WO2021007015A1 - Système d'amortissement réglable pour porte-outil non rotatif - Google Patents

Système d'amortissement réglable pour porte-outil non rotatif Download PDF

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Publication number
WO2021007015A1
WO2021007015A1 PCT/US2020/038883 US2020038883W WO2021007015A1 WO 2021007015 A1 WO2021007015 A1 WO 2021007015A1 US 2020038883 W US2020038883 W US 2020038883W WO 2021007015 A1 WO2021007015 A1 WO 2021007015A1
Authority
WO
WIPO (PCT)
Prior art keywords
damper assembly
ram
damper
suspension springs
front plate
Prior art date
Application number
PCT/US2020/038883
Other languages
English (en)
Inventor
David Umstadt
Original Assignee
Fives Giddings & Lewis, Llc
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
Priority claimed from US16/506,139 external-priority patent/US10920848B2/en
Application filed by Fives Giddings & Lewis, Llc filed Critical Fives Giddings & Lewis, Llc
Publication of WO2021007015A1 publication Critical patent/WO2021007015A1/fr

Links

Classifications

    • 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
    • B23B29/24—Tool holders for a plurality of cutting tools, e.g. turrets
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2260/00—Details of constructional elements
    • B23B2260/02—Cams
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2260/00—Details of constructional elements
    • B23B2260/096—Levers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B2260/00—Details of constructional elements
    • B23B2260/136—Springs

Definitions

  • An adjustable damping arrangement for a non-rotating tool holder uses springs to suspend a damper mass in the interior of the ram and damping rubber rings that can be selectively compressed to adjust the dynamic stiffness of the ram.
  • Lathe cutting capability is limited by the dynamic stiffness of the machine tool structure. Cutting tools supported by narrow rams at long extensions on vertical lathes provide the reach to cut tall parts, but often lack adequate stiffness.
  • the value of dynamic stiffness varies with frequency and is lowest at specific frequencies related to structural natural frequencies or modes. The minimum stiffness can be 50% or less than the stiffness at the rest of the frequencies, and defines the cutting capacity of the machine.
  • the frequency, stiffness, modal mass, and damping can vary as the machine elements are moved over their operating ranges.
  • Static stiffness and mass are often dictated by the machine type and size and can be difficult to alter significantly.
  • Damping which may be defined as the ability to absorb or neutralize vibrating energy can be increased through the addition of machine elements. Greater damping results in higher stiffness.
  • a spring-mass-damper may be tuned to a particular frequency for operation of the ram at the greatest extension, the lowest stiffness condition for the ram.
  • Figure 1 is a perspective view of a ram with a cutting tool attached.
  • Figure 2 is a side sectional view of a ram showing a mass damper installed in the interior of the ram.
  • Figure 3 is a perspective view of the tie rods and the suspension springs used in a damper assembly.
  • Figure 4 is a perspective view of the tie rods connected to the front plate of a damper assembly and mounted on a tool holder.
  • Figure 5 is a perspective view of the tie rods, the tension rod, and the suspension springs of a damper assembly.
  • Figure 6 is a perspective view of the tie rods, the tension rod, and the suspension springs attached to the front plate of a damper assembly.
  • Figure 7 is a perspective view of a damper assembly mounted on a tool holder.
  • Figure 8 is a side sectional view of a damper assembly.
  • Figure 9 is a bottom view of the damper assembly showing the suspension for the damper mass.
  • Figure 10 is a perspective view of the damper assembly.
  • Figure 11 is a perspective view of the rear plate of the damper assembly.
  • Figure 12 is a side sectional view of another implementation of a ram showing a mass damper installed in the interior of the ram.
  • Figure 1 is a perspective view of a ram generally designated by the reference numeral 10.
  • the ram 10 may be used on a lathe and comprises a hollow beam 12 having an interior wall 13 best seen in Figure 2.
  • a cutting tool holder 14 may be mounted on the front end 16 of the ram 10 which may support one or more cutting tools 18. Although two tools 18 are shown in the drawing, only one tool at a time is used in a cutting operation.
  • the ram may move vertically or horizontally during operation, but the ram 10 and the tools 18 do not rotate.
  • FIG 2 is a side sectional view of a ram 10 showing a damper assembly 21 having a damper mass 20 installed in the interior of the ram 10.
  • the damper mass 20 may be mounted between a front plate 22 and a rear plate 24 in the interior of the hollow beam 12.
  • Upper and lower tie rods 25 and 26, respectively, pass through the front plate 22, the damper mass 20, and the rear plate 24.
  • Ring dampers in the form of stiff rubber rings 30 best seen in Figures 4, 5, and 6 are positioned between the damper mass 20 and the front and rear plates 22 and 24, respectively.
  • tie rod nuts 27 may be used on the threaded ends 28 of the tie rods 25 and 26 to fix the distance between the front plate 22 and the rear plate 24.
  • the ends of the tie rods 25 and 26 pass through a tie rod mounting block 32 that is positioned on an end bracket 23 that is mounted on the front plate 22.
  • a tuning bolt 64 may be threaded into a tuning block 29 and may be mounted on the tie rod mounting block 32 by bolts 54. The end of the tuning bolt 64 abuts a tuning bolt spacer 65.
  • a slotted disk 60 may be positioned between the end bracket 23 and the front plate 22, and the slotted disk 60 may be formed with a hex shaped center aperture 31 which engages a hex head end 41 on a tension rod 40.
  • the slots 61 in the disk 60 may be engaged by a disk locking bolt (not shown) to prevent the disk 60 from rotating as explained more fully below.
  • suspension springs 34 may be used to support the damper mass 20 from the upper tie rod 25.
  • the suspension springs 34 may be hung from suspension brackets 35 which rest on the upper tie rod 25.
  • the suspension springs 34 pass through vertical bores 36 in the damper mass 20 (best seen in Figures 2 and 3) and hook onto support pins 37 which engage the bottom surface 38 of the damper mass 20.
  • Eight suspension springs 34 are shown supporting the damper mass 20, four near the front plate 22 and four near the rear plate 24, but a fewer or a greater number of suspension springs may be used.
  • the tension rod 40 passes through the center of the damper mass 20 and is threaded into a plug 42 having a cam surface 43 mounted in a bore in the rear plate 24.
  • the cam surface 43 engages a follower surface 46 on a locking lever 47 as shown on Figures 7, 8 and 11.
  • the locking lever 47 has two locking feet 48 which are positioned near the outer periphery of the rear plate 24. Movement of the cam surface 43 toward the damper mass 20 causes the locking lever 47 to move radially outward toward periphery of the rear plate 24.
  • the support pins 37 may be threaded through the ends of the suspension springs 34 to support the bottom surface 38 of the damper mass 20.
  • the upper and lower tie rods 25 and 26, respectively do not have to squeeze the stiff rubber rings 30 with enough force to support the weight of the damper mass 20.
  • the suspension springs 34 provide sufficient freedom of movement to the damper mass 20 so that it is able to damp the vibrations in the ram 10.
  • the front plate 22 may have two locking pistons 51 positioned near the outer periphery of the front plate 22.
  • the pistons 51 are actuated by bolts 66 which have a cam surface 67.
  • Figure 8 shows the cam surface 67 on one of the bolts 66 that is used to force the locking piston 51 outward as the bolt 66 draws the cam surface 67 against the locking piston 51.
  • the damper assembly 21 may be inserted into the interior of the ram 10 and the front plate 22 rests against the interior wall 13.
  • Bolts 66 may then be tightened forcing the cam 69 to move the locking pistons 51 outward to secure the front plate 22 against the interior wall 13 of the ram.
  • the tension rod 40 may be tightened (which also rotates the slotted disk 60) to draw the plug 42 into the bore in the rear plate 24 to force the locking lever 47 and the locking feet 48 against the interior wall 13 of the ram.
  • the tension rod 40 is only tightened enough to remove any looseness in the fit of the damper assembly 21 in the bore of the hollow beam 12 and provide light contact pressure against the interior wall 13 of the ram.
  • a locking bolt (not shown) may be inserted into one of the slots 61 in the slotted disk 60 and threaded into the front plate 22 to prevent rotation of the disk 60 and loosening of the tension rod 40.
  • the slots 61 in the disk 60 may be spaced differently from the threaded openings in the front plate 22 that receives the locking bolt. This difference operates as a Vernier and allows the disk 60 to be located at increments that are smaller than the spacing between adjacent slots 61.
  • the upper and lower tie rods 25 and 26 exert pressure on the stack of parts consisting of the rear plate 24, the rear rubber rings 30, the damper mass 20, the front rubber rings 30, the front plate 22, the end bracket 23 and the tie rod mounting block 32.
  • the tie rod nuts 27 on the upper and lower tie rods 25 and 26 are set to the length of the components with no pressure on the rubber rings 30. In this adjustment, the rubber rings 30 are in their loosest state, and the damper frequency is low.
  • the dynamic stiffness of the ram may be adjusted by tuning the damper mass
  • the resonant frequency of the damper mass 20 may be adjusted to the resonant frequency of the ram by compressing the rubber rings 30.
  • the tuning bolt 64 is used.
  • the tuning bolt 64 is threaded into the tuning block 29, and the end of the tuning bolt 64 abuts the tuning bolt spacer 65. Turning the tuning bolt 64 advances it into the tuning block 29 and presses onto the tuning bolt spacer 65, the slotted disc 60, and the front plate 22 to increase the compression on the rubber rings 30.
  • the locking feet 48 mechanically couple the rear plate 24 to the interior wall 13 of the ram 10, and the locking pistons 51 couple front plate to the interior wall 13 of the ram 10.
  • the front plate 22 and the rear plate 24 transfer vibration of the ram 10 to the rubber rings 30 which react against the damper mass 20 to absorb vibrational energy of the ram.
  • the suspension springs 34 support the weight of the damper mass 20, and the upper and lower tie rods 25 and 26 do not have to squeeze the stiff rubber rings 30 with enough force to support the weight of the damper mass 20, the damper mass 20 has sufficient freedom of movement so that it is able to damp the vibrations in the ram 10.
  • a damper assembly includes a damper mass 20 installed in the interior of the ram 100.
  • the damper mass 20 may be mounted between a front plate 22’ and a rear plate 24 in the interior of the hollow beam 12.
  • the front plate 22’ is a unitary structure that can extend partially within the ram 100 yet also remain at least partially outside of the internal cavity of the ram 100 and also abut an end 52 of the ram 10 thereby acting as an enclosure of the hollow cavity within the ram 100.
  • a backing plate 56 can be fitted onto the front plate 22’ and include bores 58 for receiving the upper and lower tie rods 25 and 26.
  • the threaded ends 28 can extend through both the bores 54 in the end plate 22’ and the bores 58 in the backing plate 56; the ends 28 can be secured with tie rod nuts 27.
  • Ring dampers in the form of stiff rubber rings 30 are positioned between the damper mass 20 and the front and rear plates 22’ and 24, respectively.
  • a tuning bolt 64 may be threaded into a tuning block 29.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Auxiliary Devices For Machine Tools (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

Ensemble amortisseur destiné à être utilisé avec un porte-outil non rotatif comprenant un coulisseau creux pour supporter un outil non rotatif et un ensemble amortisseur monté dans le coulisseau creux pour absorber les vibrations du coulisseau. L'ensemble amortisseur comprend une plaque avant et une plaque arrière, une tige de liaison supérieure et une tige de liaison inférieure s'étendant entre la plaque avant et la plaque arrière, et une masse d'amortissement montée entre la plaque avant et la plaque arrière. Des amortisseurs annulaires sont montés entre la masse d'amortissement et les plaques avant et arrière, et des ressorts de suspension sont montés entre la tige de liaison supérieure et la tige de liaison inférieure. Les ressorts de suspension supportent le poids de la masse d'amortissement de sorte que les amortisseurs annulaires ne doivent pas supporter le poids de la masse d'amortissement, et la masse d'amortissement est libre de réagir aux vibrations dans le coulisseau.
PCT/US2020/038883 2019-07-09 2020-06-22 Système d'amortissement réglable pour porte-outil non rotatif WO2021007015A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US16/506,139 US10920848B2 (en) 2016-10-03 2019-07-09 Adjustable damping arrangement for a non-rotating tool holder
US16/506,139 2019-07-09

Publications (1)

Publication Number Publication Date
WO2021007015A1 true WO2021007015A1 (fr) 2021-01-14

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2020/038883 WO2021007015A1 (fr) 2019-07-09 2020-06-22 Système d'amortissement réglable pour porte-outil non rotatif

Country Status (1)

Country Link
WO (1) WO2021007015A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11396048B2 (en) * 2017-09-15 2022-07-26 Sandvik Intellectual Property Ab Turning tool and method for metal cutting

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002113603A (ja) * 2000-10-06 2002-04-16 Honda Motor Co Ltd 防振切削工具
JP2003089006A (ja) * 2001-09-11 2003-03-25 Toyota Jidosha Hokkaido Kk チャックにおける防振ダンパ
EP1952951B1 (fr) * 2007-01-31 2012-11-21 HILTI Aktiengesellschaft Machine-outil manuelle tournante et frappante avec un amortisseur de vibrations
US20130118848A1 (en) * 2011-11-11 2013-05-16 Mag Ias, Llc Symmetrical head mounted tuned mass damper
US8656807B2 (en) * 2009-07-15 2014-02-25 Fives Machining Systems, Inc. Damped rotary encoder
US20180093329A1 (en) * 2016-10-03 2018-04-05 Fives Giddings & Lewis, Llc Adjustable damping arrangement for a non-rotating tool holder
US20190331194A1 (en) * 2016-10-03 2019-10-31 Fives Giddings & Lewis, Llc Adjustable damping arrangement for a non-rotating tool holder

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002113603A (ja) * 2000-10-06 2002-04-16 Honda Motor Co Ltd 防振切削工具
JP2003089006A (ja) * 2001-09-11 2003-03-25 Toyota Jidosha Hokkaido Kk チャックにおける防振ダンパ
EP1952951B1 (fr) * 2007-01-31 2012-11-21 HILTI Aktiengesellschaft Machine-outil manuelle tournante et frappante avec un amortisseur de vibrations
US8656807B2 (en) * 2009-07-15 2014-02-25 Fives Machining Systems, Inc. Damped rotary encoder
US20130118848A1 (en) * 2011-11-11 2013-05-16 Mag Ias, Llc Symmetrical head mounted tuned mass damper
US20180093329A1 (en) * 2016-10-03 2018-04-05 Fives Giddings & Lewis, Llc Adjustable damping arrangement for a non-rotating tool holder
US20190331194A1 (en) * 2016-10-03 2019-10-31 Fives Giddings & Lewis, Llc Adjustable damping arrangement for a non-rotating tool holder

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11396048B2 (en) * 2017-09-15 2022-07-26 Sandvik Intellectual Property Ab Turning tool and method for metal cutting

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