US20020083805A1 - Metal cutting apparatus and method for damping feed-back vibrations generated thereby - Google Patents

Metal cutting apparatus and method for damping feed-back vibrations generated thereby Download PDF

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US20020083805A1
US20020083805A1 US10/006,713 US671301A US2002083805A1 US 20020083805 A1 US20020083805 A1 US 20020083805A1 US 671301 A US671301 A US 671301A US 2002083805 A1 US2002083805 A1 US 2002083805A1
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Prior art keywords
oscillatory motion
damping force
damping
tool
phase
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US10/006,713
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English (en)
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Mikael Lundblad
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Sandvik AB
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Assigned to SANDVIK AKTIEBOLAG reassignment SANDVIK AKTIEBOLAG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LUNDBLAD, MIKAEL
Publication of US20020083805A1 publication Critical patent/US20020083805A1/en
Priority to US10/851,099 priority Critical patent/US20040240955A1/en
Priority to US11/178,335 priority patent/US7647853B2/en
Abandoned legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q17/00—Arrangements for observing, indicating or measuring on machine tools
    • B23Q17/09—Arrangements for observing, indicating or measuring on machine tools for indicating or measuring cutting pressure or for determining cutting-tool condition, e.g. cutting ability, load on tool
    • B23Q17/0952—Arrangements for observing, indicating or measuring on machine tools for indicating or measuring cutting pressure or for determining cutting-tool condition, e.g. cutting ability, load on tool during machining
    • B23Q17/0971—Arrangements for observing, indicating or measuring on machine tools for indicating or measuring cutting pressure or for determining cutting-tool condition, e.g. cutting ability, load on tool during machining by measuring mechanical vibrations of parts of the machine
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q11/00—Accessories fitted to machine tools for keeping tools or parts of the machine in good working condition or for cooling work; Safety devices specially combined with or arranged in, or specially adapted for use in connection with, machine tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B27/00—Tools for turning or boring machines; Tools of a similar kind in general; Accessories therefor
    • B23B27/002—Tools for turning or boring machines; Tools of a similar kind in general; Accessories therefor with vibration damping means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B29/00—Holders for non-rotary cutting tools; Boring bars or boring heads; Accessories for tool holders
    • B23B29/02—Boring bars
    • B23B29/022—Boring bars with vibration reducing means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23C—MILLING
    • B23C5/00—Milling-cutters
    • B23C5/003—Milling-cutters with vibration suppressing means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q11/00—Accessories fitted to machine tools for keeping tools or parts of the machine in good working condition or for cooling work; Safety devices specially combined with or arranged in, or specially adapted for use in connection with, machine tools
    • B23Q11/0032—Arrangements for preventing or isolating vibrations in parts of the machine
    • B23Q11/0039—Arrangements for preventing or isolating vibrations in parts of the machine by changing the natural frequency of the system or by continuously changing the frequency of the force which causes the vibration
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q17/00—Arrangements for observing, indicating or measuring on machine tools
    • B23Q17/09—Arrangements for observing, indicating or measuring on machine tools for indicating or measuring cutting pressure or for determining cutting-tool condition, e.g. cutting ability, load on tool
    • B23Q17/0952—Arrangements for observing, indicating or measuring on machine tools for indicating or measuring cutting pressure or for determining cutting-tool condition, e.g. cutting ability, load on tool during machining
    • B23Q17/0971—Arrangements for observing, indicating or measuring on machine tools for indicating or measuring cutting pressure or for determining cutting-tool condition, e.g. cutting ability, load on tool during machining by measuring mechanical vibrations of parts of the machine
    • B23Q17/0976—Detection or control of chatter
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/005—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion using electro- or magnetostrictive actuation means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2250/00—Compensating adverse effects during turning, boring or drilling
    • B23B2250/16—Damping of vibrations
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2260/00—Details of constructional elements
    • B23B2260/108—Piezoelectric elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2260/00—Details of constructional elements
    • B23B2260/128—Sensors
    • B23B2260/1285—Vibration sensors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23C—MILLING
    • B23C2250/00—Compensating adverse effects during milling
    • B23C2250/16—Damping vibrations
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S82/00—Turning
    • Y10S82/904—Vibrating method or tool
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T408/00—Cutting by use of rotating axially moving tool
    • Y10T408/76—Tool-carrier with vibration-damping means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T409/00—Gear cutting, milling, or planing
    • Y10T409/10—Gear cutting
    • Y10T409/101431—Gear tooth shape generating
    • Y10T409/105883—Using rotary cutter
    • Y10T409/10636—On reciprocating carriage
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T409/00—Gear cutting, milling, or planing
    • Y10T409/30—Milling
    • Y10T409/304312—Milling with means to dampen vibration
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T82/00—Turning
    • Y10T82/10—Process of turning
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T82/00—Turning
    • Y10T82/25—Lathe
    • Y10T82/2593—Work rest
    • Y10T82/2595—Work rest with noise or vibration dampener

Definitions

  • the present invention relates to the damping of feed-back vibrations generated by a metal cutting tool during the chip-removing machining of metal.
  • the invention relates to a method of such damping which involves:
  • the invention also relates to a vibration damper and a mechanical apparatus for performing the method.
  • Regenerative vibration is so named because of the closed-loop nature of the dynamic cutting process.
  • Each tool pass leaves disturbances in the form of undulations on the workpiece due to the vibrations of the tool and workpiece, and those disturbances produce mechanical feedback vibrations in subsequent passes of the tool.
  • regenerative vibration can be described as a small transient wave that is machined into the workpiece. That small wave will become the driving force, causing the system to vibrate increasingly again in subsequent passes, i.e., the vibrations from one pass are amplified by those of the next pass. Unstable conditions can cause a small wavelet to develop and increase around the circumference, giving non-acceptable machining results.
  • Damping of vibration in tools for chip removing machining has previously been achieved by pure mechanical damping, i.e., the tool shaft being formed with a cavity in which is disposed a counter-oscillating mass of, for instance, heavy metal.
  • the weight and location of the mass is tuned in order to provide damping of oscillations within a certain range of frequencies.
  • the cavity is then filled with a viscous liquid, e.g. oil, and is plugged.
  • this technique works passably only in those cases where the overhang of the shaft from a fastening device is approx. 4-10 times longer than the diameter thereof.
  • the pure mechanical damping has an obvious disadvantage in that the range of frequencies within which the damping acts, is very limited. An additional inconvenience consists of the strength-wise weakening of the shaft resulting from the presence of that cavity.
  • a piezo element consists of a material, most often of a ceramic type, which when compressed or elongated in a certain direction (the direction of polarization), generates an electric field in the same direction.
  • the piezo element usually has the shape of a rectangular plate having a direction of polarization, which is parallel to the major axis of the plate.
  • Electric resistive components included in the control module will generate heat according to known physics. In doing so, vibration energy is converted to thermal energy, whereby a passively damping, but not damping effect on the vibrations is obtained.
  • shunts selected frequencies can be brought to be damped with particular efficiency.
  • such frequencies are the so-called “own-frequencies” of the exposed “own-modes” of the object, which are those preferably being excited.
  • a piezo element may be compressed or elongated by an electric voltage being applied over the piezo element, during which the same may be used as a control or operating device (actuator).
  • actuator an electric voltage being applied over the piezo element
  • This can be used for active vibration control by selecting the polarity of the applied electric voltage in such a way that the mechanical stress of the operating device acts in the opposite direction, as an external, mechanical stress.
  • the emergence of vibrations is suppressed by the fact that another kinetic energy, for instance rotation energy, is prevented from being converted to vibration energy.
  • the synchronization of the applied electric voltage relative to the external mechanical stress takes place by supplying a feedback signal from a deformation sensitive sensor to a control means in the form of a logical control circuit, e.g. a programmable micro-processor.
  • the processor processes the signal to control the electric voltage applied over the operating device.
  • the control function i.e. the relation between the input signal from the sensor and the output voltage, may, in that connection, be made very complex. For instance, a self-learning system for adaptation to varying conditions is feasible.
  • the sensor may consist of a separate, deformation sensitive device, e.g. a second piezo element, or be common with the operating device.
  • This type of vibration damper is not suitable for force-induced vibrations, but only for regenerative, i.e. feed-back vibrations, which, e.g., arise in a tool during mechanical machining when a small disturbance gives a mechanical feed-back in the tool.
  • feed-back vibrations e.g., arise in a tool during mechanical machining when a small disturbance gives a mechanical feed-back in the tool.
  • Such a mechanical feed-back may cause an increasing oscillatory motion, and thereby an undesired uneven surface of the machined blank and reduced service life of the tool.
  • extenders are used, which frequently causes bending vibrations which not only lead to impaired dimensional accuracy and irregularities in the workpiece, but also to reduced service life of the tool and the cutting inserts or machining elements thereof.
  • the purpose of the present invention is to improve the control of a vibration-damping device for cutting tools having a regenerative oscillatory motion.
  • the control device is arranged to impose the damping force out of phase by 60°-120° alternatively 240°-300° in relation to the oscillatory motion.
  • the control device is arranged to impose the damping force out of phase by 70°-110° alternatively 250°-290° in relation to the oscillatory motion.
  • the control device is arranged to impose the damping force out of phase by 80°-100° alternatively 260°-280° in relation to the oscillatory motion. In this way, a faster damping of the oscillatory motion is obtained. Best results are achieved when the control device is arranged to impose the damping force out of phase by 90° alternatively 270° in relation to the oscillatory motion.
  • a co-directed force should be given when the same is imposed out of phase between 60° and 120° in relation to the oscillatory motion, while a counter directed force should be imposed out of phase between 240° and 300° in relation to the oscillatory motion.
  • control device is arranged to give a damping force in the area of 50-1500 Hz.
  • the vibration-damping device may be a hydraulic or pneumatic cylinder or an electromagnetic device.
  • said mechanical structure comprises a tool for chip removing machining.
  • FIG. 1 is a schematic side view of a long narrow body in the form of a tool shaft during bending, deformation at oscillation (1 st resonance frequency).
  • FIG. 2 is a graph showing the bending torque in the body.
  • FIG. 3 a side view of a cut end portion of the body in connection with a fastening end so as to illustrate the stress in the body during bending deformation proportional to elongation.
  • FIG. 4 is a transparent perspective view of a tool shaft.
  • FIG. 5 is a perspective view of a bar extender for milling tools formed with a circular cross-section.
  • FIGS. 6 - 8 are perspective views of respective tool shafts having a square cross-section and in different alternative embodiments, wherein FIG. 6 shows a piezo element mounted in a countersink of a tool draft; FIG. 7 shows the countersink of FIG. 6 covered by a lid; FIG. 8 shows a piezo element mounted on the outside of the shaft.
  • FIG. 9 is a perspective view of a tool for active vibration damping mounted in a carrier.
  • FIG. 10 is an analogous perspective view of an alternative embodiment for passive vibration damping.
  • FIG. 11 shows schematically the damping of an oscillatory motion by means of a counter force in phase with the oscillation.
  • FIGS. 12 - 13 show schematically the damping of an oscillatory motion according to the invention, wherein FIG. 12 shows the application of a constant-amplitude damping force, whereas FIG. 13 discloses the application of a damping force having a gradually diminishing amplitude.
  • FIG. 1 a long narrow body in the form of a bar or a shaft 1 of a tool is illustrated, which is intended to carry one or more (cutting) inserts of the tool during turning or milling.
  • the body 1 has a fastening end 2 and a free, external end 3 .
  • the body has an external surface 4 , which may be cylindrical or comprise a plurality of plane surfaces if the body has a polygonal, e.g. rectangular cross-section shape.
  • the body 1 may have an arbitrary cross-section shape, however, most commonly circular or rectangular.
  • numeral 5 designates a part in which the body 1 is fastened, the body extending cantilever-like from the fastening part.
  • the body 1 is shown in a state when the same has been deformed in a first self-bending state or “own-mode.”
  • FIG. 2 a graph is shown which illustrates how the bending torque M b in this case varies along the body. As is seen in the graph, a maximum bending moment arises, and thus a maximum axial elongation, at or near the fastening end 2 . The same is valid for all lower modes, which are normally energy-wise dominant during bending vibrations of tools for chip removing machining.
  • FIG. 3 a portion of the body 1 deformed by bending in FIG. 1 is shown in the area of the fastening end.
  • the elongation at bending deformation varies in the cross-direction of the body (the elongation is strongly exaggerated for illustrative reasons) is illustrated.
  • the maximum elongations are obtained at the envelope surface or external surface 4 of the body.
  • FIG. 4 a fundamental design of a bar or a shaft 1 is schematically shown in which two plate-formed, rectangular piezo elements 8 are fastened on opposite, longitudinal plane surfaces 4 of the shaft of rectangular cross-section.
  • the piezo elements 8 are placed in the area near the fastening end 2 of the shaft.
  • the shaft has a machining element in the form of a cutting insert 9 .
  • the piezo elements 8 are positioned in an area where the maximum axial elongation occurs during bending deformation. Although this location is preferred, also other locations are feasible.
  • the piezo elements 8 are oriented with the major faces thereof essentially parallel to the plane surfaces 4 of the bar or shaft 1 and with the major axes essentially parallel to the longitudinal axis of the shaft or bar 1 , at which the piezo elements 8 at bending vibration will be deformed while retaining the rectangular shape.
  • the body 1 consists of a cylindrical bar extender intended for a milling tool.
  • a chip forming machining element 9 in the form of a cutting edge is formed adjacent to a chip pocket 10 at the free end 3 of the bar extender.
  • a piezo element 8 is attached on the envelope surface 4 of the bar extender in an area near the fastening end 2 .
  • the major axis of the piezo element is parallel to the length extension of the bar extender. Consequently, with this orientation, the piezo element 9 acts also here most efficiently for the damping of bending vibration.
  • the shaft of the tool is advantageously formed with a plurality of piezo elements, some of which being oriented with the long sides thereof essentially parallel to the length extension of the shaft, while others are oriented at approximately a 45° angle.
  • one or more piezo elements are provided having different respective orientations.
  • Piezo elements are usually fragile, particularly such of the ceramic type. Therefore, in demanding environments, the same should have some form of protection in order to achieve art acceptable service life.
  • FIGS. 6 - 8 tool shafts having a rectangular cross-section are shown, the piezo element 8 being attached and protected in alternative ways. In all cases, the piezo elements are placed in an area near the fastening part 5 (which part may consist of a conventional clamping unit in which the tool is detachably mounted).
  • the piezo element 8 is mounted in a countersink 11 and advantageously covered by a protection layer, for instance of the epoxy type.
  • the piezo clement is assumed to be mounted in the countersink 11 and covered by a stiff lid 12 .
  • the piezo element 8 is mounted to, e.g. glued on, the outside of the shaft.
  • These alternatives should only be seen as examples, those of which shown in FIGS. 6 and 7 being preferred. It should be understood that the same type of protection for the piezo elements is independent of the cross-section shape of the tool shaft.
  • the piezo elements co-operate with means for electric control or guiding of the same.
  • FIGS. 9 and 10 examples are shown of how the tool 1 has been formed with such control means.
  • the tool is mounted in a carrier 13 .
  • a control means for damping is shown in the form of a control means 14 formed near the fastening end 2 and an electric connection 15 , via which one or more piezo elements 8 are connected to the control module 14 for separate or common control of respective piezo elements.
  • This module 14 comprises at least electric resistive components.
  • the control module 14 also comprises one or more shunts, at which selected frequencies may be damped particularly efficiently.
  • FIG. 9 illustrates a control means for active damping in the form of a free-standing logical control circuit 16 , e.g. a programmable microprocessor, for separate or common control of (via the schematically illustrated electric connection 15 ) voltages applied over the piezo elements 8 .
  • the connection 15 may in this case comprise collector shoes or the like.
  • the piezo elements 8 in the embodiment exemplified in FIG. 10 for active damping simultaneously act as both operating devices and sensors, it is feasible to realise the same two functions by separate operating devices and sensors, wherein the sensors do not need to consist of piezo elements.
  • the depicted locations of the control module 14 and logic control circuit 16 are preferred, other locations are feasible.
  • it is feasible, as in the case of the logic control circuit 16 to arrange the control module 14 freestanding from the tool.
  • the advantage of placing the control module 14 in the vicinity of the fastening end is that the module becomes simple to connect to the piezo elements, whereas the advantage of arranging it at a freestanding position is that it becomes easier to protect the module against harmful mechanical effects.
  • FIG. 11 shows schematically how damping of an undesired oscillatory motion in a mechanical structure generally comes about according to afore-mentioned U.S. Ser. No. 09/913,271. If a damping force 20 is counter-directed to, and in phase with, the oscillatory motion 22 , the motion is quickly dampened. However, this requires a very large accuracy as regards phase correctness. If a phase error arises between the damping force and the oscillatory motion, the counter-directed dampening force will be partly co-directed with the oscillatory motion, which may lead to the oscillatory motion not being quenched to the desired degree.
  • FIG. 12 shows schematically the damping of the oscillatory motion of the mechanical structure according to the invention.
  • the sensor detects the oscillatory motion 22 .
  • the signal is transferred to the control device, which processes the signal and determines the oscillatory motion's phase by defining positive and negative, respectively, zero crossing,
  • the control device also calculates the amplitude and frequency of the oscillation.
  • the control device then sends out a control signal to the vibration damper (actuator), which generates a force 20 ′ counter-directed relative to the tool's velocity 24 .
  • the phase is displaced a quarter of, alternatively three-quarters of, a wavelength in relation to the oscillatory motion.
  • the damping force Since the damping force is applied in counter-direction to the velocity of the oscillatory motion, the damping force will tend to deform the tool in that counter direction. Accordingly, regenerative vibration can be damped without a risk that the damping force will amplify the vibration, e.g., the result of an unbalanced relationship therebetween.
  • the invention thus eliminates a need for a high degree of accuracy between the phases of the damping force frequency and the regenerative vibration frequency.
  • FIG. 13 it is shown how a counter force 20 ′′ directed in the opposite direction to that of the tool's oscillatory motion 22 can be imposed at gradually decreasing oscillation amplitude (in lieu of constant amplitude) to avoid a new generation of vibrations, and is thereby easier to control.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Auxiliary Devices For Machine Tools (AREA)
  • Vibration Prevention Devices (AREA)
  • Automatic Control Of Machine Tools (AREA)
  • Turning (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Machine Tool Sensing Apparatuses (AREA)
  • Cutting Tools, Boring Holders, And Turrets (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
US10/006,713 2000-12-08 2001-12-10 Metal cutting apparatus and method for damping feed-back vibrations generated thereby Abandoned US20020083805A1 (en)

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Application Number Priority Date Filing Date Title
US10/851,099 US20040240955A1 (en) 2000-12-08 2004-05-24 Metal cutting apparatus and method for damping feed-back vibrations generated thereby
US11/178,335 US7647853B2 (en) 2000-12-08 2005-07-12 Metal cutting apparatus and method for damping feed-back vibrations generated thereby

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0004540A SE517878C2 (sv) 2000-12-08 2000-12-08 Förfarande och anordning för vibrationsdämpning av metalliska verktyg för spånavskiljande bearbetning samt verktyg innefattande en dylik anordning
SE0004540-1 2000-12-08

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US10/851,099 Abandoned US20040240955A1 (en) 2000-12-08 2004-05-24 Metal cutting apparatus and method for damping feed-back vibrations generated thereby
US11/178,335 Expired - Fee Related US7647853B2 (en) 2000-12-08 2005-07-12 Metal cutting apparatus and method for damping feed-back vibrations generated thereby

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EP1566481A1 (de) * 2004-02-13 2005-08-24 Voith Paper Patent GmbH Schaberdämpfung
US20060291973A1 (en) * 2005-06-28 2006-12-28 Ingvar Claesson Device and a method for preventing or reducing vibrations in a cutting tool
US20070056414A1 (en) * 2003-10-31 2007-03-15 Martin Saeterbo Arrangement for damping of vibrations and defection in a tool holder
DE102005060779A1 (de) * 2005-12-16 2007-06-21 Eads Deutschland Gmbh Kraftgenerator
US7591209B2 (en) * 2003-11-26 2009-09-22 Sumitomo Electric Hardmetal Corp. Vibration suppressing cutting tool
US20130236254A1 (en) * 2010-11-29 2013-09-12 Techspace Aero S.A. Two-material one-piece cutting tool
EP3241647B1 (de) 2016-05-03 2019-02-06 Soraluce, S.Coop. Werkzeugmaschine mit aktivem dämpfungssystem
US10254104B2 (en) 2015-10-19 2019-04-09 Kennametal Inc Method and apparatus for center height alignment of a boring bar
EP3511112A1 (de) 2018-01-15 2019-07-17 Soraluce, S.Coop. Werkzeugmaschine mit aktiver dämpfung
US10500648B1 (en) * 2018-06-12 2019-12-10 Iscar, Ltd. Tool holder having integrally formed anti-vibration component and cutting tool provided with tool holder
US10744567B2 (en) * 2015-09-10 2020-08-18 Citizen Watch Co., Ltd. Control device for machine tool and machine tool
CN112935295A (zh) * 2021-01-22 2021-06-11 山东大学 一种用于深腔加工的嵌入式阻尼减振车刀杆及方法

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WO2021049429A1 (ja) * 2019-09-10 2021-03-18 京セラ株式会社 切削構造体、データ収集システム及び切削工具
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Cited By (21)

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US6776563B2 (en) * 2001-02-23 2004-08-17 Eiji Shamoto Method of controlling elliptical vibrator
US20020119021A1 (en) * 2001-02-23 2002-08-29 Eiji Shamoto Method of controlling elliptical vibrator
EP1422440A1 (de) * 2002-11-25 2004-05-26 Rolls-Royce Deutschland Ltd & Co KG Schwingungsdämpfungsvorrichtung sowie Verfahren zur Schwingungsdämpfung zur aktiven Dämpfung von Schwingungen eines Bauteils
US20070056414A1 (en) * 2003-10-31 2007-03-15 Martin Saeterbo Arrangement for damping of vibrations and defection in a tool holder
US7908947B2 (en) * 2003-10-31 2011-03-22 Teeness Asa Arrangement for damping of vibrations and defection in a tool holder
US20050114431A1 (en) * 2003-11-25 2005-05-26 Singh Uma K. System and method for a generic mobile synchronization framework
US7591209B2 (en) * 2003-11-26 2009-09-22 Sumitomo Electric Hardmetal Corp. Vibration suppressing cutting tool
US20050109182A1 (en) * 2003-11-26 2005-05-26 Sumitomo Electric Industries, Ltd. Vibration-suppressing cutting tool
US7490536B2 (en) 2003-11-26 2009-02-17 Sumitomo Electric Hardmetal Corp. Vibration-suppressing cutting tool
EP1566481A1 (de) * 2004-02-13 2005-08-24 Voith Paper Patent GmbH Schaberdämpfung
US20060291973A1 (en) * 2005-06-28 2006-12-28 Ingvar Claesson Device and a method for preventing or reducing vibrations in a cutting tool
US7234379B2 (en) * 2005-06-28 2007-06-26 Ingvar Claesson Device and a method for preventing or reducing vibrations in a cutting tool
DE102005060779B4 (de) * 2005-12-16 2008-07-10 Eads Deutschland Gmbh Kraftgenerator
DE102005060779A1 (de) * 2005-12-16 2007-06-21 Eads Deutschland Gmbh Kraftgenerator
US20130236254A1 (en) * 2010-11-29 2013-09-12 Techspace Aero S.A. Two-material one-piece cutting tool
US10744567B2 (en) * 2015-09-10 2020-08-18 Citizen Watch Co., Ltd. Control device for machine tool and machine tool
US10254104B2 (en) 2015-10-19 2019-04-09 Kennametal Inc Method and apparatus for center height alignment of a boring bar
EP3241647B1 (de) 2016-05-03 2019-02-06 Soraluce, S.Coop. Werkzeugmaschine mit aktivem dämpfungssystem
EP3511112A1 (de) 2018-01-15 2019-07-17 Soraluce, S.Coop. Werkzeugmaschine mit aktiver dämpfung
US10500648B1 (en) * 2018-06-12 2019-12-10 Iscar, Ltd. Tool holder having integrally formed anti-vibration component and cutting tool provided with tool holder
CN112935295A (zh) * 2021-01-22 2021-06-11 山东大学 一种用于深腔加工的嵌入式阻尼减振车刀杆及方法

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SE0004540D0 (sv) 2000-12-08
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US20040240955A1 (en) 2004-12-02
SE517878C2 (sv) 2002-07-30
CN1478006A (zh) 2004-02-25
EP1339516A1 (de) 2003-09-03
CN1236884C (zh) 2006-01-18
KR100844095B1 (ko) 2008-07-04
DE60129458T2 (de) 2008-04-17
ATE367234T1 (de) 2007-08-15
KR20030061836A (ko) 2003-07-22
SE0004540L (sv) 2002-06-09
EP1339516B1 (de) 2007-07-18
JP2004515371A (ja) 2004-05-27
US7647853B2 (en) 2010-01-19
US20050262975A1 (en) 2005-12-01

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