US3914975A - Hydraulic press brake - Google Patents
Hydraulic press brake Download PDFInfo
- Publication number
- US3914975A US3914975A US512943A US51294374A US3914975A US 3914975 A US3914975 A US 3914975A US 512943 A US512943 A US 512943A US 51294374 A US51294374 A US 51294374A US 3914975 A US3914975 A US 3914975A
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- United States
- Prior art keywords
- die
- punch
- hydraulically actuated
- hydraulic
- bending operation
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- Expired - Lifetime
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
- B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
- B21D5/0272—Deflection compensating means
Definitions
- ABSTRACT A hydraulic press brake is disclosed having a stationary die cooperating with a movable die or punch to perform a bending operation on an elongated workpiece. Movement of the punch is effected by means of a pair of first hydraulic piston-cylinder units each of which is located proximate to one end of the punch.
- At least one second hydraulic piston-cylinder unit acts on the stationary die at a location intermediate the ends thereof to impart a convex bend to the fixed die to compensate for any concave bending of the movable die during a bending operation, thereby maintaining the surfaces of the fixed and movable dies substantially parallel.
- Pressurized hydraulic fluid is fed to the first and second hydraulic piston-cylinder units through feed conduits leading from a common pump, with a pressure reducing valve being interposed in the feed conduits between the pump and the second hydraulic piston-cylinder unit.
- FIG. 1 A first figure.
- FIG. 1 is a front view, with portions broken away, of a hydraulic press brake embodying the concepts of the present invention, and including a schematic illustration of the hydraulic system;
- FIG. 2 is a perspective view of a typical product bent in accordance with conventional techniques
- FIG. 3 is a perspective view showing a typical punch and cooperating lower die
- FIG. 4 is a view in side elevation of the apparatus shown in FIG. I.
- FIG. 5 is a sectional view of a reducing valve employed in the hydraulic system schematically depicted in FIG. 1.
- 9 denotes a lower stationary frame carrying a lower die 3.
- the hydraulic mechanisms 11, 13, 15 are provided respectively with piston and piston rods 11p, 13p and 15p which exert an upward force on the die 3 through the frame 9.
- three such hydraulic mechanisms are disclosed, although it will be appreciated that this number may be varied without departing from the spirit and scope of the invention.
- the .ram 17 carrying the upper punch or die 1 is constructed with athicker central portion in accordance with known techniquesrto minimize any upward or concave warpingduring a bending operation.
- Theframe 9 islpivotally carried on horizontal fixed pins 19, 21, the said frame having an elongated opening or slot 23 to accommodate pine 21. This arrangement permits the frame 9 to bend upwardly or convexly when an upward force is exerted thereon by the hydraulic mechanisms 11, 13 and. 15.
- Hydraulic mechanisms 33, 35 are positioned to exert downward forces on the ends of the ram 17 carrying punch l.
- a pump P is driven by motor M and draws hydraulic fluid from a tank T. The fluid is pumped through conduits 30, 29 to mechanism 33, through conduits 30, 31 to mechanism 35, and through conduits 30, 29, 27 and thence through conduits 39, 41 and 43 to hydraulic mechanisms 15, 13 and 11.
- a pressure reducing valve 25 is located in conduit 27 between the hydraulic mechanisms 15, l3, l1 and pump P.
- the pressure reducing valve 25 is of a type wherein the amount of pressure reduction may be optionally selected so that any desired pressure may be obtained in proportion to the pressure being applied to the hydraulic mechanisms 33, 35.
- FIG. 5 shows one such typical pressure reducing valve 25 wherein P is a high pressure inlet, P is a reduced pressure outlet, P is a port for a pressure gauge, 1 is a piston and S is a spring. With this arrangement, any increase (or decrease) in pressure P is accompanied by a proportional change in pressure P
- the conduits 37, 39, 41 and 43 are provided with appropriate check valves.
- the hydraulic press brake of the present invention is characterized in that the upward warp of the stationary frame and the die carried thereon follows the warp of the ram and the punch to avoid such oppositely directed warps of the upper and the lower dies which might otherwise separate the punch from the lower die at the center, thereby obviating the defects that characterize products bent in accordance with conventional techniques as shown in FIG. 2.
- a hydraulic press brake comprising: stationary frame means supporting an elongated die; movable ram means carrying an elongated punch, said punch being adapted to cooperate with said die in performing a bending operation on an elongated workpiece positioned therebetween; first hydraulically actuated means acting on said movable ram means at locations proximate to the ends thereof for moving said ram means and punch towards said stationary frame and elongated die during a bending operation; second hudraulically actuated means acting on said stationary frame means at a location intermediate the ends of the die supported thereon, said second hydraulically actuated means being operative to bend said stationary draulic fluid being applied to said second hydraulically actuated means in proportion to the pressure of the hydraulic fluid being applied to said first hydraulically actuated means.
Abstract
A hydraulic press brake is disclosed having a stationary die cooperating with a movable die or punch to perform a bending operation on an elongated workpiece. Movement of the punch is effected by means of a pair of first hydraulic piston-cylinder units each of which is located proximate to one end of the punch. At least one second hydraulic piston-cylinder unit acts on the stationary die at a location intermediate the ends thereof to impart a convex bend to the fixed die to compensate for any concave bending of the movable die during a bending operation, thereby maintaining the surfaces of the fixed and movable dies substantially parallel. Pressurized hydraulic fluid is fed to the first and second hydraulic piston-cylinder units through feed conduits leading from a common pump, with a pressure reducing valve being interposed in the feed conduits between the pump and the second hydraulic piston-cylinder unit.
Description
United States Patent [1 1 Kawano Oct. 28, 1975 [73] Assignee: Amada Company Limited, lsehara,
Japan [22] Filed: Oct. 7, 1974 [21] Appl. No.: 512,943
Related U.S. Application Data [63] Continuation-impart of Ser. No. 358,125, May 5, 1973, abandoned, which is a continuation of Ser. No. 209,771, Dec. 20, 1971, abandoned.
[30] Foreign Application Priority Data FOREIGN PATENTS OR APPLICATIONS 1,452,818 11/1970 Germany 72/389 Primary Examiner-C. W. Lanham Assistant Examiner-Gene P. Crosby Attorney, Agent, or FirmThompson, Birch, Gauthier & Samuel [5 7] ABSTRACT A hydraulic press brake is disclosed having a stationary die cooperating with a movable die or punch to perform a bending operation on an elongated workpiece. Movement of the punch is effected by means of a pair of first hydraulic piston-cylinder units each of which is located proximate to one end of the punch. At least one second hydraulic piston-cylinder unit acts on the stationary die at a location intermediate the ends thereof to impart a convex bend to the fixed die to compensate for any concave bending of the movable die during a bending operation, thereby maintaining the surfaces of the fixed and movable dies substantially parallel. Pressurized hydraulic fluid is fed to the first and second hydraulic piston-cylinder units through feed conduits leading from a common pump, with a pressure reducing valve being interposed in the feed conduits between the pump and the second hydraulic piston-cylinder unit.
2 Claims, 5 Drawing Figures US. Patent Oct. 28, 1975 Sheet 1 of2 3,914,975
FIG.
FIG. 5
US. Patent Oct. 28, 1975 Sheet2of2 3,914,975
FIG. 3
INVENTOR MMW ATTORNEYS HYDRAULIC PRESS BRAKE DESCRIPTION or THEINVENTION mechanical characteristics of the workpiece, e.g., tensile strength, elastic limit, yield point, as well as the resilient characteristics of the workpiece. For example, when a conventional press brake is operated with use of an elongated punch and an elongated die, the downward forces on the punch are exerted at the ends respectively of the ram supporting the punch and the stationary frame supporting the die. Thus, the punch has a tendency to warp upwardly in a concave manner, whereas the stationary die has a tendency to warp downwardly in a concave manner, because of the resistance of the workpiece to bending. As a result, the lower surface of the punch tends to part from the upper surface of the die. The resulting product is distorted (as shown in FIG. 2) with warps and 7 at the central portions thereof.
Attempts have been made at solving the above problem by increasing the thickness of the central portion of the ram supporting the movable punch. This arrangement can only be employed, however, for the bending of certain materials of a specified bending resistance. Inaccurate bends are still likely to result when materials of different kinds are being bent with greater resistances to bending.
A general object of the present invention is the provision of novel and improved means for obviating the problems noted above. This and other more specific objects and advantages of the present invention will become more apparent as the description proceeds with the aid of the accompanying drawings wherein:
FIG. 1 is a front view, with portions broken away, of a hydraulic press brake embodying the concepts of the present invention, and including a schematic illustration of the hydraulic system;
FIG. 2 is a perspective view of a typical product bent in accordance with conventional techniques;
FIG. 3 is a perspective view showing a typical punch and cooperating lower die;
FIG. 4 is a view in side elevation of the apparatus shown in FIG. I; and
FIG. 5 is a sectional view of a reducing valve employed in the hydraulic system schematically depicted in FIG. 1.
With reference now to the drawings, 9 denotes a lower stationary frame carrying a lower die 3. Reference characters l1, l3 and denote hydraulic mechanisms or cylinders which are mounted on a rigid plate 16 secured to the frame 9 at locations intermediate the ends of the die 3. The hydraulic mechanisms 11, 13, 15 are provided respectively with piston and piston rods 11p, 13p and 15p which exert an upward force on the die 3 through the frame 9. In the embodiment herein disclosed, three such hydraulic mechanisms are disclosed, although it will be appreciated that this number may be varied without departing from the spirit and scope of the invention.
The .ram 17 carrying the upper punch or die 1 is constructed with athicker central portion in accordance with known techniquesrto minimize any upward or concave warpingduring a bending operation.
The pressure reducing valve 25 is of a type wherein the amount of pressure reduction may be optionally selected so that any desired pressure may be obtained in proportion to the pressure being applied to the hydraulic mechanisms 33, 35. FIG. 5 shows one such typical pressure reducing valve 25 wherein P is a high pressure inlet, P is a reduced pressure outlet, P is a port for a pressure gauge, 1 is a piston and S is a spring. With this arrangement, any increase (or decrease) in pressure P is accompanied by a proportional change in pressure P Although not shown, it will be further understood that the conduits 37, 39, 41 and 43 are provided with appropriate check valves.
In view of the above, it will now be seen that since the stationary frame 9 and the lower die 3 are pressed upwards by the hydraulic cylinders 11, 13 and 15, during a bending operation, they do not warp downward as shown by C in FIG. 1, but warp as shown by curve C,, so as to follow the warp of the punch 1 and the ram 17 as shown by curve C Thus the hydraulic press brake of the present invention is characterized in that the upward warp of the stationary frame and the die carried thereon follows the warp of the ram and the punch to avoid such oppositely directed warps of the upper and the lower dies which might otherwise separate the punch from the lower die at the center, thereby obviating the defects that characterize products bent in accordance with conventional techniques as shown in FIG. 2.
I claim:
1. A hydraulic press brake comprising: stationary frame means supporting an elongated die; movable ram means carrying an elongated punch, said punch being adapted to cooperate with said die in performing a bending operation on an elongated workpiece positioned therebetween; first hydraulically actuated means acting on said movable ram means at locations proximate to the ends thereof for moving said ram means and punch towards said stationary frame and elongated die during a bending operation; second hudraulically actuated means acting on said stationary frame means at a location intermediate the ends of the die supported thereon, said second hydraulically actuated means being operative to bend said stationary draulic fluid being applied to said second hydraulically actuated means in proportion to the pressure of the hydraulic fluid being applied to said first hydraulically actuated means.
2. The apparatus as claimed in claim 1 wherein said first and second hydraulically actuated means comprise piston-cylinder assemblies.
Claims (2)
1. A hydraulic press brake comprising: stationary frame means supporting an elongated die; movable ram means carrying an elongated punch, said punch being adapted to cooperate with said die in performing a bending operation on an elongated workpiece positioned therebetween; first hydraulically actuated means acting on said movable ram means at locations proximate to the ends thereof for moviNg said ram means and punch towards said stationary frame and elongated die during a bending operation; second hydraulically actuated means acting on said stationary frame means at a location intermediate the ends of the die supported thereon, said second hydraulically actuated means being operative to bend said stationary frame means and die convexly to thereby compensate for concave bending of said punch and ram means during a bending operation; hydraulic pump means; conduit means connecting said hydraulic pump means to said first and second hydraulically actuated means; and pressure reducing valve means in said conduit means between said pump means and said second hydraulically actuated means, said pressure reducing valve means being operative to reduce the pressure of the hydraulic fluid being applied to said second hydraulically actuated means in proportion to the pressure of the hydraulic fluid being applied to said first hydraulically actuated means.
2. The apparatus as claimed in claim 1 wherein said first and second hydraulically actuated means comprise piston-cylinder assemblies.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US512943A US3914975A (en) | 1970-12-25 | 1974-10-07 | Hydraulic press brake |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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JP11768570 | 1970-12-25 | ||
US35812573A | 1973-05-05 | 1973-05-05 | |
US512943A US3914975A (en) | 1970-12-25 | 1974-10-07 | Hydraulic press brake |
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US3914975A true US3914975A (en) | 1975-10-28 |
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US512943A Expired - Lifetime US3914975A (en) | 1970-12-25 | 1974-10-07 | Hydraulic press brake |
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Cited By (31)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4016742A (en) * | 1970-12-25 | 1977-04-12 | Seiji Shiokawa | Press-forming apparatus |
US4098109A (en) * | 1976-04-13 | 1978-07-04 | Promecam Sisson-Lehmann | Bending press or similar machine tool |
US4332536A (en) * | 1980-04-09 | 1982-06-01 | Nrm Corporation | Hydraulic tire press |
US4347727A (en) * | 1980-07-28 | 1982-09-07 | Galiger Barry J | Programmable upward-stroke insert mechanism for bending brakes and method of use |
US4390334A (en) * | 1980-04-09 | 1983-06-28 | Nrm Corporation | Hydraulic tire press |
US4557792A (en) * | 1983-04-15 | 1985-12-10 | Hitachi, Ltd. | Hot press |
US4563139A (en) * | 1983-01-27 | 1986-01-07 | Kabushiki Kaisha Kobe Seiko Sho | Mold clamping mechanism for tire curing machines |
US4580434A (en) * | 1983-11-14 | 1986-04-08 | Cincinnati Incorporated | Deflection compensating assembly for a press brake |
US4702688A (en) * | 1985-04-15 | 1987-10-27 | Bernd Schenk | Apparatus for producing articles from a synthetic resin |
US4825681A (en) * | 1987-01-22 | 1989-05-02 | Kenneth L. Smedberg | Pneumatic press counterbalance and cushion construction |
US4860571A (en) * | 1986-09-26 | 1989-08-29 | Kenneth L. Smedberg | Power press with improved cushioning system |
US4875849A (en) * | 1988-03-14 | 1989-10-24 | Huang Jin S | Rubber shaping machine |
US4918956A (en) * | 1987-08-27 | 1990-04-24 | The Minster Machine Company | Monitorable and compensatable feedback tool and control system for a press using a solid tool backup element |
US4939918A (en) * | 1987-08-27 | 1990-07-10 | The Minster Machine Company | Monitorable and compensatable feedback tool and control system for a press |
US4945742A (en) * | 1987-08-27 | 1990-08-07 | The Minster Machine Company | Monitorable and compensatable feedback tool and control system for a press |
US5067340A (en) * | 1988-05-05 | 1991-11-26 | Macgregor Donald C | Precision press brake |
US5193452A (en) * | 1989-09-11 | 1993-03-16 | Willem Dieperink | Folding press with deflection compensating means |
US5347840A (en) * | 1991-08-17 | 1994-09-20 | L. Schuler Gmbh | Press comprising a press table and a sliding table |
US5930888A (en) * | 1995-12-01 | 1999-08-03 | Ralph C. Ball | Device to hold, dispense and install slotted weights used with fishing line |
FR2782942A1 (en) * | 1998-09-09 | 2000-03-10 | Amada Europ Sa | ACTIVE LOWER APRON BENDING PRESS |
DE3943349C2 (en) * | 1988-12-29 | 2001-08-23 | Amada Co | Sheet metal bending machine |
US20040099038A1 (en) * | 2002-10-17 | 2004-05-27 | Alberto Arduino | Bending press with a substantially undeformable toolholder beam |
US20040103707A1 (en) * | 2000-12-12 | 2004-06-03 | Andreas Winters | Internal high pressure forming device and method and corresponding tool system |
AT507946B1 (en) * | 2009-03-13 | 2011-10-15 | Amada Europ Sa | BANK PRESS FOR BENDING FOILS |
WO2013072859A1 (en) * | 2011-11-15 | 2013-05-23 | Adira, S.A. | Beam for deformation compensation in press brakes |
ITTV20120125A1 (en) * | 2012-07-06 | 2014-01-07 | Gasparini Ind S R L | DEVICE FOR BENDING IN FOLDING PRESSES. |
US20150273555A1 (en) * | 2012-10-18 | 2015-10-01 | Nivora Ip B.V. | Spring Means for Device for Working Sheet-Like Material |
US20160144588A1 (en) * | 2013-06-19 | 2016-05-26 | Bruderer Ag | Method for warping the machine bed and/or the press ram of a punching press and punching press |
CN106271622A (en) * | 2016-08-31 | 2017-01-04 | 武汉立奥自动化有限公司 | A kind of dovetail forming processing device |
USD807933S1 (en) * | 2015-08-14 | 2018-01-16 | Henri Emil Louis Maurice Zermatten | Tool for a press brake |
CN108723126A (en) * | 2018-05-25 | 2018-11-02 | 安徽省航天机床制造股份有限公司 | A kind of deflection compensating mechanism of bending machine |
Citations (4)
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US3163105A (en) * | 1962-06-11 | 1964-12-29 | Pacific Ind Mfg Co | Pivotal drive connection |
US3550425A (en) * | 1967-07-26 | 1970-12-29 | Promecan Sisson Lehmann | Hydraulic machine for deforming sheet metal |
US3587286A (en) * | 1968-12-06 | 1971-06-28 | Rezso Fritsch | Press brake |
US3668919A (en) * | 1969-09-12 | 1972-06-13 | Toshio Hongo | Combination hydraulic shearing and pressbrake machine |
-
1974
- 1974-10-07 US US512943A patent/US3914975A/en not_active Expired - Lifetime
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3163105A (en) * | 1962-06-11 | 1964-12-29 | Pacific Ind Mfg Co | Pivotal drive connection |
US3550425A (en) * | 1967-07-26 | 1970-12-29 | Promecan Sisson Lehmann | Hydraulic machine for deforming sheet metal |
US3587286A (en) * | 1968-12-06 | 1971-06-28 | Rezso Fritsch | Press brake |
US3668919A (en) * | 1969-09-12 | 1972-06-13 | Toshio Hongo | Combination hydraulic shearing and pressbrake machine |
Cited By (39)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4016742A (en) * | 1970-12-25 | 1977-04-12 | Seiji Shiokawa | Press-forming apparatus |
US4098109A (en) * | 1976-04-13 | 1978-07-04 | Promecam Sisson-Lehmann | Bending press or similar machine tool |
US4332536A (en) * | 1980-04-09 | 1982-06-01 | Nrm Corporation | Hydraulic tire press |
US4390334A (en) * | 1980-04-09 | 1983-06-28 | Nrm Corporation | Hydraulic tire press |
US4347727A (en) * | 1980-07-28 | 1982-09-07 | Galiger Barry J | Programmable upward-stroke insert mechanism for bending brakes and method of use |
US4686129A (en) * | 1983-01-27 | 1987-08-11 | Kabushiki Kaisha Kobe Seiko Sho | Mold clamping mechanism for tire curing machines |
US4563139A (en) * | 1983-01-27 | 1986-01-07 | Kabushiki Kaisha Kobe Seiko Sho | Mold clamping mechanism for tire curing machines |
US4557792A (en) * | 1983-04-15 | 1985-12-10 | Hitachi, Ltd. | Hot press |
US4580434A (en) * | 1983-11-14 | 1986-04-08 | Cincinnati Incorporated | Deflection compensating assembly for a press brake |
US4702688A (en) * | 1985-04-15 | 1987-10-27 | Bernd Schenk | Apparatus for producing articles from a synthetic resin |
US4860571A (en) * | 1986-09-26 | 1989-08-29 | Kenneth L. Smedberg | Power press with improved cushioning system |
US4825681A (en) * | 1987-01-22 | 1989-05-02 | Kenneth L. Smedberg | Pneumatic press counterbalance and cushion construction |
US4945742A (en) * | 1987-08-27 | 1990-08-07 | The Minster Machine Company | Monitorable and compensatable feedback tool and control system for a press |
US4918956A (en) * | 1987-08-27 | 1990-04-24 | The Minster Machine Company | Monitorable and compensatable feedback tool and control system for a press using a solid tool backup element |
US4939918A (en) * | 1987-08-27 | 1990-07-10 | The Minster Machine Company | Monitorable and compensatable feedback tool and control system for a press |
US4875849A (en) * | 1988-03-14 | 1989-10-24 | Huang Jin S | Rubber shaping machine |
US5067340A (en) * | 1988-05-05 | 1991-11-26 | Macgregor Donald C | Precision press brake |
DE3943349C2 (en) * | 1988-12-29 | 2001-08-23 | Amada Co | Sheet metal bending machine |
US5193452A (en) * | 1989-09-11 | 1993-03-16 | Willem Dieperink | Folding press with deflection compensating means |
US5347840A (en) * | 1991-08-17 | 1994-09-20 | L. Schuler Gmbh | Press comprising a press table and a sliding table |
US5930888A (en) * | 1995-12-01 | 1999-08-03 | Ralph C. Ball | Device to hold, dispense and install slotted weights used with fishing line |
FR2782942A1 (en) * | 1998-09-09 | 2000-03-10 | Amada Europ Sa | ACTIVE LOWER APRON BENDING PRESS |
WO2000013813A1 (en) * | 1998-09-09 | 2000-03-16 | Amada Europe | Press brake with active lower table |
US6401512B1 (en) | 1998-09-09 | 2002-06-11 | Amada Europe | Press brake with active lower table |
US20040103707A1 (en) * | 2000-12-12 | 2004-06-03 | Andreas Winters | Internal high pressure forming device and method and corresponding tool system |
US20040099038A1 (en) * | 2002-10-17 | 2004-05-27 | Alberto Arduino | Bending press with a substantially undeformable toolholder beam |
US7013698B2 (en) * | 2002-10-17 | 2006-03-21 | Alberto Arduino | Bending press with a substantially undeformable toolholder beam |
AT507946B1 (en) * | 2009-03-13 | 2011-10-15 | Amada Europ Sa | BANK PRESS FOR BENDING FOILS |
WO2013072859A1 (en) * | 2011-11-15 | 2013-05-23 | Adira, S.A. | Beam for deformation compensation in press brakes |
ITTV20120125A1 (en) * | 2012-07-06 | 2014-01-07 | Gasparini Ind S R L | DEVICE FOR BENDING IN FOLDING PRESSES. |
EP2682198A1 (en) * | 2012-07-06 | 2014-01-08 | Gasparini Industries S.r.l. | Cambering device in bending presses |
EP2682198B1 (en) | 2012-07-06 | 2018-06-20 | Gasparini Industries S.r.l. | Cambering device in bending presses |
US20150273555A1 (en) * | 2012-10-18 | 2015-10-01 | Nivora Ip B.V. | Spring Means for Device for Working Sheet-Like Material |
US9440275B2 (en) * | 2012-10-18 | 2016-09-13 | Nivora Ip B.V. | Spring means for device for working sheet-like material |
US20160144588A1 (en) * | 2013-06-19 | 2016-05-26 | Bruderer Ag | Method for warping the machine bed and/or the press ram of a punching press and punching press |
USD807933S1 (en) * | 2015-08-14 | 2018-01-16 | Henri Emil Louis Maurice Zermatten | Tool for a press brake |
CN106271622A (en) * | 2016-08-31 | 2017-01-04 | 武汉立奥自动化有限公司 | A kind of dovetail forming processing device |
CN106271622B (en) * | 2016-08-31 | 2018-07-17 | 武汉立奥自动化有限公司 | A kind of dovetail forming processing device |
CN108723126A (en) * | 2018-05-25 | 2018-11-02 | 安徽省航天机床制造股份有限公司 | A kind of deflection compensating mechanism of bending machine |
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