Hydraulic drive with rapid stroke and load stroke

Abstract

A hydraulic drive including a first differential cylinder that includes a first and a second pressure chamber and a first piston that separates the first from the second pressure chamber and having two pumps delivering in opposite direction. The hydraulic drive further includes a second differential cylinder that includes a first and a second pressure chamber and a second piston that separates the first pressure chamber from the second pressure chamber, and a directional control valve that has a first and a second switching position. The pumps in the first switching position are respectively hydraulically connected via pressure chambers of the first differential cylinder that are different from each other and whereby the pumps in the second switching position are respectively connected via pressure chambers of the second differential cylinder that are different from each other.

Claims

1. A hydraulic drive for a hydraulic press, said hydraulic drive comprising: a first pump and a second pump delivering in an opposite direction; a first differential cylinder, including: a first pressure chamber and a second pressure chamber; and a first piston that separates said first pressure chamber from said second pressure chamber; a second differential cylinder, including: a first pressure chamber and a second pressure chamber; and a second piston that separates the first pressure chamber from the second pressure chamber of the second differential cylinder; and a directional control valve that has a first switching position and a second switching position, wherein said first pump and said second pump in the first switching position are respectively hydraulically connected via said first pressure chamber and said second pressure chamber of the first differential cylinder, and wherein said first pump and said second pump in the second switching position are respectively connected via said first pressure chamber and said second pressure chamber of the second differential cylinder.

2. The hydraulic drive according to claim 1, wherein said first pressure chamber and said second pressure chamber of the first differential cylinder each have a respective hydraulic effective surface, and said hydraulic effective surface of said first pressure chamber of the first differential cylinder is larger than said hydraulic effective surface of said second pressure chamber of the first differential cylinder, wherein said first pressure chamber and said second pressure chamber of the second differential cylinder each have a respective hydraulic effective surface, and said hydraulic effective surface of said first pressure chamber of the second differential cylinder is larger than said hydraulic effective surface of said second pressure chamber of the second differential cylinder.

3. The hydraulic drive according to claim 2, wherein each respective hydraulic effective surface of the second differential cylinder is larger than each respective hydraulic effective surface of the first differential cylinder.

4. The hydraulic drive according to claim 2, wherein a surface ratio of said hydraulic effective surface of said first pressure chamber of the first differential cylinder and said hydraulic effective surface of said second pressure chamber of the first differential cylinder relative to said hydraulic effective surface of said first pressure chamber of the second differential cylinder and said hydraulic effective surface of said second pressure chamber of the second differential cylinder is substantially identical.

5. The hydraulic drive according to claim 2, wherein said first pump and said second pump each have a delivery volume that is adapted to a surface ratio of each respective hydraulic effective surface of the first differential cylinder and the second differential cylinder.

6. The hydraulic drive according to claim 1, wherein said first piston and said second piston are mechanically movably coupled.

7. The hydraulic drive according to claim 1, further including a tank that can be connected hydraulically with at least one of said first pump and said second pump, said first pressure chamber and said second pressure chamber of the first differential cylinder, and said first pressure chamber and said second pressure chamber of the second differential cylinder.

8. The hydraulic drive according to claim 1, wherein said directional control valve is an 8/2 directional control valve.

9. The hydraulic drive according to claim 1, wherein said directional control valve can be at least one of hydraulically and electronically switched, depending on a pressure limit in at least one of said first pressure chamber in the first differential cylinder and said first pressure chamber in the second differential cylinder.

10. The hydraulic drive according to claim 1, wherein said directional control valve can be mechanically switched, depending on a position of at least one of said first piston and said second piston.

11. The hydraulic drive according to claim 1, further including at least one check-valve arranged such that cavitation can be avoided in said first pressure chamber and said second pressure chamber of the first differential cylinder and in said first pressure chamber and said second pressure chamber of the second differential cylinder.

12. A method for operating a hydraulic drive having hydraulic fluid therein, said hydraulic drive including a first pump and a second pump delivering in an opposite direction, a first differential cylinder including a first pressure chamber and a second pressure chamber and a first piston that separates said first pressure chamber from said second pressure chamber of the first differential cylinder, a second differential cylinder including a first pressure chamber and a second pressure chamber and a second piston that separates the first pressure chamber from the second pressure chamber of the second differential cylinder, and a directional control valve that has a first switching position and a second switching position, wherein said first piston and said second piston are movably coupled, the method comprising the steps of: actuating the first switching position so that said first pump moves hydraulic fluid into said first pressure chamber of the first differential cylinder and said second pump moves hydraulic fluid out of said second pressure chamber of the first differential cylinder; and actuating the second switching position so that said first pump moves hydraulic fluid into said first pressure chamber of the second differential cylinder and said second pump moves hydraulic fluid out of said second pressure chamber of the second differential cylinder.

13. The method according to claim 12, further including the step of switching said directional control valve from the first switching position into the second switching position when a pressure limit is exceeded in said first pressure chamber of the first differential cylinder.

14. The method according to claim 12, wherein the directional control valve is moved through a spring actuation from the second switching position into the first switching position if falling below a reset pressure in said first pressure chamber of the second differential cylinder.

15. The method according to claim 12, wherein after a reversal of a delivery direction of said first pump and said second pump in the first switching position, said first pump moves hydraulic fluid out of said first pressure chamber of the first differential cylinder and said second pump moves hydraulic fluid into said second pressure chamber of the first differential cylinder.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The above-mentioned and other features and advantages of this invention, and the manner of attaining them, will become more apparent and the invention will be better understood by reference to the following description of an embodiment of the invention taken in conjunction with the accompanying drawing, wherein:

(2) FIG. 1 illustrates a hydraulic circuit diagram of an embodiment of an inventive hydraulic drive.

(3) Corresponding reference characters indicate corresponding parts throughout the single view. The exemplification set out herein illustrates one embodiment of the invention and such exemplification is not to be construed as limiting the scope of the invention in any manner.

DETAILED DESCRIPTION OF THE INVENTION

(4) Referring now to the drawing, hydraulic drive 10 includes a cylinder arrangement that, as a whole, is identified with reference number 12. Cylinder arrangement 12 includes two hydraulic differential cylinders 14, 16 that are separated from each other. First differential cylinder 14 includes a piston 18 and a piston rod 20 that is connected with piston 18. Piston 18 separates differential cylinder 14 into a first pressure chamber 22 and in a second pressure chamber 24. On the side of first pressure chamber 22 the first differential cylinder 14 has a hydraulic effective surface 26, whereby first differential cylinder 14 has a hydraulic effective surface 28 on the side of second pressure chamber 24. Hydraulic effective surface 26 has a surface ratio of approximately 2:1 relative to hydraulic effective surface 28. However another surface ratio is also conceivable.

(5) Second differential cylinder 16 also includes a piston 30 that separates the second differential cylinder 16 into a first pressure chamber 32 and a second pressure chamber 34. On the side of first pressure chamber 32, second differential cylinder 16 has a hydraulic effective surface 36, whereby second differential cylinder 16 has a hydraulic effective surface 38 on the side of second pressure chamber 34. Hydraulic effective surface 36 has a surface ratio of for example 2:1 relative to hydraulic effective surface 38. However, another surface ratio is also conceivable. This surface ratio is approximately consistent with the surface ratio of effective surface 26 relative to effective surface 28.

(6) Piston 30 is connected with piston rod 20 of first differential cylinder 14. Consequently the two pistons 20, 30 of the two differential cylinders are mechanically coupled, movably by piston rod 20. Piston 30 is moreover connected with an additional piston rod 40. A tool, work piece or functional part of a machine that is not illustrated in the drawing, can be arranged on piston rod 40.

(7) The hydraulic drive furthermore includes two hydraulic pumps 42, 44 that are illustrated in the drawing only as a differential pump. The differential pump provides different delivery volumes at their respective outlets. The two pumps 42, 44 are driven by a hydraulic motor that is not illustrated and deliver in opposite direction. First pump 42 has a greater delivery volume than second pump 44. The delivery volume of first pump 42 is proportional to the delivery volume of second pump 44 at a ratio that is approximately consistent to the surface ratio of effective surfaces 26, 36 of first pressure chambers 22, 32 relative to effective surfaces 28, 38 of second pressure chambers 24, 34. The delivery volumes of pumps 42, 44 are thus adapted to the surface ratios of effective surfaces 26, 28, 36, 38.

(8) First pressure chamber 22 of first differential cylinder 14 can be connected with first pump 42 or with a pressure tank 50 via a first hydraulic line 46 by a directional control valve 48 that has a first and a second switching position. Second pressure chamber 24 of first differential cylinder 14 can be connected with second pump 44 or with pressure tank 50 via a second hydraulic line 52.

(9) First pressure chamber 32 of second differential cylinder 16 can be connected with pressure tank 50 or with first pump 42 via a third hydraulic line 54. Moreover, first pressure chamber 32 of second differential cylinder 16 can be connected with pressure tank 50 via a fourth hydraulic line 56. Second pressure chamber 34 of second differential cylinder 16 can be connected with pressure tank 50 or with second pump 44 via a fifth hydraulic line 58.

(10) Directional control valve 48 can be designed as an 8/2 directional control valve. This means that the directional control valve 48 includes eight controlled connections and two switching positions. In the current example, directional control valve 48 is realized through two 4/2 directional control valves 60, 62 that are coupled with each other. Directional control valve 48, or respectively directional control valves 60, 62 can be switched from the first switching position that is illustrated in the drawing against a reset force of spring 64, into a second switching position. The switching elements (valve pistons) of directional control valves 60, 62 are mechanically coupled with each other. As shown in FIG. 1, directional control valve 48 is hydraulically controlled, in that the hydraulic pressure that is present in hydraulic line 68 is fed back via a control line 66. Depending upon the switching position of directional control valve 48, hydraulic line 68 is connected either with hydraulic line 46 or with hydraulic line 54.

(11) In order to avoid vacuums or cavitation, hydraulic drive 10 moreover comprises three check valves 70, 72 and 74.

(12) Hydraulic drive 10 can operate as follows: when the non-illustrated servo motor drives pumps 42, 44 and the directional control valve 48 is in the first switching position shown in FIG. 1 then pump 42 moves hydraulic fluid into first pressure chamber 22 of first differential cylinder 14, whereby second pump 44 moves hydraulic fluid out of second pressure chamber 24 of first differential cylinder 14. First pressure chamber 32 of second differential cylinder 16 receives hydraulic fluid via check valve 70 or respectively via hydraulic line 56, whereas hydraulic fluid can flow from second pressure chamber 34 of second differential cylinder 16 into pressure tank 50. Consequently, pumps 42, 44 act in the first switching position only upon pressure chambers 22, 24 of first hydraulic differential cylinder 14. Due to the smaller hydraulic effective surfaces 26, 28 and the movable coupling by piston rod 20, the two pistons 18, 30 of both differential cylinders 14, 16 are moved downward in a rapid stroke, that is in the direction of arrow 76.

(13) If piston rod 40 or respectively a press tool that is arranged on the piston rod encounters an obstacle, the pressure in first pressure chamber 22 of first differential cylinder 14, or respectively in hydraulic lines 46, 68 increases. If the pressure that is fed back via control line 66 increases to above a pressure limit that was preset via spring 64 of directional control valve 48, valve 48 is moved against the force of spring 64 into its second switching position toward the right, that is in the direction of arrow 78.

(14) At a consistent delivery direction of pumps 42, 44 first pump 42 moves hydraulic fluid into first pressure chamber 32 of second differential cylinder 16, whereby second pump 44 moves hydraulic fluid out of second pressure chamber 34 of first differential cylinder 16. First pressure chamber 22 of first differential cylinder 14 received hydraulic fluid via hydraulic line 46 from pressure tank 50, whereas hydraulic fluid can flow from second pressure chamber 24 of first differential cylinder 14 via hydraulic line 52 into pressure tank 50. Consequently, in the second switching position pumps 42, 44 only act upon pressure chambers 32, 34 of second hydraulic differential cylinder 16. Because of the larger hydraulic effective surfaces 36, 38 and the movable coupling by piston rod 20, both pistons 18, 30 of the two differential cylinders 14, 16 are moved downward in a load stroke, that is in the direction of arrow 76. During the load stroke a slower movement occurs at greater force. A power transmission can be achieved through an appropriate selection of the surface ratios. If, for example effective surfaces 36, 38 of second differential cylinder 16 are ten times larger than effective surfaces 26, 28 of first differential cylinder 14, a power transmission of 10:1 can be realized.

(15) After completion of a load stroke the pressure in first pressure chamber 32 of second differential cylinder 16, or respectively in hydraulic lines 54, 68 drops. If the pressure drops below a predefined reset pressure of directional control valve 48 then the valve is moved again by the spring force of spring 64 into its first switching position that is illustrated in FIG. 1.

(16) Pumps 42, 44 are again hydraulically connected in the first switching position with pressure chambers 26, 28 of the first differential cylinder. If the delivery direction of pumps 42, 44 is reversedfor example by reversing the rotational direction of the motor that is not illustratedthen first pump 42 moves hydraulic fluid out of first pressure chamber 22 of first differential cylinder 14, whereby second pump 44 moves hydraulic fluid into second pressure chamber 24 of first differential cylinder 14. Second differential cylinder 16 does now not participate in the fluid exchange with pumps 42, 44. Due to the movable coupling by piston rod 20, pistons 18, 30 of the two differential cylinders can again be moved upward in a rapid return stroke, in the opposite direction to that indicated by arrow 76.

(17) Thus, a displacement control system can be produced with the inventive hydraulic drive 10, whereby the drive can be operated in a rapid stroke and a load stroke, whereby efficiency losses can be avoided and whereby the drive can be produced cost effectively, since pumps 42, 44 can be sized comparatively small.

(18) While this invention has been described with respect to at least one embodiment, the present invention can be further modified within the spirit and scope of this disclosure. This application is therefore intended to cover any variations, uses, or adaptations of the invention using its general principles. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this invention pertains and which fall within the limits of the appended claims.