Hydraulic drawing cushion of a drawing press and method of operating the hydraulic cushion

Abstract

A hydraulic drawing cushion (17) for a drawing press (10) includes at least one hydraulic cylinder (21) comprising a piston rod (27) that causes a total force (G) to act on the metal sheet holding ring (20). The hydraulic cylinder (21) comprises a hydraulic work circuit (37) to generate a hydraulic work force (A) in a work direction (Z) to act on a ring part (28) to which a force can be applied on both sides. Independently, a spring force (F) acts on the piston (26). The spring force (F) is neither controlled nor adjusted, but is preset. Preferably, the spring force (F) is exclusively a function of the position or location of the piston (26) relative to the cylinder housing (25). The total force (G) acting on the piston (26) results from the addition of the vectors of the work force (A) and the spring force (F).

Claims

1. A drawing press (10), comprising: a floating plate (18) configured to move in a work direction, a drawing cushion (17) comprising: a hydraulic cylinder (21) comprising a cylinder housing (25) and a piston (26) with a piston rod (27), wherein the piston rod is configured to drive the floating plate (18), a plurality of hydraulic work chambers (29, 30) including a first work chamber, a second work chamber, and a third work chamber provided in the cylinder housing (25), a spring device (45) configured as a fluidic spring device (45a) and configured to apply an essentially constant spring force (F) to the piston (26) during operation of the drawing press (10), a first piston area (31) is adjacent to the first work chamber (29), and a second piston area (32) is adjacent to the second work chamber, and wherein the first work chamber (29) and the second work chamber (30) are connected to a hydraulic pump (40) of a hydraulic work circuit (37), wherein the fluidic spring device (45a) comprises a pressure storage (50) that is connected to the third work chamber (47) of the cylinder (21) via a pressure line (49), wherein the third work chamber (47) is adjacent to a third piston area (48) of the piston (26).

2. A drawing press (10) as in claim 1, wherein the spring force (F) is not a function of a hydraulic pressure or a volume flow of the first work chamber's (29) and/or in the second work chamber's (30) hydraulic medium.

3. A drawing press (10) as in claim 1, wherein the hydraulic pump (40) of the hydraulic work circuit (37) is configured to generate a hydraulic pressure in the first work chamber (29) or in the second work chamber (30), said hydraulic pressure generating a work force (A) on the respective first piston area (31) or the second piston area (32).

4. A drawing press (10) as in claim 3, wherein the work force (A) generated on the first piston area (31) acts counter the spring force (F), and that the work force (A) generated on the second piston area (32) acts in the spring force (F) direction.

5. A drawing press (10) as in claim 1, wherein the spring force (F) is only a function of the piston's (26) position (Z1, Z2).

6. A drawing press (10) as in claim 1, wherein the spring device (45) has a spring constant (D) that is high relative to a maximum piston stroke (Z2-Z1) such that a force difference (FD) between a minimum value (Fmin) and a maximum value (Fmax) of the spring force (F) is at most 10% to 15% of the maximum value (Fmax) of the spring force (F).

7. A drawing press (10) as in claim 1, wherein the spring device (45) is designed without active electrical and electromechanical components.

8. A drawing press (10) as in claim 1, wherein a maximum hydraulic volume of hydraulic medium in the pressure storage (50) is greater than the third work chamber's (47) maximum volume.

9. A drawing press (10) as in claim 1, wherein the hydraulic work circuit's (37) hydraulic medium is completely separate from the fluidic spring device's (45a) hydraulic medium.

10. A drawing press (10) as in claim 1, wherein the hydraulic pump (40) of the hydraulic work circuit (37) can be driven by an electric motor (41) in both directions of rotation.

11. The drawing press of claim 1 wherein the spring device (45) is configured to apply the first spring force (F) to the piston (26) in support of a drawing operation of the drawing press.

12. Method of operating a drawing press (10) comprising a floating plate (18) configured to move in a work direction and a hydraulic drawing cushion (17) comprising a hydraulic cylinder (21) comprising a cylinder housing (25) and a piston (26) with a piston rod (27), wherein the piston rod (27) is configured to drive the floating plate (18), a plurality of hydraulic work chambers (29, 30) including a first work chamber, a second work chamber, and a third work chamber are provided in the cylinder housing (25), and a first piston area (31) is adjacent to the first work chamber (29) and a second piston area (32) is adjacent to the second work chamber, the method comprising: controlling and/or adjusting one or more of the piston's (26) position, movement, and/or holding force or the floating plate (18) by control or adjustment of hydraulic pressure and/or volume flow of the first or second work chamber's (29, 30) hydraulic medium, and applying a spring force (F) to the piston (26) by a spring device (45) configured as a fluidic spring device (45a) without directly controlling or adjusting the spring force (F) during operation of the drawings press (10), wherein the fluidic spring device (45a) comprises a pressure storage (50) that is connected to the third work chamber (47) of the cylinder (21) via a pressure line (49), wherein the third work chamber (47) is adjacent to a third piston area (48) of the piston (26).

13. The method of claim 12 wherein the applying the spring force (F) comprises applying the spring force to bias the piston (26) in support of a drawing operation of the drawing press.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 a schematic view resembling a block circuit diagram of an exemplary embodiment of a drawing press;

(2) FIG. 2 a schematic representation resembling a block circuit diagram of an exemplary embodiment of a hydraulic cylinder with a spring device;

(3) FIG. 3 a schematic representation resembling a block circuit diagram of a modified exemplary embodiment of a hydraulic cylinder with a fluidic spring device;

(4) FIG. 4 a schematic representation of the spring force, the work force and the resultant total force acting on the piston of the cylinder as a function of the rotational speed of the hydraulic pump; and

(5) FIG. 5 a schematic representation of the spring force as a function of the position of the piston.

DETAILED DESCRIPTION

(6) FIG. 1 is a schematic illustration of a drawing press 10 with a press frame 11. A ram 12 is arranged on the press frame 11 so as to be movable in a work direction Z, for example in vertical direction. A press drive 13 is disposed for moving the ram 12. Arranged on the ram 12 is a first tool 14. At a distance from the first tool, a second tool 15 is supported by the press frame 11, for example by means of a press table 16.

(7) Furthermore, the drawing press 10 comprises a hydraulic drawing cushion 17. The hydraulic drawing cushion 17 is located on the side of the second tool 15 that faces away from the first tool 14, i.e., in accordance with the example, below the press table 16. A floating plate 18 is associated with the hydraulic drawing cushion 17. Pressure rods 19 are provided on the floating plate 18, said pressure rods extending from the floating plate 18 to the second tool 15. In accordance with the example, the pressure rods 19 extend through the press table 16 and through the second tool 15 and/or past the second tool 15. On the ends of pressure rods 19 opposite the floating plate 18, there is arranged a metal sheet holding ring 20. The metal sheet holding ring 20 can be moved together with the floating plate 18 in a work direction Z. To accomplish this, the floating plate 18 is movably supported in work direction Z by means of at least one hydraulic cylinder 21 relative to the press frame 11. FIG. 1 shows only one single hydraulic cylinder 21. Depending on how the drawing press 10 is dimensioned, the floating plate 18 may also comprise several, preferably identically configured, hydraulic cylinders 21.

(8) FIGS. 2 and 3 show exemplary embodiments of a hydraulic cylinder 21, as well as components of the drawing cushion 17 connected to the hydraulic cylinder 21. To avoid confusion, these components that are connected to the hydraulic cylinder 21 are not shown in FIG. 1; however, they are also provided in that case.

(9) The hydraulic cylinder 21 has a cylinder housing 25 and a piston 26 supported in the cylinder housing 25 so as to be movable back and forth in work direction Z. The piston 26 has a piston rod 27 to which a ring part 28 is rigidly mounted. The ring part 28 divides an interior space in the cylinder housing 25 into a first work chamber 29 and a second work chamber 30. The two work chambers 29, 30 are fluidically sealed relative to each other by the ring part 28. Adjacent to the first work chamber 29, a first piston area 31 exists on the ring part 28 and, adjacent to the second work chamber 30, a second piston area 32 exists. The first piston area 31 and the second piston area 32 are each configured as annular surfaces and have the same size in the preferred exemplary embodiment. In accordance with the example, the first work chamber 29 and the second work chamber 30 have a cylindrical shape and, in particular, the shape of a circular cylinder.

(10) The piston rod 27 projects at least on one side and, preferably, only on one side, from the cylinder housing 25 and has a free end 33 at that location. The free end 33 of the piston rod 27 is connected to the floating plate 18 in the drawing press 10.

(11) The first two work chambers 29, 30 of the hydraulic cylinder 21 are in fluidic communication with a hydraulic work circuit 37. The hydraulic work circuit 37 comprises a first hydraulic line 38 that is in fluidic communication with the first work chamber 29, as well as a second hydraulic line 39 that is in fluidic communication with the second work chamber 30. The two hydraulic lines 38, 39 are connected to a hydraulic pump 40 and indirectly connected to each other by the interposed hydraulic pump 40. The hydraulic pump 40 can be operated in both directions of rotation. For driving the hydraulic pump 40, a motor is used, i.e., an electric motor 41 in accordance with the example. In the exemplary embodiment, the electric motor 41 is actuated via a control unit 42. The control unit 42 may control and/or adjust the operating parameters of the electric motor 21 such as, for example, the rotational speed n, the direction of rotation, the electric current of the motor or the like. Adjustment parameters for the control unit 42 may also be the volume flow of the hydraulic volume conveyed by the hydraulic pump 40 and/or the hydraulic pressure in one of the two hydraulic lines 38, 39 or in one of the two work chambers 29, 30. All mentioned parameters can be controlled or adjusted individually or, together, in any desired combination. The rotational speed n and/or other operating parameters of the hydraulic pump 40 can also be set for the adjustment of the position and/or the speed and/or the total force G acting on the piston rod 27.

(12) The first piston area 31 and the second piston area 32 may also be dimensioned differently. This results in different-size volume flows of the hydraulic pump 40 into or out of the work chambers 29, 30 when the piston 26 is being moved, so that appropriate compensation means may be provided in the hydraulic work circuit 37. The hydraulic work circuit 37 is half open, as it were.

(13) Considering the preferred exemplary embodiments of the hydraulic drawing cushion 17 illustrated here, no hydraulic components that can be activated or actuated during the drawing operation such as, for example actuatable hydraulic valves, are inserted in the first hydraulic line 38 and the second hydraulic line 39. The hydraulic medium can be conveyed out of the first work chamber 29 and into the second work chamber 30 by means of the hydraulic pump 40. Conversely, the hydraulic medium can be conveyed from the second work chamber 30 into the first work chamber 29. A work force A can be set on the piston 26 by means of the hydraulic pressure set in the first work chamber 29 and the second work chamber 30, respectively. The work force A is oriented in work direction Z. Depending on which of the two work chambers 29, 30 is subjected to pressure, the work force A forces the piston rod 27 out of the cylinder housing 25 into the completely moved-out position, or the work force A forces the piston rod 27 into the cylinder housing 25 into the completely moved-in position. The work force A may also be equal to zero if the hydraulic pump 40 is in idle mode.

(14) When the press is stopped, i.e., when no drawing operation is being performed, a safe mode of the press can be established with appropriate securing means (not illustrated), for example shut-off valves in one or more hydraulic lines, or mechanical locking means. These securing means are not active during a drawing operation.

(15) Furthermore, the hydraulic drawing cushion 17 comprises a spring device 45. The spring device 45 generates a spring force F that acts on the piston 26 and, in accordance with the example, on piston rod 27. The spring force F acts in work direction Z. The spring force F is oriented in such a manner that it displaces the piston rod 27 from the cylinder housing 25 into its completely moved-out position. The work force A that is generated by the hydraulic work circuit 37 can be oriented in the same direction as the spring force F and increase said spring force or the spring force F may be oriented in opposite direction and decrease said spring force. The sum of the spring force F and the prevailing work force A results in a total force G that acts on the piston 26. The quantity of the spring force F is always greater than zero.

(16) The spring device 45 may be a mechanical, fluidic or a combined spring device. In the exemplary embodiment as in FIG. 2, the spring device 45 is only illustrated schematically as an example in the form of a helical spring. The spring device 45 may be arranged in or on the cylinder housing 25. Preferably, the spring device 45 is coupled with the piston rod 27 in such a manner that the spring force F is inserted along the longitudinal axis of the piston rod 27 in order to avoid a tilting of the piston rod 27 relative to the cylinder housing 25. Preferably, the spring device 45 acts on the front side on the piston rod 27. For example, the face 46 of the piston rod 27 that exists on the end opposite the free end 33 may act as a contact surface for the spring device 45. The size of the face 46 of the piston rod 27 can be increased or decreasedif necessaryby an appropriately configured cylindrical end piece on the piston rod 27.

(17) In accordance with the example, the spring device 45 generates an essentially constant spring force F which, in the exemplary embodiments described herein, is only a function of the position of the piston 26 in work direction Z. Other than that, the spring force F cannot be controlled or adjusted, or be influenced by other parameters. Therefore, in an unchanged position of the piston, the spring force F is constant.

(18) The dependency of the spring force F on the position of the piston 26 in work direction Z is schematically illustrated by FIG. 5. The piston 26 can be moved between a first position Z1 in which the piston rod 27 is completely retracted and a second position Z2 in which the piston rod 27 is completely moved out. In doing so, the following relationship applies, based on Hooke's Law:
F=D.Math.Z
wherein F is the change of the spring force F, Z is the change of the position of the piston 26 in work direction Z, and D is the spring constant of the spring device 45.

(19) As is obvious from FIG. 5, the spring force F changes between a maximum value Fmax in the first position Z1 of the piston 26, in which the piston rod 27 is completely moved in, and a minimum value Fmin in the second position Z2 of the piston 26, in which the piston rod 27 is completely moved in. The force difference FD between the maximum value Fmax and the minimum value Fmin of the spring force F should be as low as possible. The force difference FD can be influenced by the embodiment of the spring device 45 and is at most 10% to 15% of the maximum value Fmax of the spring force F in one exemplary embodiment.

(20) In particular, the spring force F is not a function of the work force A that is generated on the piston 26 via the hydraulic work circuit 37 or the hydraulic pump 40. The rotational speed n of the hydraulic pump 40, the volume flow or the hydraulic pressure in the hydraulic work circuit 37 do not influence the spring force F.

(21) Preferably, the spring device 45 comprises no electrically components that can be electrically activated. Consequently, the spring force F cannot be controlled or adjusted during the operation of the hydraulic drawing cushion. However, there may be a provision for setting the spring force F when the drawing press 10 is set up, dependent of the reshaping task of the drawing press 10, and for adapting the maximum possible work force A. This setting then remains unchanged during the entire operation of the drawing press 10. In accordance with the example, the spring force F only changes as a function of the position of the piston 26.

(22) Referring to the exemplary embodiment shown by FIG. 3, the spring device 45 is configured as a fluidic spring device 45a. In doing so, the spring force F is transmitted to the piston 26 by a fluid and, in accordance with the example, by a hydraulic medium. To accomplish this, a third work chamber 47 adjoined by a third piston area 48 is provided in the cylinder housing. Referring to the exemplary embodiment shown here, the third piston area 48 of the piston 26 is the face 46. The third piston area 48 is greater than the first piston area 31 and the second piston area 32 and, in accordance with the example, is at least greater by a factor of 5.

(23) The third work chamber 47 is connected to a pressure storage 50 via a pressure line 49. For example, a membrane storage or the like can be used as the pressure storage. The pressure storage 50 comprises a hydraulic chamber 51. Located inside the hydraulic chamber, there is a specific volume percentage of the hydraulic medium that can be shifted between the third work chamber 47 and the pressure chamber 51 via the pressure line 49. The pressure storage 50 comprises a force generating means 52. The force generating means 52 can generate, for example mechanically and/or fluidically, a force acting on a pressure element 53. The pressure element 53 is supported in the pressure storage 50 in a movable and, in particular, in a shiftable manner in the pressure storage, for example a piston, a membrane or the like.

(24) The pressure element 53 has a pressure area 54 that pushes against the hydraulic medium in the pressure chamber 51. In doing so, the pressure area 54 is larger than the third work area 48 or the face 46 of the piston 26. Preferably, the pressure area 54 is larger by at least the factor of 5 to 10 than the third work area 48. As a result of this, it is achieved, for example, that the change of the spring force F due to a changing position of the piston 26 is sufficiently small and remains in a prespecified region between the minimum value Fmin and the maximum value Fmax of the spring force F.

(25) The volume of the pressure chamber 51 of the pressure storage 50 when the piston rod 27 is completely moved in is greater than the volume of the third work chamber 47 when the piston rod 27 is completely moved out. In other words: The maximum volume of the pressure chamber 51 is greater than the maximum volume of the third work chamber 47. As a result of this, it is ensured that hydraulic medium always remains in the pressure chamber 51.

(26) The spring device 45 may comprise a transmission arrangement so that the generated force is transmitted to the piston 26 and generates a spring force F at that location. Considering the fluidic spring device 45a, it is the pressure area 54, the hydraulic chamber 51, the pressure line 49, the third work chamber 47 and the third piston area 48 that form the transmission arrangement. The latter transmits the force generated by the force generating means 52 to the piston 26.

(27) The main difference between the embodiment as in FIG. 2 and the embodiment as in FIG. 3 of the hydraulic drawing cushion 17 consists in that the spring device 45 as in FIG. 2 generates a spring force F acting directly on the piston 26. In a fluidic spring device 45a as in FIG. 3, the force of the force generating means 52 is transmitted via the hydraulic medium to the piston 26. In doing so, a transmission can be achieved due to the surface ratio between the third work area 48 and the pressure area 54. Furthermore, the maximum distance traveled by the pressure area 54 or the pressure element 53 can be shorter than the maximum piston stroke of the piston 26 between its first position Z1 and its second position Z2. Consequently, the position-dependent change of the spring force F that acts through the fluidic spring device 45a on the piston 26 can be kept low.

(28) The hydraulic medium of the hydraulic work circuit 37 is completely separate from the hydraulic medium of the fluidic spring device 45a. The fluidic spring device 45a can thus form a module without external fluidic and/or electrical connections, which module can also be embodied as an integral part with the cylinder housing 25 or be installed on said cylinder housing.

(29) The total force G is schematically represented as an example by FIG. 4, wherein said total force acts on the piston 26 as a function of the rotational speed n of the hydraulic pump 40. The dashed line indicates the work force A that is attained due to the hydraulic circuit 37 and thus the hydraulic pump 40. In doing so, negative rotational speeds of the hydraulic pump 40 correspond to a conveying direction of the hydraulic pump 40 in the first work chamber 29, whereas positive rotational speeds n illustrate the opposite conveying direction into the second work chamber 30.

(30) FIG. 4 shows the spring force F as a function of the rotational speed n. As described hereinabove, the spring force F may slightly change as a function of the position of the piston 26, however not as a function of the rotational speed n of the hydraulic pump 40, so that the spring force F in FIG. 4 remains constant. The sum of the work force A and the spring force F results in the total force G that acts on the piston 26. In the exemplary embodiment, the spring force F is selected such that the total force G cannot become lower than zero and that thus the direction of the total force G cannot be changed. The consequence of this is that only a total force G acts on the piston 26, said total force displacing the piston rod into the moved-out position. The inward movement of the piston rod occurs during the drawing operation through the force of the ram 12 that acts on the metal sheet holding ring 20 via the first tool 14 while the drawing operation is being performed.

(31) Consequently, by varying the rotational speed n of the hydraulic pump 40, the total force G can varied and adjusted during the drawing operation. In so doing, the total force G may also be controlled or adjusted, for example, as a function of the position or the movement of the ram 12.

(32) If the hydraulic drawing cushion 17 comprises only one hydraulic cylinder 21, the holding force that is applied via the metal sheet holding ring 20 to the metal sheet to be reshaped corresponds to the total force G. If several hydraulic cylinders 21, each comprising a hydraulic work circuit 37 and a spring device 45, are provided, the holding force of the metal sheet holding ring 20 results from the sum of the respective total forces G of the individual hydraulic cylinders 21.

(33) The invention relates to a hydraulic drawing cushion 17 for a drawing press 10. The hydraulic drawing cushion 17 comprises at least one hydraulic cylinder 21 comprising a piston rod 27 that causes a total force G to act on the metal sheet holding ring 20. The hydraulic cylinder 21 comprises a hydraulic work circuit 37 by means of which a hydraulic work force A can be generated in a work direction Z to act on a piston's 26 ring part 28 to which a force can be applied on both sides. Independent of the work force A generated by the hydraulic work circuit 37 to act on the piston 26 of the hydraulic cylinder 21, a spring force (F) acts on the piston (26). The spring force F is generated by a spring device 45. The spring force F is neither controlled nor adjusted, but is preset. Preferably, the spring force F is exclusively a function of the position or location of the piston 26 relative to the cylinder housing 25. The total force G acting on the piston 26 results from the addition of the vectors of the work force A and the spring force F.

LIST OF REFERENCE SIGNS

(34) 10 Drawing press 11 Press frame 12 Ram 13 Press drive 14 First tool 15 Second tool 16 Press table 17 Hydraulic drawing cushion 18 Floating plate 19 Pressure rod 20 Metal sheet holding ring 21 Hydraulic cylinder 25 Cylinder housing 26 Piston 27 Piston rod 28 Ring part* 29 Work chamber 30 Second work chamber 31 First piston area 32 Second piston area 33 Free end of the piston rod 37 Working hydraulic circuit 38 First hydraulic line 39 Second hydraulic line 40 Hydraulic pump 41 Electric motor 45 Spring device 45a Fluidic spring device 46 Face 47 Third work chamber 48 Third piston area 49 Pressure line 50 Pressure accumulator 51 Pressure chamber 52 Force generating means* 53 Pressure element 54 Pressure area A Work force D Spring constant F Spring force G Total force Z Work direction Z1 First position Z2 Second position