Hydraulic drive with rapid stroke and load stroke

Abstract

A hydraulic drive including a differential cylinder that has a first pressure chamber and a second pressure chamber and a differential piston, a first hydraulic pump that includes a pump intake and a pump outlet, a directional control valve having a first switching position and a second switching position, a high pressure tank, and an additional hydraulic cylinder that includes an additional pressure chamber hydraulically connected with the pump intake and with the high pressure tank and an additional piston limiting the additional pressure chamber, the differential piston being movably coupled with the additional piston, wherein in the first switching position of the directional control valve the first pressure chamber is hydraulically connected with the second pressure chamber, and in the second switching position of the directional control valve the second pressure chamber is not hydraulically connected with the first pressure chamber.

Claims

1. A hydraulic drive, comprising: a differential cylinder, including: a first pressure chamber and a second pressure chamber; and a differential piston that separates the first pressure chamber from the second pressure chamber; a first hydraulic pump, including: a pump intake and a pump outlet; a directional control valve having a first switching position and a second switching position; a low pressure tank; a high pressure tank; and an additional hydraulic cylinder, including: an additional pressure chamber hydraulically connected with said pump intake and with said high pressure tank; and an additional piston limiting the additional pressure chamber, said differential piston being movably coupled with said additional piston by a common piston rod such that said differential piston and said additional piston are coaxial, wherein said first pressure chamber is hydraulically connected with said pump outlet, and further wherein in the first switching position of said directional control valve said first pressure chamber is hydraulically connected with said second pressure chamber, and in the second switching position of said directional control valve said second pressure chamber is not hydraulically connected with said first pressure chamber and is instead hydraulically connected with the low pressure tank.

2. The hydraulic drive according to claim 1, wherein said first pressure chamber includes a first hydraulic effective surface, said second pressure chamber includes a second hydraulic effective surface, and said additional pressure chamber includes an additional hydraulic effective surface, whereby a differential surface is consistent with the first hydraulic effective surface and the second hydraulic effective surface of said additional hydraulic effective surface.

3. The hydraulic drive according to claim 1, wherein said directional control valve is designed such that it can be switched when a pressure limit is exceeded in said first pressure chamber.

4. The hydraulic drive according to claim 1, further including a variable speed electric motor that drives said first hydraulic pump.

5. The hydraulic drive according to claim 1, wherein said high pressure tank has a tank pressure of 50 to 150 bar.

6. The hydraulic drive according to claim 1, wherein said high pressure tank has a tank pressure of 100 bar.

7. The hydraulic drive according to claim 1, further including a hydraulic auxiliary circuit that includes a feed pump and an auxiliary circuit directional control valve, wherein in a first switching position of the auxiliary circuit directional control valve, the feed pump is hydraulically connected with said high pressure tank.

8. The hydraulic drive according to claim 7, wherein said hydraulic auxiliary circuit further includes a cooler and a filter.

9. The hydraulic drive according to claim 1, further including a pressure sensor that is hydraulically connected with said first pressure chamber.

10. The hydraulic drive according to claim 1, further including a pressure sensor that is hydraulically connected with said additional pressure chamber.

11. The hydraulic drive according to claim 1, further including a position sensor for measuring a position of at least one of said differential piston and said additional piston.

12. The hydraulic drive according to claim 1, further including a pressure relief valve to protect against an excess pressure in said first hydraulic pump.

13. A method for operating a hydraulic drive having a hydraulic fluid therein and including a differential cylinder that includes a first pressure chamber, a second pressure chamber and a differential piston that separates the first pressure chamber from the second pressure chamber, a low pressure tank, a high pressure tank, and an additional hydraulic cylinder that includes an additional pressure chamber and an additional piston which limits the additional pressure chamber, wherein said differential piston is movably coupled with said additional piston by a common piston rod such that said differential piston and said additional piston are coaxial, the method comprising the steps of: moving the hydraulic fluid to said additional pressure chamber from said high pressure tank in a rapid stroke; moving the hydraulic fluid out of said additional pressure chamber via said hydraulic pump; moving the hydraulic fluid into said first pressure chamber via said hydraulic pump, wherein in the rapid stroke the first pressure chamber and the second pressure chamber are hydraulically connected; and moving the hydraulic fluid from said high pressure tank to said additional pressure chamber in a load stroke, in which the first pressure chamber and the second pressure chamber are not hydraulically connected and instead the second pressure chamber is hydraulically connected to the low pressure tank.

14. The method according to claim 13, wherein switching from the rapid stroke to the load stroke occurs when exceeding a pressure limit in first pressure chamber.

15. The method according to claim 14, wherein after a completion of the load stroke, said additional pressure chamber is supplied with hydraulic fluid from said high pressure tank.

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 drawings, wherein:

(2) FIG. 1 is a hydraulic circuit diagram that illustrates a first embodiment of a hydraulic drive according to the present invention;

(3) FIG. 2 is a substitute circuit diagram that illustrates the hydraulic drive according to the present invention, as shown in FIG. 1, in a rapid stroke; and

(4) FIG. 3 is a substitute circuit diagram that illustrates the hydraulic drive according to the present invention, as shown in FIG. 1, in a load stroke.

(5) Corresponding reference characters indicate corresponding parts throughout the several views. 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

(6) Referring now to FIG. 1, there is shown a hydraulic drive 10 according to the current invention. Drive 10 includes a differential cylinder 12 that includes a first pressure chamber 14, a second pressure chamber 16 and a differential piston 18 that separates the first pressure chamber 14 from second pressure chamber 16. First pressure chamber 14 has a first hydraulic effective surface 20, whereby second pressure chamber 16 has a second hydraulic effective surface 22. First hydraulic effective surface 20 is larger than second hydraulic surface 22. Piston 18 is connected with piston rod 24 on which, for example, a pressing tool that is not illustrated in the drawings can be mounted.

(7) Drive 10 moreover includes an additional hydraulic cylinder 26, having an additional pressure chamber 28 and an additional piston 30 which limits additional pressure chamber 28. Additional pressure chamber 28 comprises a hydraulic additional effective surface 32. Hydraulic additional effective surface 32 can be as large as a differential surface of the first hydraulic effective surface 20 and the second hydraulic effective surface 22, so that the following may apply:
A.sub.32=A.sub.20A.sub.22.

(8) Additional piston 30 can be mechanically movably coupled with differential piston 18 by a common piston rod 34.

(9) Drive 10 further includes an adjustable speed electric motor 36 whose direction of rotation can be reversible. Electric motor 36 drives a hydraulic pump 38 which includes a pump intake 40 and a pump outlet 42. Hydraulic pump 38 can be designed as a four-quadrant pump. It can however also be replaced by two two-quadrant pumps that deliver in an opposite direction and provide identical delivery volumes.

(10) Drive 10 includes a high pressure tank 44 and a low pressure tank 46. High pressure tank 44 may have a tank pressure of approximately 100 bar, whereas low pressure tank 44 may have a tank pressure of approximately 5 bar. Furthermore, drive 10 includes a directional control valve 48 having two switching positions. Directional valve 48 features a hydraulic control line 50 that is hydraulically connected with first pressure chamber 14 and can be moved from a first switching position illustrated in FIG. 1 against the force of a spring 52 into a second switching position.

(11) A directional control valve 48 or position sensor 54 can be arranged on additional piston 30, or respectively in the region of additional piston 30 with which a current piston position of additional piston 30 or respectively of differential piston 18 can be detected. Furthermore, a pressure sensor 56 can be provided that is hydraulically connected with additional pressure chamber 28 for measuring the pressure in additional pressure chamber 28. Furthermore, a pressure sensor 58 can be provided for the purpose of measuring the pressure in first pressure chamber 14 and which is connected hydraulically with first pressure chamber 14.

(12) A check valve 60 can be arranged between first pressure chamber 14 and second pressure chamber 16 for switching changeover compensation of directional control valve 48. An additional check valve 62 can furthermore be arranged for switching changeover compensation between second pressure chamber 16 and low pressure tank 46. Furthermore, a pressure relief valve 64 can be provided for overpressure protection of hydraulic pump 38.

(13) Hydraulic drive 10 can include an auxiliary hydraulic circuit 66 that includes a feed pump 68 which in turn is driven by an electric motor 70. Auxiliary circuit 66 can moreover include a cooler 72, a filter 74, a check valve 76, and a tank 78. Auxiliary circuit 66 furthermore can have an auxiliary circuit directional control valve 80 that has three switching positions. In a first switching position, to the left in FIG. 1, feeding pump 68 is hydraulically connected with high pressure tank 44. In a second switching position, in the center in FIG. 1, hydraulic fluid can only drain off via a pressure relief valve 82 that is intended for pressure relief of feed pump 68, pressure relief valve 62, as well as via a pre-tensioned valve 84 into auxiliary circuit 66, in other words through cooler 72 and filter 74. In a third switching position of auxiliary circuit direction control valve 80, to the right in FIG. 1, hydraulic fluid can be directed for cooling and/or filtering into auxiliary circuit 66.

(14) Hydraulic circuit 10 lastly may also include a check valve 86, which is provided to prevent cavitation during operation, in other words, it is provided for the case that the delivery volume of pump 38 is not adapted to the volumes of respective pressure chambers 14, 16, 28.

(15) In FIG. 1, pump intake 40, as well as high pressure tank 44 are hydraulically connected with additional pressure chamber 28. First pressure chamber 14 is furthermore hydraulically connected with pump outlet 42. In one switching position of directional control valve 48 illustrated on the right in FIG. 1, directional control valve 48 is shifted through the spring force of spring 52. In the first switching position, first pressure chamber 14 is hydraulically connected with second pressure chamber 48. If a pressure limit that is adjustable via the spring force of spring 52 is exceed, directional control valve 48 can be switched into a second switching position that is illustrated right in FIG. 1, whereby first pressure chamber 14 is not hydraulically connected with second pressure chamber 16 in the second switching position. Rather, second pressure chamber 16 is then hydraulically connected with low pressure chamber 46.

(16) Hydraulic drive 10 can operate as follows: during operation of hydraulic drive 10, high pressure tank 44 can be charged in the first switching position of auxiliary circuit directional control valve 80 by feed pump 68 to a tank pressure of approximately 100 bar. Due to the hydraulic connection of high pressure tank 44 with additional pressure chamber 28, the same acts as an hydraulic spring, in other words the hydraulic drive 10 is pre-tensioned upward, in other words in an opposite direction of an arrow 88, as shown in FIG. 1.

(17) In one rotational direction of electric motor 36, hydraulic pump 38 moves (pumps) hydraulic fluid at pump outlet 42 into first pressure chamber 14, whereas hydraulic pump 38 moves (pumps) hydraulic fluid out of additional pressure chamber 28 at pump intake 40. If directional control valve 48 is in its first switching position first pressure chamber 14 is connected with second pressure chamber 16. If differential piston 18 and additional piston 30 that are movably coupled via common piston rod 34 are moved downward in the direction of arrow 88, hydraulic fluid can flow from second pressure chamber 16 via directional control valve 48 into first pressure chamber 14, due to the hydraulic connection of first and second pressure chambers 14, 16.

(18) Only the hydraulic fluid for filling first pressure chamber 14 which cannot already overflow from second pressure chamber 16 must consequently be provided by the hydraulic pump 38 at pump outlet 42. Since hydraulic effective surface 32 is as large as the differential surface of first hydraulic effective surface 20 and second hydraulic effective surface 22, a substitute circuit diagram as illustrated in FIG. 2 can be realized. Hydraulic drive 10 acts like a synchronized speed cylinder 82 that can include additional pressure chamber 28 and a resulting pressure chamber 84.

(19) A hydraulic effective surface 86 of resulting pressure chamber 84 is consistent with the differential surface of first hydraulic effective surface 20 and second hydraulic effective surface 22. Piston 89, illustrated in FIG. 2, can be moved in a rapid stroke in the direction of arrow 90.

(20) It is important that FIG. 2 represents a substitute circuit diagram of drive 10 according to FIG. 1, whereby the direction of movement of the drive in FIG. 2 is not consistent with the direction of movement of the drive in FIG. 1. If, as explained above, hydraulic fluid can flow from second pressure chamber 16 into first pressure chamber 14 via directional control flow valve 48, movably coupled pistons 18, 30 can be moved downward in the direction of arrow 88 in a so-called rapid stroke at comparatively low force and high speed. The movement speed is adjustable via the rotational speed of electric motor 36.

(21) If a stamping or pressing tool which is not illustrated in FIG. 1 and that is arranged on piston rod 24 impinges upon an obstacle, for example, a metal sheet work piece, the pressure increases in first pressure chamber 14. If the pressure in first pressure chamber 14 increases to above the pressure limit or switching pressure of directional control valve 48 which is preset by spring 52 and which is fed back via control line 50 to directional control valve 48, then directional control valve 48 is moved from the first switching position into the second switching positionagainst the spring force of spring 52. Second pressure chamber 16 is now hydraulically connected with low pressure tank 46.

(22) The behavior of hydraulic drive 10 in the second switching position of directional control valve 48 can also be illustrated by a substitute circuit diagram that is illustrated in FIG. 3. Since the hydraulic fluid can no longer flow from second pressure chamber 16 into first pressure chamber 14, the entire hydraulic fluid that is necessary for filling first pressure chamber 14 must be provided by hydraulic pump 38. At an unchanged pump pressure of hydraulic pump 38, hydraulic pump 38 now no longer delivers onto the differential surface of first hydraulic effective surface 20 and of second hydraulic effective surface 22, but rather only onto first hydraulic effective surface 20. Hydraulic drive 10 thus acts in the second switching position of directional control valve 48 like a differential cylinder 92, as shown in FIG. 3.

(23) It is important that also in FIG. 3 a substitute circuit diagram of drive 10 is illustrated, whereby the operating direction of drive 10 in FIG. 3 is not consistent with the operating direction of the drive in FIG. 1. If hydraulic pump 38 described above moves (pumps) hydraulic fluid at pump outlet 42 into first pressure chamber 14 and moves (sucks) hydraulic fluid at pump intake 40 out of additional pressure chamber 28, movably coupled pistons 18, 30 can be moved in a so-called load stroke downward in the direction of arrow 88 at comparatively great force and low speed.

(24) Since now the delivery volume of hydraulic pump 38 at pump intake 40 and at pump outlet 42 is no longer adapted to the surface ratio of hydraulic effective surfaces 20, 32 andas shown in FIG. 3hydraulic drive 10 acts like a differential cylinder 92, additional hydraulic fluid for filling additional pressure chamber 28 must be provided by high pressure tank 44. Since high pressure tank 44 has a tank pressure of approximately 100 bar, a pressure acts upon pump intake 40 in rapid stroke, whereby hydraulic pump 38 can thus be partially operated as a motor. Due to the pressure at pump intake 40, torque assistance can be achieved, whereby in turn electric motor 36 can be sized smaller.

(25) Since additional pressure chamber 28 is hydraulically connected with a high pressure tank 44, cutting shock damping can be provided during the operation of hydraulic drive 10 by the pre-tensioning of additional pressure chamber 28, in an opposite direction of the effective direction of drive 10 in the load stroke mode. The force resulting from the pressure in additional pressure chamber 28 can thus, for example, prevent thatin the event of a punch tearing through a metal sheet work piecethe punch makes an uncontrolled movement. Cutting shock damping can be adjusted by adjusting the pressure in high pressure chamber 44.

(26) After completion of the load stroke, the pressure in first pressure chamber 14 can drop below a reset pressure which is below the pressure limit of directional control valve 48. Directional control valve 48 can again be returned into the first switching position through the spring force of spring 52.

(27) If the rotational direction of electric motor 26 and thereby also the delivery direction of hydraulic pump 38 is reversed, and hydraulic pump 38 therefore moves (pumps) hydraulic fluid at the pump intake out of hydraulic pump 38, and at pump outlet 42 moves (sucks) hydraulic fluid into hydraulic pump 38, movably coupled pistons 18, 30 can again be moved upward in a return stroke, in the opposite direction to that indicated by arrow 88.

(28) 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.