WO2005092549A1 - Dispositif d’amortissement pour machine-outil, machine et procede de decoupe adiabatique a tres haute cadence - Google Patents
Dispositif d’amortissement pour machine-outil, machine et procede de decoupe adiabatique a tres haute cadence Download PDFInfo
- Publication number
- WO2005092549A1 WO2005092549A1 PCT/FR2004/003207 FR2004003207W WO2005092549A1 WO 2005092549 A1 WO2005092549 A1 WO 2005092549A1 FR 2004003207 W FR2004003207 W FR 2004003207W WO 2005092549 A1 WO2005092549 A1 WO 2005092549A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cylinder
- damping
- tool
- cutting
- machine
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
- B23D23/00—Machines or devices for shearing or cutting profiled stock
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
- B23D15/00—Shearing machines or shearing devices cutting by blades which move parallel to themselves
- B23D15/12—Shearing machines or shearing devices cutting by blades which move parallel to themselves characterised by drives or gearings therefor
- B23D15/14—Shearing machines or shearing devices cutting by blades which move parallel to themselves characterised by drives or gearings therefor actuated by fluid or gas pressure
Definitions
- the present invention relates to a damping device for a machine tool, intended for absorbing excess energy during an impact generated in this machine tool, for cutting or punching operations, for example, as well an adiabatic cutting machine incorporating said damping device and an adiabatic cutting process at very high speed.
- Sequential cutting of parts such as metal bars can be done using shearing machine tools.
- adiabatic cutting machines
- adiabatic In order to obtain an adiabatic cut, as opposed to the traditional cut by shearing, it is necessary to use a very high energy, in order to generate a local softening of the metal over a few hundredths of a millimeter, thus creating a zone with the plastic condition.
- This adiabatic cutting makes it possible to cut steels of great hardnesses, going up to 300 HB, without carrying out a heat treatment of annealing before to soften the metal.
- the cut section is of high quality, because it has a good perpendicularity, as well as an improved surface finish, without burrs or chips.
- the energy necessary for this type of cutting is obtained by setting in motion at a speed greater than 10 m / s a mass, also called a striking cylinder, which moves a striking hammer and a movable knife. It is the impact of this mobile knife on the bar that allows it to be cut into pieces. However, the energy generated is only used at 90% for cutting and the excess energy is transmitted to the machine tool itself.
- the mass of the tool cylinder should be increased in proportions such that this solution cannot be envisaged industrially.
- oversizing would necessarily reduce the cutting rates due to the masses to be moved.
- a quick estimate shows that this type of machine is not suitable for cutting bars whose diameter exceeds about 20 mm.
- this machine requires the superimposition in height of the tool cylinders and shock absorber. This configuration is very bulky, and requires a deep civil engineering pit, which increases the installation costs accordingly.
- the object of the present invention is therefore to remedy the drawbacks of the devices of the prior art by providing a damping device for a machine tool generating an impact, having a reduced bulk.
- the integration of this damping device in an adiabatic cutting machine must allow the cutting of metal bars at a rate greater than or equal to 80 pieces / min.
- this device must be able to be versatile and thus be used both for cutting bars less than 20 mm in diameter, as for cutting bars with diameters up to 80 mm.
- a first object of the invention consists of a damping device for a machine tool, intended for the absorption of excess energy during an impact generated in said machine tool, comprising a block support provided with an orifice, inside which can slide at least one damping cylinder between a high position and a low position, said low position being reached by absorption of said excess energy.
- a second object of the invention consists of an adiabatic machine for cutting metal bars, comprising in its upper part a fixed knife, a striking cylinder, a striking hammer and a movable knife, driven by the striking hammer, and in its lower part a damping device according to the invention.
- the machine according to the invention comprises hydraulic control means of the damping cylinder and / or of the tool cylinder.
- a third object of the invention is constituted by a sequential cutting process at very high rate of metal bars, comprising the repetition of a cycle, the steps of which consist in: - introducing a metal bar into a machine according to the invention, up to '' that the area where it is to be cut is placed directly above the moving knife, - set the moving knife in motion under the weight of the striking cylinder, until a linear speed of at least 10m / s is reached , - cut the metal bar under the impact of the movable knife, the stroke of which is stopped by contact with the at least one jack of the damping device, the position of which has been previously adjusted, then - replace the movable knife and the cylinder of the damping device in their initial position.
- the cutting machine comprises a tool cylinder integrated in the damping device so that in the low position, the tool cylinder is entirely below the surface thereof, process in which replaces the movable knife in its initial position under the action of the tool cylinder, then retracts the tool cylinder inside the damping cylinder, to a level below the surface thereof, before proceeding with a new cutting cycle, the tool cylinder accompanying the downward movement of the damping cylinder when the latter receives the impact of said movable knife.
- the method according to the invention may also have the following characteristics, alone or in combination: - the cutting rate of said metal bars is greater than or equal to 80 pieces per minute, - the metal bars have a diameter greater than 20 mm, of preferably greater than 29 mm, or even 40 mm. - the metal bars have a diameter between 35 and 80 mm. - the metal bars are made of steel.
- FIG. 1A shows a schematic sectional view of a cutting device adiabatic according to the invention, at the start of the cycle
- - Figure 1B shows a schematic sectional view of the cutting device of Figure 1A, in the middle of the cycle
- - Figure 1C shows a schematic sectional view of the cutting device FIG. 1A, at the end of the cycle
- - FIG. 2A represents a detailed section view of an embodiment of an adiabatic cutting device according to the invention, at the start of the cycle
- FIG. 2B represents a view in detailed section of the device of FIG. 2A, in the middle of the cycle
- FIG. 2C represents a detailed section view of the device of FIG. 2A, at the end of the cycle.
- the upper part 3 of the cutting machine 1 comprises, from top to bottom, a striking cylinder 7 placed above and at a certain distance from a striking hammer 8, itself secured to a movable knife 9.
- the cylinder impact device is connected to a hydraulic or pneumatic circuit making it possible to move it in translation in the vertical direction, at very high speed.
- the movable knife 9 comprises in its middle an opening 10 whose dimensions are such that the metal bar B having to be cut, can pass through said opening 10.
- the movable knife 9 can move in translation in the vertical direction.
- the upper part 3 of the machine 1 finally comprises a fixed knife 1 1, placed against the movable knife 9, upstream of the path of the metal bar B to be cut.
- This fixed knife January 1 also includes an opening 12 whose dimensions are such that the metal bar B to be cut, can pass through said opening 12.
- Figure 1A shows the machine 1 at the start of the cycle.
- the striking cylinder 7 is in the high position, at a preset distance from the striking hammer 8, this distance determining the amount of energy transmitted to the moving knife 9.
- the moving knife 9 is also in the high position, the opening 10 being positioned in the extension of the opening 12, to allow the introduction of a bar B to be cut.
- the tool cylinder 6 is retracted inside the damping cylinder 5 before the movable knife 9 is set in motion.
- the damping cylinder 5 is in the high position .
- FIG. 1B shows the same device in the middle of the cycle, during the setting in motion of the striking cylinder 7, which has caused the displacement in translation of the assembly constituted by the striking hammer 8 and the movable knife 9.
- a piece L is cut adiabatically under the action of the upper part of said movable knife 9, while the energy not absorbed by the cutting is absorbed by the downward movement of the damping cylinder 5 when it enters contact with the lower part of the movable knife 9.
- the striking hammer 8 and the movable knife 9 move, in this example, from 1 to 5 mm downward, to ensure adiabatic cutting of the piece L.
- FIG. 1C represents the same device at the end of the cycle, after cutting the piece L.
- the damping cylinder 5 is translated to return to the initial position, as is the striking cylinder 7 which returns to the initial position by translation towards the high.
- the movable knife 9 is also returned to the initial position by the movement from the bottom to the top of the tool cylinder 6, placed inside the damping cylinder 5, and which is made to emerge by means of a supply. hydraulic or pneumatic.
- the bar B is then advanced the length of a piece, then the tool cylinder 6 is retracted into the damping cylinder 5, under the surface thereof.
- the machine 1 is then again in the start of cycle configuration, as shown in FIG. 1A.
- the entire cycle was carried out in 0.4 ms for cutting a steel bar of hardness 285HB and with a diameter of 70mm.
- an adiabatic hydraulic cutting machine 21 comprising a lower part 22 and an upper part 23.
- the lower part 22 consists of a block 24, possibly removable , and provided with four support feet, a damping device comprising a damping cylinder 25, and a tool cylinder 26 integrated in the cylinder 15 coaxially.
- the damping cylinder 25 slides inside an orifice 40 arranged in the block 24, and is closed by a cover 41 ensuring the sealing of the various hydraulic chambers and the guiding of the damping cylinder 25 in the upper part of the block 24.
- the guiding of the damping cylinder 25 in the lower part of the block 24 is ensured by guide seals and by the deposition of an anti-wear coating on the surface of said cylinder 25.
- This coating which is preferably metallic, allows in particular to improve the life of the jack 25, in a manner known per se. Provision may also be made to combine a first coating in the upper part of the cylinder 25 in order to extend the life of the seals by minimizing their wear, and a second coating in the lower part of the cylinder 25 to improve its wear resistance as well as that of block 24. Those skilled in the art know the most suitable materials for producing these different coatings. Thus protected, these elements can be used for several million cycles.
- the jack 25 is here produced in a single block in a steel having undergone various conventional treatments to optimize its wear resistance and its resilience. It is bored in its center to allow the mounting of the tool cylinder 26.
- the damping cylinder 25 finally comprises at its lower part a coaxial needle 48 externally taking the form of a rack on which a graduated wheel 49 comes to mesh.
- the needle 48 is pierced axially and radially in the upper part, its various orifices being connected to an oil reservoir (not shown).
- the tool cylinder 26 can slide inside the bore arranged in the shock absorber cylinder 25.
- This bore is closed at the bottom by a plug 50 screwed into the shock absorber cylinder 25.
- the translational guidance of the tool cylinder 26 in the cylinder 25 is provided by guide seals, as well as by depositing suitable antiwear coatings.
- the cylinder 26 is produced in a single block in a steel having undergone various treatments to improve its resistance to wear and its resilience.
- the assembly of the damping cylinder 25, of the tool cylinder 26 and of the plug 50 allows the constitution of three hydraulic chambers for controlling the damping cylinder 25: a lower chamber 51, an intermediate chamber 52 and an upper chamber 53
- the upper part 23 of the machine 21 comprises a striking cylinder (not shown), a hammer 28 secured to a movable knife 29. The latter has a passage opening 30.
- the energy to be absorbed in the damping will then be equal to 10% of the initial energy to which will be added the energy due to the acceleration. There is then a risk of seeing a rebound phenomenon appear, very harmful to obtaining a high cutting rate.
- the height of the damping cylinder 25 is adjusted by means of the adjustment wheel 49, located on the block 24. This wheel allows the height of the needle 48 to be adjusted, by means of a pulley-belt assembly (not shown). ).
- the upper 53, intermediate 52 and lower 51 chambers for controlling the damping cylinder 25 are connected to a hydraulic oil supply circuit. When the lower chamber 51 is supplied with oil, the damping cylinder 25 begins to move upwards, until the oil reaches the upper part of the needle 38.
- the lower chamber 51 is re-supplied, which has the consequence of returning it to its high position at the start of the cycle. Furthermore, when the upper and intermediate hydraulic chambers 53 and 52 for controlling the damping cylinder 25 are supplied with oil, the lower 47 and upper chambers 46 for controlling the tool cylinder 26 are also supplied.
- the upper chamber 46 for controlling the tool cylinder 26 communicates with the upper chamber 53 for controlling the damping cylinder 25 thanks to the presence of the two orifices 42 and 43 located in the middle part of the damping cylinder 25
- the lower chamber 47 for controlling the tool cylinder 26 communicates with the intermediate chamber 52 of the damping cylinder 25 thanks to the presence of the two orifices 44 and 45, located in the lower part of the damping cylinder 25
- the pressure in the control chambers of the tool cylinder is therefore equal to the hydraulic supply pressure.
- the pressure in the control chambers of the tool cylinder 26 is equal to the hydraulic supply pressure.
- the tool cylinder 26 is then in the high position, against the movable knife 29, and as shown in FIG.
- the damping device allows precise adjustment of the damping height as a function of the diameter of the bar to be cut, in order to optimize the energy necessary for adiabatic cutting.
- the use of a damping cylinder allows the reduction of the volume of the block, because it does not play the role of an anvil.
- the tool cylinder meanwhile, undergoes no effort during cutting, since it is retracted inside the damping cylinder during striking.
- its positioning does not depend on the diameter of the bar to be cut, which saves considerable time when changing tools.
- the absence of a remote tool lifting system on the machine block also saves time when changing tools.
- the combination of these two devices makes it possible both to achieve high production rates, but also to guarantee a long service life for each element.
- the damping device according to the invention is in no way limited to use in an adiabatic cutting machine and can be used in any machine tool where one must absorb a surplus of energy not consumed by the application. We can thus cite presses or pestles, for example.
- the design of the tool cylinder, located inside a damper cylinder can be applied to any system requiring rapid replacement of a tool to its initial position.
- compressed air instead of a hydraulic liquid, in order to ensure the different movements of the damping cylinders and of the tools.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Shearing Machines (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04816379A EP1720679A1 (fr) | 2004-02-27 | 2004-12-14 | Dispositif d'amortissement pour machine-outil, machine et procede de decoupe adiabatique a tres haute cadence |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0401974 | 2004-02-27 | ||
FR0401974A FR2866823B1 (fr) | 2004-02-27 | 2004-02-27 | Dispositif d'amortissement pour machine-outil, machine et procede de decoupe adiabatique a tres haute cadence |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005092549A1 true WO2005092549A1 (fr) | 2005-10-06 |
Family
ID=34834081
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2004/003207 WO2005092549A1 (fr) | 2004-02-27 | 2004-12-14 | Dispositif d’amortissement pour machine-outil, machine et procede de decoupe adiabatique a tres haute cadence |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1720679A1 (fr) |
FR (1) | FR2866823B1 (fr) |
WO (1) | WO2005092549A1 (fr) |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0833714A1 (fr) * | 1995-06-21 | 1998-04-08 | Hydropulsor Ab | Machine a impacts |
WO2000032339A1 (fr) * | 1998-11-18 | 2000-06-08 | Hydropulsor Ab | Procede et dispositif se rapportant a un effet de choc sur un objet en mouvement |
WO2001028723A1 (fr) * | 1999-10-19 | 2001-04-26 | Hydropulsor Ab | Agencement de presse a estamper et procede |
WO2002094488A1 (fr) * | 2001-05-22 | 2002-11-28 | Aahs Ulf | Procede et appareil de decoupe de profils creux a grande vitesse |
WO2003086690A1 (fr) * | 2002-04-08 | 2003-10-23 | Morphic Technologies Aktiebolag (Publ) | Dispositif d'usinage a grande vitesse |
US6764644B2 (en) * | 1998-02-18 | 2004-07-20 | Hydropulsor Ab | Method of using an impact machine |
-
2004
- 2004-02-27 FR FR0401974A patent/FR2866823B1/fr not_active Expired - Fee Related
- 2004-12-14 EP EP04816379A patent/EP1720679A1/fr not_active Withdrawn
- 2004-12-14 WO PCT/FR2004/003207 patent/WO2005092549A1/fr not_active Application Discontinuation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0833714A1 (fr) * | 1995-06-21 | 1998-04-08 | Hydropulsor Ab | Machine a impacts |
US6764644B2 (en) * | 1998-02-18 | 2004-07-20 | Hydropulsor Ab | Method of using an impact machine |
WO2000032339A1 (fr) * | 1998-11-18 | 2000-06-08 | Hydropulsor Ab | Procede et dispositif se rapportant a un effet de choc sur un objet en mouvement |
WO2001028723A1 (fr) * | 1999-10-19 | 2001-04-26 | Hydropulsor Ab | Agencement de presse a estamper et procede |
WO2002094488A1 (fr) * | 2001-05-22 | 2002-11-28 | Aahs Ulf | Procede et appareil de decoupe de profils creux a grande vitesse |
WO2003086690A1 (fr) * | 2002-04-08 | 2003-10-23 | Morphic Technologies Aktiebolag (Publ) | Dispositif d'usinage a grande vitesse |
Also Published As
Publication number | Publication date |
---|---|
FR2866823A1 (fr) | 2005-09-02 |
FR2866823B1 (fr) | 2007-05-04 |
EP1720679A1 (fr) | 2006-11-15 |
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