Spring-damper element for the mounting of a punching press

Abstract

The invention relates to a spring-damper element (2) for mounting a punching press (1), with a hydraulic damper unit (3) with a first fluid chamber (4) and a second fluid chamber (5), wherein, in the intended operation, a hydraulic fluid is displaced from the first fluid chamber (4) via a throttle point (6) into the second fluid chamber (5) when the spring-damper element (2) is compressed. The damper unit further comprises an overload valve (7) arranged between the first fluid chamber (4) and the second fluid chamber (5), which overload valve opens when a specific fluid pressure is reached in the first fluid chamber (4) or when a specific pressure difference is reached between the first fluid chamber (4) and the second fluid chamber (5) and releases a bypass (8) via which hydraulic fluid then flows from the first fluid chamber (4) into the second fluid chamber (5) bypassing the throttle point (6). Thereby, the spring-damper element (2) is designed in such a way that the fluid pressure or the pressure difference, respectively, at which the overload valve (7) opens can be adjusted when the spring-damper element (2) is installed as intended. With such spring-damper elements according to the invention, it becomes possible to create a mounting arrangement for a punching press, the damping characteristics of which can be adjusted without significant effort, such that a variable operation of the press in wide ranges becomes possible while keeping the ground loading to a minimum in each case.

Claims

1. A spring-damper element for the mounting of a punching press, with a hydraulic damper unit with a first fluid chamber and a second fluid chamber, wherein, in the intended operation, a hydraulic fluid is displaced from the first fluid chamber via a throttle point of selected cross-section into the second fluid chamber during compression of the spring-damper element, and with an overload valve arranged between the first fluid chamber and the second fluid chamber, which, on reaching a specific fluid pressure in the first fluid chamber or on reaching a specific pressure difference between the first fluid chamber and the second fluid chamber, is opened by the specific fluid pressure or pressure difference and releases a bypass, via which hydraulic fluid then flows from the first fluid chamber into the second fluid chamber, bypassing the throttle point, wherein the overload valve is adjustable so that the valve is closed and fluid flow through the valve is blocked until the fluid pressure or the pressure difference, respectively, to which the overload valve is adjusted is reached and the valve opens.

2. The spring-damper element according to claim 1, wherein the throttling point of the hydraulic damper unit is a check valve that during rebound of the spring-damper element, allows hydraulic fluid to flow back from the second fluid chamber into the first fluid chamber via a flow cross-section which is wider than the selected cross-section of the throttle point.

3. The spring-damper element according to claim 1, wherein the fluid pressure or the pressure difference, respectively, at which the overload valve opens is adjustable steplessly or in steps.

4. The spring-damper element according to claim 1, wherein the fluid pressure or the pressure difference, respectively, at which the overload valve opens is manually adjustable and/or automatically adjustable via a control system.

5. The spring-damper element according to claim 1, wherein the fluid pressure or the pressure difference, respectively, at which the overload valve opens is adjustable during the intended operation.

6. The spring-damper element according to claim 1, wherein the fluid pressure or the pressure difference, respectively, at which the overload valve opens is adjustable to substantially zero or the overload valve is brought into an open state.

7. The spring-damper element according to claim 1, wherein the hydraulic damper unit comprises a switchable bypass valve arranged between the first fluid chamber and the second fluid chamber, which in the open state releases a bypass, via which hydraulic fluid flows from the first fluid chamber into the second fluid chamber during compression of the spring-damper element, bypassing the throttle point, and via which hydraulic fluid flows from the second fluid chamber into the first fluid chamber during rebound of the spring-damper element.

8. The spring-damper element according to claim 1, wherein the spring-damper element comprises a pneumatic cylinder for adjusting the fluid pressure or the pressure difference, respectively, at which the overload valve opens, which pneumatic cylinder is subjected to a specific air pressure during the intended operation.

9. The spring-damper element according to claim 1, wherein the spring-damper element comprises a threaded spindle which acts on one or more valve springs for adjusting the fluid pressure or the pressure difference, respectively, at which the overload valve opens.

10. A method for operating a punching press which is mounted on spring-damper elements according to claim 1, including the step of operating the press with different settings of the fluid pressure or the pressure difference, respectively, at which the overload valves of the spring-damper elements open, during different intended operating conditions.

11. The method for operating a punching press which is mounted on spring-damper elements according to claim 10, including the step of setting the fluid pressure or the pressure difference, respectively, at which the overload valves of the spring-damper elements open, during the intended operation of the punching press to achieve a specific amplitude with which the punching press oscillates in the spring-damper elements.

12. The method according to claim 11, including the step of setting of the fluid pressure or the pressure difference, respectively, at which the overload valves of the spring-damper elements open, to achieve a maximum permissible amplitude with which the punching press oscillates in the spring-damper elements.

13. The method according to claim 11 including the steps of measuring the amplitude by means of one or more distance measuring sensors, and adjusting the fluid pressure or the pressure difference, respectively, at which the overload valves of the spring-damper elements open to cause the punching press to oscillate with a desired amplitude in the spring-damper elements.

14. The method according to claim 13, wherein the step of measuring the amplitude is performed separately for each spring-damper element, and the step of adjusting the fluid pressure or the pressure difference, respectively, at which the overload valve opens is controlled separately for each spring-damper element.

15. The method according to claim 11, wherein the step of setting the fluid pressure or the pressure difference, respectively, at which the overload valves of the spring-damper elements open, is effected by means of pneumatic cylinders.

16. The method according to claim 11, wherein the step of setting the fluid pressure or the pressure difference, respectively, at which the overload valves of the spring-damper elements open, is effected by means of threaded spindles which act on one or more valve springs.

17. The spring-damper element according to claim 3, wherein the fluid pressure or the pressure difference, respectively, at which the overload valve opens is manually adjustable and/or automatically adjustable via a control system.

18. The spring-damper element according to claim 1, wherein the overload valve is also a one-way valve blocking flow from the second fluid chamber to the first fluid chamber regardless of pressures.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Further embodiments, advantages and applications of the invention result from the dependent claims and from the now following description on the basis of the figures. Thereby show:

(2) FIG. 1 a punching press which is mounted on spring-damper elements according to the invention;

(3) FIG. 2 a vertical section through one of the spring-damper elements from FIG. 1;

(4) FIG. 3 a vertical section through a first variant of the spring-damper element from FIG. 2; and

(5) FIG. 4 a vertical section through a second variant of the spring-damper element from FIG. 2.

DETAILED DESCRIPTION

(6) FIG. 1 shows a punching press 1 which is mounted on four identical spring-damper elements 2 according to the invention on a factory floor 21.

(7) As can be seen in synopsis with FIG. 2 which shows a vertical section through one of the spring-damper elements 2, the spring-damper element 2 comprises a central hydraulic damper unit 3 which is surrounded by six helical spring packages 15 arranged with uniform pitch on a concentric circle around it, over which a support plate 16 which supports a support column 17 of the punching press 1, is supported on a support body 18, which comprises the hydraulic damper unit 3 and is supported on the floor 21 over a floorplate 19 and a damping mat 20 arranged underneath it. Each of the helical spring packages 15 comprises a smaller coil spring 15a and a larger coil spring 15b, whereby the smaller coil spring 15a is arranged concentrically within the larger coil spring 15b.

(8) The hydraulic damper unit 3 comprises a first fluid chamber 4 and a second fluid chamber 5 which are filled with a hydraulic fluid and are separated from each other by a damper piston 23 which is connected to the support plate 16 via a ball pin 24.

(9) In the damper piston 23, a connection channel 22 is arranged whichextends between the first fluid chamber 4 and the second fluid chamber 5 and in which a throttle point 6 is arranged. The throttle point 6 is formed by a type of check valve, the valve closing body of which is formed by a plate 25 with a throttle bore. When pressure is applied to this check valve on its side facing the first fluid chamber 4, the plate 25 is pressed against a valve seat such that the first fluid chamber 4 and the second fluid chamber 5 are only connected to each other via the throttle bore in the plate 25. When this check valve is pressurized on its side facing the second fluid chamber 5, the plate 25 is pushed away from the valve seat and releases a flow cross-section which is significantly larger than its throttle bore, via which the first fluid chamber 4 and the second fluid chamber 5 are then connected to each other.

(10) Accordingly, during compression of the spring-damper element 2, which results in a displacement of the damper piston 23 into the first fluid chamber 4 and subsequently in a pressure increase in the first fluid chamber 4, hydraulic fluid is displaced from the first fluid chamber 4 into the second fluid chamber 5 only via the throttle bore in the plate 25, with the effect that a damping effect is achieved during compression.

(11) During rebound, on the other hand, a considerably larger flow cross-section is available for the return flow of hydraulic fluid from the second fluid chamber 5 into the first fluid chamber 4, and this results in a significantly lower damping effect or no damping effect at all.

(12) As can be seen further on, the hydraulic damper unit 3 further comprises an easily accessible overload valve 7 arranged on the outside of the spring-damper element 2, which is associated with a bypass-line 8 between the first fluid chamber 4 and the second fluid chamber 5 and which opens when a specific fluid pressure is reached in the first fluid chamber 4 or when a specific pressure difference is reached between the first fluid chamber 4 and the second fluid chamber 5, such that hydraulic fluid then flows from the first fluid chamber 4 via the bypass line 8 into the second fluid chamber 5, bypassing the throttle point 6. Thereby, a further increase in pressure in the first fluid chamber 4 is prevented.

(13) This overload valve 7 essentially consists of a valve plate 26 which is pressed against a valve seat by a spring 13. The spring preload can be adjusted with a threaded spindle 12 or it can be revoked completely. At the top of the threaded spindle 12, a marking edge 27 is arranged directly opposite a scale 28, by means of which the set spring preload can be metered.

(14) FIG. 3 shows a vertical section through a first variant of the spring-damper element, which differs from the spring-damper element shown in FIG. 2 only in that the valve plate 26 of the overload valve 7 is not loaded by a spring pretensioned by means of a threaded spindle, but by means of a pneumatic cylinder 11 which is pressurized with a specific air pressure in accordance with the desired opening pressure. This spring-damper element also has a distance measuring sensor 14, by means of which the oscillating movement of the punching press is detected by a machine controller (not shown) and the compressed air supply to the pneumatic cylinder 11 is automatically regulated in such a way that the punching press 1 oscillates with a desired amplitude in the spring-damper elements 2.

(15) FIG. 4 shows a vertical section through a first variant of the spring-damper element, which differs from the spring-damper element shown in FIG. 2 only in that the hydraulic damper unit 3 additionally comprises a switchable bypass valve 9 arranged between the first fluid chamber 4 and the second fluid chamber 5, which bypass valve 9 in the open state releases a bypass 10, via which hydraulic fluid flows from the first fluid chamber 4 into the second fluid chamber 5 when the spring-damper element 2 is compressed bypassing the throttle point 6 and the overload valve 7, and hydraulic fluid flows back from the second fluid chamber 5 into the first fluid chamber 4 when the spring-damper element 2 is rebound, in such a way that practically no damping effect is present in both directions.

(16) While in the present application preferred embodiments of the invention are described, it must be clearly pointed out that the invention is not limited to these and that it can also be realized in another way within the scope of the now following patent claims.