WO2012006751A1 - Procédé et dispositif pour cisailler un matériau en barre - Google Patents

Procédé et dispositif pour cisailler un matériau en barre Download PDF

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Publication number
WO2012006751A1
WO2012006751A1 PCT/CH2011/000160 CH2011000160W WO2012006751A1 WO 2012006751 A1 WO2012006751 A1 WO 2012006751A1 CH 2011000160 W CH2011000160 W CH 2011000160W WO 2012006751 A1 WO2012006751 A1 WO 2012006751A1
Authority
WO
WIPO (PCT)
Prior art keywords
end portion
shearing
rod material
blade
compressive force
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CH2011/000160
Other languages
German (de)
English (en)
Inventor
Andreas Matt
Mihai Vulcan
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hatebur Umformmaschinen AG
Original Assignee
Hatebur Umformmaschinen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hatebur Umformmaschinen AG filed Critical Hatebur Umformmaschinen AG
Publication of WO2012006751A1 publication Critical patent/WO2012006751A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • B23D33/00—Accessories for shearing machines or shearing devices
    • B23D33/10—Stops for positioning work

Definitions

  • the invention relates to a method for shearing off an end section of a rod material according to the preamble of independent claim 1 and to an apparatus for carrying out the method according to the preamble of independent claim 8.
  • Shearing methods and corresponding devices of the generic type are generally known and are used, for example, in the production of molded parts from metallic materials.
  • a metallic rod material is usually inserted between a fixed fixed blade and a relatively movable blade cutter, with a cutaway end portion of the rod material projecting longitudinally beyond the shear plane defined by the fixed blade and the blade.
  • the section knife is then guided transversely to the bar material against the fixed blade while the
  • the invention is therefore based on the object to improve a method of the type mentioned in terms of the quality of the section. More specifically, cracking and other artifacts should be avoided. In addition, no burrs or other disturbing deformations should also occur at the separation points of the (metallic) bar material and the sheared end section. This object is achieved by the method according to the invention and the
  • rod material as used herein is meant any material having a pronounced longitudinal extent and any cross-section which is constant over the length of the extension, in particular metallic rods, rods and wires of any dimensions fall within this definition. Circular cross-sections are the rule but the invention is not so limited.
  • end portion is meant both an unprocessed and a machined, for example, reshaped portion at the end of the rod material.
  • the essence of the invention consists in the following: In a method for
  • Section knife theandscherende end portion is brought during the shearing process the front side in contact with a longitudinal stop and acted on the longitudinal stop with a compressive force in the longitudinal direction of the rod material.
  • the compressive force is preferably chosen so that caused by them
  • Compressive stress in the end section compensates for the shear and tensile stresses occurring during the shearing process.
  • the application of the compressive force to the end portion begins shortly after the cutting blade engages the bar stock and ends shortly before or immediately after the end portion is completely sheared. It is particularly advantageous if the loading of the end section with the pressure force after 0.2-20%, preferably 0.2-10%, more preferably 0.5-5%, of the shear path begins. Furthermore, it is advantageous if the loading of the end section with the pressure force ends at 85-100%, preferably 90-100%, of the shearing path. Under shear is to be understood as the distance of the section blade from contact with the rod material to the complete shearing of the end portion. The shear path corresponds to the cross-sectional dimension of the rod material in the direction of the shearing movement.
  • the rod material is additionally secured by a separate clamping device against displacement in the longitudinal direction.
  • the compressive force acting on the end portion of the rod material is preferably timed or depending on the shear path of the movable
  • Section knife regulated so that it initially rises as steep as possible to a maximum and then slightly decreases, until it is then degraded percentage as soon as possible completely. It is particularly advantageous if the
  • the compressive force is controlled so that the surface pressure caused by it in the shear plane remains approximately constant over the greater part of the shearing process.
  • the surface pressure corresponds to the compressive force divided by the shear area (still to be sheared cross-sectional area of the rod material).
  • the compressive force is chosen so high that the surface pressure is at least about half of the flow stress. The latter is known to depend on material, temperature, rate of deformation, degree of deformation, etc.
  • Flow stress can, for example, in the hot working in the range of 50-100 MPa lie or even higher values of eg 500 MPa reach, especially in cold forming.
  • the structure and at the end of the percentage rapid reduction of the pressure force done very quickly, if possible within 0-4 ms, preferably 1-2 ms.
  • the application of the compressive force is preferably still in the phase of plastic deformation of the rod material and before the shear force has reached its maximum value.
  • the pressure force is advantageously generated by acting on the longitudinal stop hydraulic means. According to a preferred, in particular for
  • the pressure force is generated by a force acting on the longitudinal stop hydraulic shock wave
  • a device suitable for carrying out the method according to the invention comprises a fixed fixed blade and a transversely to the longitudinal direction of the
  • Rod material against the fixed blade movably driven section blade a longitudinal stop for ahomzusendenenden end portion of the rod material and pressurizing means for applying the end portion during the shearing process over the longitudinal stop with a compressive force in the longitudinal direction of the rod material.
  • the pressurization means are adapted to apply the compressive force to the end portion for a limited time window, which time window is in the range of 0.2-20%, preferably 0.2-10%, more preferably 0.5-5%. , that of the mobile
  • Section knife begins from contact with the rod material and ends in the range of 85-100%, preferably 90-100%, of the shear path.
  • Fig. 1 - a longitudinal section through the most essential parts of a
  • FIG. 2 shows the device parts of FIG. 1 in a perspective view
  • FIG. 3 is an enlarged detail view of part of the device of FIG.
  • FIG. 4-6 each a sectional view analogous to FIG. 3, but with different
  • Fig. 12 - a diagram of a first variant of a hydraulic arrangement
  • Fig. 13-14 two sketches of a second variant of a hydraulic system
  • Fig. 15 - a pressure-time diagram
  • Fig. 16-17 two diagrams for explaining the course of typical procedure
  • the devices illustrated in the drawings essentially comprise a locally fixed fixed blade 10, a clamping device 20, a movable
  • the fixed blade 10 is approximately semicircular in cross-section, as well as the clamping device 20.
  • the fixed blade 10 and the clamping device 20 form between them a channel through which a metallic rod material R in the longitudinal direction A as far as and performed is until the front end of the rod material R comes into contact with the longitudinal stop 50 with its front side.
  • the fixed blade 10 and the movable section blade 30 are arranged slightly offset in the longitudinal direction and define a shear plane S between them.
  • the shear plane S is normally perpendicular to the longitudinal direction A of the
  • Rod material R is sheared off.
  • the movable section blade 30 is driven by known per se, symbolized by an arrow 35 in the drawing drive means.
  • the shearing movement is towards the fixed blade 10.
  • the thereby covered actual shear path is defined as the distance of the section blade 30 between the engagement of the same in the rod material R and the complete shearing of the end portion R E of the rod material R, thus corresponds substantially to the transverse dimension of the rod material R in the direction of movement of the section blade 30th
  • feed means are provided, for example, include an attacking on the circumference of the rod material R, openable and closable intake assembly, the longitudinal direction and is mobile driven drivable.
  • Shearing process are held in the longitudinal direction.
  • the clamping device 20 is pressed against the rod material R to do so.
  • the necessary, known per se drive means are symbolized in the drawing by an arrow 25.
  • Figures 7, 8 and 8a show the movable section blade 30 and the
  • the movable section blade 30 comprises a main body 31, on whose substantially semi-cylindrical inner side a cutting support 32 made of a particularly hard or hardened material is attached.
  • the substantially semicircular, the fixed blade facing edge of the cutting support 32 forms a shear lip 32 a.
  • the fixed blade comprises a base body 11, on whose substantially semi-cylindrical inner side a cutting support 12 made of a particularly hard or hardened material is attached.
  • Cutting pad 12 forms a shear lip 12a.
  • FIG. 8a shows this in an enlarged detail.
  • the clamping device 20 consists of a substantially semi-cylindrical clamping jaw 21 with a conically shaped inner section 21a, which facilitates the insertion of the rod material R.
  • FIG. 4 shows, instead of the combination of open fixed blade 10 and clamping device 20, a closed fixed blade 10 'can also be provided.
  • the closed fixed blade 10 ' comprises a base body 11', on whose substantially cylindrical inner side a cutting support 12 'made of a particularly hard or hardened material is attached.
  • the substantially circular, the movable section blade facing edge of the cutting pad 12 ' forms a shear lip 12b.
  • the movable section blade may be formed as a closed circular blade.
  • FIG. 10 shows an axial section through a closed section blade 30 '. This comprises a substantially annular base body 31 ', on whose substantially cylindrical inner side a cutting support 32' made of a particularly hard or hardened material is attached. The substantially circular, the fixed blade facing edge of the cutting support 32 'forms a shear lip 32b.
  • Figures 5 and 6 show two further embodiments of the
  • the longitudinal stop 50 has an anvil-like shape
  • the rod material R or its end portion R E are during the Abschervorgangs the front side in contact with the front or end face 51a of the stopper head 51.
  • the front or end face 51a is perpendicular or preferably at an angle of 90 ° -88 ° inclined to Longitudinal direction (axis) of the bar stock R.
  • the stop shaft 52 is screwed to a coaxial piston rod 61 and thus kinematically coupled in the longitudinal direction.
  • the piston rod 61 is in turn kinematically connected to a stop piston 62, in particular integrally formed therewith.
  • the stop piston 62 and its piston rod 61 are axially movably mounted (slightly) in a piston chamber 63 of a fixedly arranged piston housing 60, wherein the axial movability is limited by a spacer sleeve 64 enclosing the piston rod 61.
  • the maximum stroke of the Stop piston 62 and thus also the longitudinal stop 50 is about 1 mm. It can best be seen from FIG. 9 and designated there by h.
  • In the piston chamber 63 open in the axial or longitudinal direction in front of and behind the piston 62nd
  • connection lines 65 and 66 for a hydraulic medium. Via the connection line 65, the stop piston 62 and thus indirectly also the longitudinal stop 50 in the direction of the end portion R E of the rod material R back to be pressurized, via the connecting line 66 in the opposite direction.
  • pressurization of the longitudinal stop 50 can alternatively be done pneumatically or by mechanical means.
  • the movable section blade 30 is moved transversely to the longitudinal direction of the rod material R in the direction of the fixed blade 10. As soon as the movable section blade 30 engages with the rod material R, it is pressed against the fixed blade 10, so that the fixed blade 10 also comes into engagement with the rod material R with its shear lip 12a. Immediately or with a small delay, the
  • Longitudinal stop 50 is pressed over the stop piston 62 against the end portion R E of the rod material R, so that the end portion R E is acted upon in its longitudinal direction with a compressive force F D.
  • the shear lip 12a of the fixed blade 10 is at this time already in engagement with the rod material R and supports this, so that it can not move back under the pressure force F D. This support is supported in the longitudinal direction, if any, by the
  • the movable section blade 30 is now further moved transversely to the rod material R with applied pressure force F D until the end portion R E is completely sheared off. Just before or at the latest at the end of the shearing path (when the end portion R E is completely sheared off), the loading of the end portion R E is terminated with the pressing force F D.
  • Clamping device 20 are moved back to their respective starting positions. This may start a new process cycle.
  • the compressive force FD acting on the end section R E of the bar stock R is advantageously not constant throughout the shear path, but has
  • the shear force counteracting the movable section blade 30 has a similar course, which is represented by the curve fs in FIGS. 16 and 17, respectively. It is important that the maxima of the two curves occur as close as possible to each other, but the pressure force FD has reached its maximum before the shear force is highest. In the example illustrated in FIGS. 16 and 17, the maximum shear force is about 54 kN (right ordinate axis, unit kN). As FIGS. 16 and 17 further illustrate in each case on the basis of the curve sf, the shearing surface decreases as the shearing movement of the section blade 30 progresses
  • the compressive force FD applied to the end portion RE of the rod material R is timed such that the surface pressure caused by it in the shear plane is approximately constant over the greatest part of the shear path (for example in the range of 50 MPa). It is also important that the compressive force is chosen so that the surface pressure generated by them is at least half of the flow stress. For example, in FIGS. 16 and 17, a typical course of the
  • the pressing of the end portion RE of the rod material R with the (timed) compressive force F D begins, as already mentioned, as soon as the shear lip of the fixed blade 10 has sufficiently engaged with the rod material R to support it against displacement, even before Occurrence of maximum shear force. In practice, this is about 0.2-20% of the shear, preferably about 0.2-10% and more preferably about 0.5-5% of the shear stroke.
  • the pressure buildup must be relatively fast and still during the phase of plastic deformation of the rod material R take place.
  • the application of the pressure force F D is ideally terminated when the shearing has been completed. For practical reasons, however, it takes place a little earlier, about 85%, preferably about 90%, of the Scherwegs.
  • the pressure build-up and the percentage fast pressure reduction at the end should advantageously take place within a time span of 0-4 ms, preferably 1-2 ms.
  • the pressurization of the longitudinal stop 50 indirectly via the stop piston 62 in the piston housing 60 may preferably be implemented by a hydraulic arrangement.
  • a first variant of such a hydraulic arrangement is shown schematically in FIG.
  • the hydraulic arrangement comprises a first hydraulic pressure accumulator 71, a second hydraulic accumulator 72, a hydraulic tank 73, two controllable valves 74 and 75 and a continuously controllable servo valve 76.
  • a control 77 is provided for actuating the valves 74 and 75 and controlling the servo valve 76.
  • the first hydraulic accumulator 71 is communicatively connected via the servo valve 76 with the connecting line 65 in the piston housing 60.
  • the second hydraulic accumulator 72 is connected via the valve 75 to the connecting line 66 in the piston housing.
  • the hydraulic tank 73 is communicatively connected via the valve 74 to the connection line 65.
  • Hydraulic medium-carrying lines are not designated in the figure 9.
  • the maximum stroke h is limited by the spacer sleeve 64.
  • the controlled temporal pressure buildup in the piston housing is done by appropriate control of
  • Servo valve 76 via the controller 77 in time allocation to the movement of Section meter 30.
  • the controller 77 is conveniently part of
  • the servo valve is closed and the valve 74 is opened to the hydraulic tank 73.
  • the valve 75 is opened so that hydraulic fluid from the second hydraulic accumulator 72 flow into the piston housing 60 and can act on the piston from the other side.
  • the second hydraulic accumulator 72 and the associated valve 75 may be provided for returning the stop piston 62 and a suitably arranged spring assembly or the like. Possibly, the provision of the
  • Stop piston 62 can also be realized by the feed movement of the rod material R.
  • Rod material in the range of typically 30-50 ms or 20-100 mm.
  • the volume of the hydraulic medium in the piston chamber 63 must be kept as small as possible in order to build up the pressure as quickly as possible.
  • the servo valve 76 must be arranged as close as possible to the piston housing 60.
  • the hydraulic accumulator 71 must be designed so that it can cover the suddenly occurring volume flow during pressure build-up.
  • Hydraulic pressure accumulator determines the amount of pressure overlay in the shearing process.
  • a process control in the sense of a constant pressure superposition via the shear path is difficult to realize because of the very short process times, but would be desirable.
  • the connecting line to the hydraulic tank 73 must be designed so that it ensures the fastest possible pressure reduction (0-4 ms, preferably 1-2 ms).
  • the very narrow time window of the pressure superposition during the shearing process can change both its length and its position on the time axis during operation (depending on the oil temperature, valve temperature, wear of the
  • the pressure profile in particular the window of pressure build-up and pressure reduction, should be continuously monitored by the controller 77 and, if necessary, preferably automatically corrected.
  • FIGS. 13-15 A second variant of the hydraulic arrangement is schematically illustrated in FIGS. 13-15, which is especially suitable for very short shearing times or relatively small cross-sectional dimensions of the bar material to be shaved in the range of typically ⁇ 10 ms or ⁇ 20 mm.
  • the stop piston 67 is slidably mounted in a main line 81 and is held by a spring assembly 68 in a (left in the drawing) starting position ( Figure 13).
  • a spring assembly 68 in a (left in the drawing) starting position ( Figure 13).
  • the other end of the main conduit 81 is closed by a plunger 82 slidably disposed in the main conduit.
  • the main line 81 is communicatively connected to a hydraulic pressure accumulator 84 via a supply line 83 and completely filled with hydraulic medium.
  • the hydraulic pressure accumulator 84 is under a pressure p 0 of eg 5 bar, so that the pressure in the main line 81 a Basic value p 0 has.
  • the restoring force of the spring assembly 68 is such that it resists the pressure p 0 , the stop piston 67 thus remains in its initial position.
  • the plunger 82 and the stop piston 67 are above a
  • Axially upstream of and abutting against the ram 82 is a rotatably driven cam 85 whose radius varies over its circumference from a minimum value r 0 to a maximum value n.
  • the cam disk 85 is in one
  • Characterized a (pressure) shock wave is generated in the main line 81, which propagates in the main line 81 at the speed of sound and the stop piston 67 acts. This transmits the pressure exerted on it on the longitudinal stop 50, which thus acts on thesignscherenden end portion of the rod material.
  • the course and the size (amplitude) of the pressure wave thus generated depends on the rotational speed co, the radius profile and the radius difference ri-r 0 of the cam disk 85.
  • the cam 85 is preferably shaped so that its radius is constant over most of its circumference, so that the
  • FIG. 15 shows a typical course of such a shock wave as a function of time t.
  • the pressure p acting on the stop piston 67 in the main line 81 rises rapidly from the mentioned initial value p 0 to a maximum value p ! (For example, in the order of 100 bar) and then drops just as quickly back to the initial value p 0 .
  • the distance LI between the plunger 82 and the stop piston 67 that is, the length of the hydraulic medium column between the two pistons 82 and 67, must be in a certain proportion to the wavelength of the generated shock wave to avoid resonance effects and pressure overlays which cause the main line to burst could. Such resonance effects can e.g. be avoided by not shown in the drawing wave damping devices in the main line.
  • the diameter of the supply line 83 to / from the hydraulic accumulator 84 is very small compared to the diameter of the main line 81 and its length L 2 must not fall below a certain critical mass. This dimension is also dependent on the wavelength of the shock wave. The dimensioning of the supply line is known in the art and therefore needs no further explanation.
  • the purpose of the container is to supply the main line with a constant pressure (e.g., 5 bar).
  • a constant pressure e.g., 5 bar
  • the shock wave has a much higher pressure (e.g., 100 bar).
  • the constant pressure must not move the longitudinal stop 50 from its position held by the spring assembly 68 position. Only by the effect of the shock wave of this is a defined force on theußscherenden end of the
  • a sudden movement of the longitudinal stop causes, unlike the first variant no pressure drop.
  • the energy contained in the shock wave is transported at the speed of sound through the main line without losses to the stop piston.
  • the losses due to friction are very low due to the relatively short line lengths and can be neglected.
  • a coupling to the hydraulic system of the entire device is not necessary, the system can operate independently.
  • the time of the pressure build-up and the pressure reduction can be determined by mechanical components, in particular cam-controlled. This time is independent of the cycle speed (speed) of the overall device, which is a very important factor.
  • the shearing method according to the invention and the corresponding device according to the invention are lowered in connection with forming processes over the entire temperature range from hot forming to forming
  • Temperature can be used up to cold forming.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shearing Machines (AREA)

Abstract

Pour cisailler un segment d'extrémité (RE) d'un matériau en barre (R), au moyen d'une lame de cisaillage (30) pouvant se déplacer contre une lame fixe (10) transversalement au sens longitudinal du matériau en barre, le segment d'extrémité (RE) à cisailler est appliqué, côté face frontale, contre une butée longitudinale (50) et soumis à une force de compression dans le sens longitudinal du matériau en barre (R) par l'intermédiaire de la butée longitudinale (50). Sous l'effet de la superposition d'un état de compression, provoquée par l'application de la force de compression, dans le segment d'extrémité à cisailler pendant le cisaillage, la qualité du cisaillage est considérablement améliorée notamment dans le cas d'un matériau en barre métallique.
PCT/CH2011/000160 2010-07-14 2011-07-08 Procédé et dispositif pour cisailler un matériau en barre Ceased WO2012006751A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1142/10 2010-07-14
CH01142/10A CH702984B1 (de) 2010-07-14 2010-07-14 Verfahren und Vorrichtung zum Abscheren von Stangenmaterial.

Publications (1)

Publication Number Publication Date
WO2012006751A1 true WO2012006751A1 (fr) 2012-01-19

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PCT/CH2011/000160 Ceased WO2012006751A1 (fr) 2010-07-14 2011-07-08 Procédé et dispositif pour cisailler un matériau en barre

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WO (1) WO2012006751A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105499698A (zh) * 2015-11-25 2016-04-20 安徽红桥金属制造有限公司 一种剪板机后置定位装置
CN109414757A (zh) * 2016-07-19 2019-03-01 哈特伯金属成型机股份公司 用于剪切杆状材料的方法及装置
CN111958033A (zh) * 2020-08-14 2020-11-20 郑州高端装备与信息产业技术研究院有限公司 一种棒料剪切机

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH422692A (de) * 1964-07-01 1966-10-31 Nikex Nehezipari Kulkere Verfahren und Vorrichtung zur Zerstückelung von Metallstangen
GB1349905A (en) * 1971-06-30 1974-04-10 Warnke Umformtech Veb K Method and apparatus for the production of disc-shaped workpieces
US3867857A (en) * 1973-11-30 1975-02-25 Tokyu Car Corp Material cutting device
WO1986003440A1 (fr) * 1984-12-07 1986-06-19 Ludwig Balint Procede et dispositf pour separer des segments de tubes

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH422692A (de) * 1964-07-01 1966-10-31 Nikex Nehezipari Kulkere Verfahren und Vorrichtung zur Zerstückelung von Metallstangen
GB1349905A (en) * 1971-06-30 1974-04-10 Warnke Umformtech Veb K Method and apparatus for the production of disc-shaped workpieces
US3867857A (en) * 1973-11-30 1975-02-25 Tokyu Car Corp Material cutting device
WO1986003440A1 (fr) * 1984-12-07 1986-06-19 Ludwig Balint Procede et dispositf pour separer des segments de tubes

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105499698A (zh) * 2015-11-25 2016-04-20 安徽红桥金属制造有限公司 一种剪板机后置定位装置
CN109414757A (zh) * 2016-07-19 2019-03-01 哈特伯金属成型机股份公司 用于剪切杆状材料的方法及装置
KR20190031476A (ko) * 2016-07-19 2019-03-26 하테부르 움포름마쉬넨 아크티엔게젤샤프트 로드 재료를 전단하기 위한 방법 및 장치
US20190291190A1 (en) * 2016-07-19 2019-09-26 Hatebur Umformmaschinen Ag Method and Device for Shearing Rod Material
US11040405B2 (en) 2016-07-19 2021-06-22 Hatebur Umformmaschinen Ag Method and device for shearing rod material
KR102412221B1 (ko) * 2016-07-19 2022-06-23 하테부르 움포름마쉬넨 아크티엔게젤샤프트 로드 재료를 전단하기 위한 방법 및 장치
CN111958033A (zh) * 2020-08-14 2020-11-20 郑州高端装备与信息产业技术研究院有限公司 一种棒料剪切机

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