1 again a positively driven pendulum motion to the Pendulum axle P.
• the second variant also corresponds to an analog thrust crank mechanism with the characteristic quantities L (distance between pendulum axis P and shaft axis W) and R (distance between eccentric axis E and shaft axis W).
• the dead center of the power stroke corresponds to a cover layer of an analogue crank mechanism. This means that the distances R and L in the lowest point of the tool are collinear and one above the other.
• an ejection mechanism 23 is integrated into the press, which is actuated by means of the movement of the sliding block.
• the ejection mechanism comprises an ejector 24 which is linearly displaceable in a guide of the plunger 22 and can press against a workpiece (not shown) at the lower end of the plunger.
• the ejector 24 is moved by a pressing operation by means of a mechanical positive guide against the workpiece and pushes it out of a tool (not shown). In this way, a reliable workpiece change is made possible in a simple manner.
• the operation of the ejector 24 by means of a ramp 27 on the sliding block 5.
• the ramp 27 is located on a presently trained as a ball head 28 of the ejector 24 at.
• the sliding block performs its pendulum motion about the pendulum axis P, wherein it slides along the pressure-side sliding surfaces 5a, 8a.
• the ejector 24 is initially in a reset by means of a spring 29 position in which he does not press on the workpiece.
• the ramp 27 After passing through the power stroke or the pressing process, the ramp 27 begins to push the ejector 24 via the ball 28.
• Fig. 7 the starting time of this ejection operation is approximately shown, with the sliding block 5 in the central position and the plunger 22 are in a bottom dead center.
• the sliding block 5 moves in the illustration of FIG. 7 further to the left and the ramp 27 moves the ejector 24 relative to the plunger 22 and to the gate 7 against the workpiece.
• the ejector 24 performs a movement about a stroke HA against the force of the spring 29th
• the ejection mechanism is illustrated with reference to the first variant of the sliding block 5 with the pressure-side concave sliding surface 5a.
• the ejector mechanism can also be combined with the second variant of the sliding block 5 with the pressure-side convex sliding surface 5a. This has the advantage that the linear path of the sliding block 5 along the sliding surface 5a otherwise the same dimensioning of the press is greater, which allows a less steep design of the ramp 27.
• the stroke HA of the mechanical ejector 23, 24 can be increased. This means that the large force required for ejection is applied by the small-stroke mechanical ejector HA.
• the hydraulic piston increases the stroke HA by the stroke HH.
• the hydraulic piston 25 is operated via a valve with hydraulic control 34.
• the transmission 30 is formed as a reversing lever, which is mounted in a pivot bearing or pivot bearing 31 on the link 7.
• the sliding block 5 is connected in a pivot bearing 32 with the reversing lever, wherein the pivot point of the pivot bearing 32 is aligned with the sliding surface 5a.
• the pivot bearing 32 may be formed as a cam roller. The pivoting movement of the reversing lever is then positively controlled via the cam roller 32 by the arranged on the sliding block 5 cassette guide 33rd
• a ramp 27 is formed on the reversing lever 30, which engages the ejector 24 as in the previous example.
• flywheel motor structural unit of flywheel 1 1 and engine 10
• Swivel bearing Swivel lever - gate (swivel bearing)
• Swivel bearing Swivel lever - sliding block (cam roller)

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Press Drives And Press Lines (AREA)
• Control Of Presses (AREA)
• Forging (AREA)
• Presses And Accessory Devices Thereof (AREA)

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• 2016
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