US3227047A - Anti-sag underarm for horizontal boring, drilling and milling machines and the like - Google Patents

Anti-sag underarm for horizontal boring, drilling and milling machines and the like Download PDF

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Publication number
US3227047A
US3227047A US259966A US25996663A US3227047A US 3227047 A US3227047 A US 3227047A US 259966 A US259966 A US 259966A US 25996663 A US25996663 A US 25996663A US 3227047 A US3227047 A US 3227047A
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Prior art keywords
underarm
arm
spindle
force
cam
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US259966A
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English (en)
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Gordon H Jones
Schultheiss Fritz
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Giddings and Lewis LLC
Giddings and Lewis Machine Tool Co
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Giddings and Lewis LLC
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Priority to US259966A priority Critical patent/US3227047A/en
Priority to FR963697A priority patent/FR1389715A/fr
Priority to BE643741D priority patent/BE643741A/xx
Priority to GB6516/64A priority patent/GB1039153A/en
Priority to DE19641477348 priority patent/DE1477348A1/de
Priority to CH199564A priority patent/CH418777A/fr
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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
    • 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
    • B23Q11/001—Arrangements compensating weight or flexion on parts of the machine
    • B23Q11/0014—Arrangements compensating weight or flexion on parts of the machine using static reinforcing elements, e.g. pre-stressed ties
    • 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
    • B23Q11/001—Arrangements compensating weight or flexion on parts of the machine
    • B23Q11/0017—Arrangements compensating weight or flexion on parts of the machine compensating the weight of vertically moving elements, e.g. by balancing liftable machine parts
    • 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
    • Y10T409/30784—Milling including means to adustably position cutter
    • Y10T409/307952—Linear adjustment
    • 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
    • Y10T409/309576—Machine frame
    • Y10T409/309744—Machine frame including means to compensate for deformation
    • Y10T409/3098—Deflection of cutter spindle

Definitions

  • the present invention relates to the field of machine tools and more specifically to a novel underarm support mechanism finding particular but not exclusive utility in machine tools of the type known as horizontal boring, drilling and milling machines.
  • Machines of this type frequently include a headstock having an extensible power driven spindle, together with a sliding support member known as an underarm.
  • the latter is translatable parallel to and in synchronism with the spindle and serves as an outboard support for the tools, fixtures or attachments utilized with the headstock.
  • Such machines are, for example, illustrated and described in United States Patents Nos. 2,890,629 and 2,984,- 159, issued June 16, 1959, and May 16, 1961, respectively, on the applications of Garner H. Schurger et al.
  • the sliding support member may be utilized as a tool carrying ram for planing or shaping operations, independently of a spindle.
  • the sliding support may actually house a spindle, the latter being substantially concentric therewith.
  • the term underarm, as used herein, is intended to apply to a variety of such sliding support members, whether or not they are associated with, or under, a spindle.
  • An underarm is usually designed as a relatively stiff, boxlike structure of substantial cross-sectional area but, upon extension from the headstock or other support, it behaves as a cantilever beam and undergoes a certain amount of deflection which tends to impair machining accuracy.
  • the deflection increases in proportion to the amount of extension of the underarm from the headstock or support and which extension may, for example, vary from zero to 60 inches.
  • Underarm deflection results from the weight of the underarm per unit length and from external loads due to the weight of the tool, fixture or attachment mounted at the outboard end of the underarm. Still another factor contributing to underarm deflection is misalignment of one or more machine frame members, or the guideways connecting such members, due to the weight, or disposition of the weight, of the underarm.
  • an object of the present invention to provide an underarm support mechanism for a machine tool which will compensate fully for underarm deflection due to the weight of the underarm itself, or to be weight of the tool, fixture or attachment mounted at the outboard end of the underarm, or to misalignment of one or more of the associated machine frame members.
  • Another object of the invention is to provide an underarm support mechanism of the character set forth and adapted to compensate automatically for underarm deflection continuously as the underarm is extended or retracted and regardless of the amount of extension within the range of underarm movement so that the underarm will remain essentially horizontal.
  • a further object is to provide an underarm support mechanism of the foregoing type wherein the compensation for underarm deflection may be selectively adjusted to correspond with various tools, fixtures or attachments mounted on the underarm.
  • Still another object of the invention is. to provide an underarm support mechanism of the character set forthand which utilizes a novel arrangement for creating internal counterbending forces of proper magnitude to prevent deflection of the underarm throughout its range of movement.
  • FIGURE 1 is a perspective view of an illustrative horizontal boring, drilling and milling machine embodying the present invention.
  • FIG. 2 is an enlarged fragmentary perspective view of the underarm support mechanism of the machine shown in FIG. 1.
  • FIG. 2A is an enlarged fragmentary perspective view detailing a portion of the adjusting mechanism within the underarm.
  • FIG. 3 is a further enlarged fragmentary sectional view taken vertically through the inboard portion-of the underarm and headstock of the machine shown in FIG. 1.
  • FIGS. 4A and 4B are further enlarged fragmentary vertical sectional views taken longitudinally through the inboard end portion of the underarm.
  • FIG. 5 is a transverse sectional view of the underarm taken in the plane of the line 5-5 of FIG. 4A.
  • FIG. 6 is a transverse sectional view taken in the plane of the line 6--6 of FIG. 4B.
  • FIG. 7 is an enlarged detailed elevational view'of an adjusting cam and index dial at the outboard end of the underarm, as shown in FIG. 4B.
  • FIG. 8 is a schematic representation of the underarm in two of its possible extended positions.
  • the present invention is there exemplified in a heavy duty horizontal boring, drilling and milling machine 10 of a general configuration wellknown to those skilled in the art.
  • the machine 10 in this instance comprises a bed 12 having three parallel ways 14 longitudinally formed thereon.
  • a vertical. column 16 including a column base, is disposed for, move: ment on the ways 14 longitudinally of the bed.
  • a control. station including a platform 22, is secured to. the casing 24 of the headstock so as to permit the operator to ride with the headstock.
  • the headstock 18 supports a horizontal spindle 26 which may be rotated and translated on an axis parallel to the top of the bed 12 by extending or retracting the spindle into and out of the headstock 18.
  • the above arrangement comprises. the working end of the machine, which performs operations on a workpiece located adjacent the spindle on an appropriate work support (not shown).
  • the machine 10 is provided with an extensible underarm St) slidably housed in the headstock 18 below and parallel to the spindle 26.
  • the underarm and the spindle are movable axially in unison to meet the requirements of any given job, the underarm providing a running support for the spindle and its associated tools, fixtures or attachments.
  • a s indle support 32 is mounted at, the outboard end of the underarm and receives and supports the end of the spindle 26.
  • the latter includes suitable means for mounting a tool and the construction of the support 32 may be such as to permit the spindle and tool to be projected axially beyond it.
  • the machine and underarm embody a novel anti-sag arrangement which is adapted to compensate fully for deflection of the underarm throughout its range of movement.
  • the foregoing is accomplished through a mechanism adapted to develop appropriate internal forces of suificient magnitude to resist deflection of the underarm due to one or more of the following factors: (1) its own weight; (2) the weight of the tool, fixture or attachment mounted at its outboard end; and (3) misalignment of one or more of the machine frame members. This imparts added rigidity to the spindle in its extended positions, thereby substantially enhancing the machining accuracy and precision of the machine.
  • the underarm 30 comprises in this instance a hollow rectangular structure defined by upper and lower plates 34, of relatively heavy construction and opposed side members 36, 37 which are somewhat lighter.
  • the side members may be joined to the plates to form the underarm shell, as by welds 38, or in any other appropriate manner so as to present relatively smooth outer walls about the perimeter of the underarm. This facilitates precise guiding and supporting of the underarm in the headstock.
  • the underarm is slidably supported in bearing surfaces provided on all four sides thereof within the headstock.
  • the bearing surfaces are arranged to permit a minimum of clearance with respect to the underarm.
  • Tapered gibs 40 shown in FIG. 3, are provided about the perimeter of the underarm and may be adjusted to obtain the proper clearance for a close sliding fit.
  • a drive arrangement is provided in the headstock 18 for extending and retracting both the spindle 26 and the underarm 30.
  • drive arrangements for the spindle and underarm are interrelated to provide coincident operation of the two, although it will be appreciated that independent drive arrangements may be provided where it would be advantageous to do so.
  • parallel driving screws 41 and 43 powered by the headstock transmission are used to traverse the spindle and underarm.
  • a driving nut 45, disposed upon the screw 41, is attached to the spindle 26 so that rotation of the screw 41 will result in travel of the nut 45 therealong, shifting the spindle to the left or right as indicated in FIG. 3, depending upon the direction in which the screw 41 is turned.
  • a driving nut 47 secured to the upper plate 34 of the underarm 30, is mounted on the screw 43, and rotation of the screw 43 results in the translation of the underarm to the right or left as viewed in FIG. 3.
  • the pitch of the threads of the screws 41 and 43 is such that when the screws are driven by the power source (not shown), translational movement of the spindle and underarm will be coordinated and in unison, thus providing continuous support for the spindle, regardless of its position relative to the headstock.
  • the underarm is constructed and arranged so as to compensate fully, throughout its range of translational movement, for deflection or droop due to its own weight, or to the weight of the tool, fixture or attachment mounted at its outboard end, or to misalignment of one or more of the machine frame members.
  • This is accomplished through means adapted to develop appropriate internal forces within the underarm to counteract the deflection which would otherwise result from one or more of these factors.
  • such means comprises an anti-sag mechanism 50 positioned within the underarm 30 and operatively connected therewith (FIGS. 2, 4A, 4B and 8).
  • the anti-sag mechanism 50 comprises a compensator beam 53 defined by a pair of laterally spaced upstanding flanges 55, 56 which are disposed within and longitudinally of the underarm.
  • the upstanding flanges 55, 56 are maintained in lateral rigidity by crossbars 57 which may be fastened thereto as by screws 59.
  • the compensator beam 53 is stressed within the underarm and relative thereto in order to set up predetermined compensating reactive forces in the underarm.
  • Controlled stressing of the beam 53 is carried out in the present instance through the novel disposition of the beam within the underarm so as to provide lever action contact between the beam and the underarm in three spaced vertical planes. These are represented in FIGS. 4A, 4B and 8 by the lines I, II and III, and the contact is such that all forces and reaction forces occurring between the beam and underarm occur substantially in those vertical planes.
  • a longitudinal cam mechanism 58 (see FIGS. 2, 3, 4A and 8) situated at the inboard end of the underarm 30 and beam 53.
  • the latter comprises, in this instance, follower means mounted on the underarm and cam means connected with the beam 53.
  • the inboard end of the underarm (the righthand end, as viewed in the drawings) is provided with a cam follower supporting frame comprising parallel side plates 60 which are fitted flush against the sides 36 and 37 of the underarm.
  • the plates 60 are joined by a flanged base plate 62, secured by means of screws 64 to the end of the plate 35, and by an L-shaped top plate 66 rigidly secured to the member 34 of the underarm by screws 68.
  • the side plates 66 pivotally support an upper cam follower 76 on a horizontal pivot pin 72 disposed transversely between them.
  • the follower 70 is actually a modified bell crank comprising an arm 74, which has a roller 76 mounted on a pin 78 at its projecting end, and a pair of downwardly extending fingers 80. The latter engage in pressure contact in the vertical plane III with a correponding pair of flat abutting surfaces 83 at;
  • the arm 74 has a radial length several times that mgs. of each finger 80, resulting in multiplication of the force: transmitted from the roller 76 to the fingers 8t).
  • a second cam follower is provided in the flange plate 62 and comprises a roller 85 disposed on a pin 87 in position such that the axes of the rollers 76 and 85, respectively, are presented in a single vertical plane.
  • the second follower is fixed with respect to the underarm and simply provides a running support for longitudinal cam 90 which actuates the follower 70.
  • the longitudinal cam 90 is fastened at one end to the headstock and traversed by the follower 70 as the underarm is translated.
  • the slope of the cam 90 is mather'natically determined to 'set up counterstresses in the underarm through the medium of the beam 53 to compensate for the droop resulting from the unit weight of the underarm as it is extended. Since the weight of the extended portion of the underarm is a linear function of the amount of extension, the slope of the cam 90 is substantially linear.
  • the longitudinal cam 90 is provided with means for adjusting its slope. Such adjustment will tend to vary somewhat from one machine to the next due to slight variations in factors such as foundation support and guideway clearances. In effecting such compensation, the adjustment of the longitudinal cam 90 will result in the application of a reverse bend to the underarm via the compensator beam 53.
  • the longitudinal cam 90 is constructed in two separate parts which are adjustable relative to one another.
  • a base member 91 is secured to a stationary wall 93, which may conveniently comprise the rear wall of the housing of headstock 18.
  • the base member 91 is pivoted as at 95 so that a few degrees angular movement is permitted.
  • the bottom wall 97 of the base member is finished and hardened and rests upon the roller 85.
  • the base member 91 is channeled as at 99 (see particularly FIGS. 2, 2A and 5), and the channel extends from the left-hand end of the base member to a point near the right-hand end of said member, as viewed in the drawings.
  • a number of hardened pins 100 traverse the channel 99 between the legs 102 flanking the channel in a line along the length thereof.
  • the second or upper part 104 of the longitudinal cam 90 is a relatively long cam bar which rests upon, and is ad justable relative to, the base member 91.
  • the bar 104 is fitted with an adjustment screw 106 at the right-hand end thereof, which may be rotated by means of head 107.
  • the screw 106 may be used to move the cam bar 104 to the right or left, the screw itself being secured against axial movement as at 108.
  • a scale 109 is mounted on the base member 91 is proximity to the end of the bar 104 and screw 106 to faciliate the making of adjustments.
  • the cam bar 104 is formed with a plurality of notches 110, 111, 112, 113, and 114, reading from right to left along the cam member.
  • Each such notch is fitted with a trapezoidal-shaped block 116, 117, 118, 119 and 120, each being fastened within a notch by any appropriate means, such as screws 121, such that a portion of each block below protrudes below the bar 104.
  • Each such portion protruding below the bar 104 defines, an inclined cam surface disposed at an angle which is less than 90 from the horizontal.
  • Each such surface is positioned opposite a pin 100 when the two parts of the cam 90 are assembled, and each surface rides on an associated piri 100 as the two parts are adjusted relatively.
  • the angle of the inclined surfaces which are indicated at 123, 124, 125, 126, and 127, respectively, increases from right to left so that the slope of the surface 123, for example, is relatively gentle as compared to that of the surface 127.
  • the downward force exerted on the abutment surfaces 83 which, it will be remembered, is at the end of the beam 53, tends to urge the beam about its intermediate pivot point indicated at on FIG. 4B which acts as a fulcrum.
  • the pivot 135 in this case comprises a pair of aligned transverse pins 137 and corresponding bearings upon which the beam 53 is adapted to ride.
  • a downward force exerted on the abutting surface 83 tends to rock the beam 53 in a clockwise direction about the pins 137, resulting in an upward force being exerted at the left-hand end of the beam 53 which is connected adjacent the outboard end of the underarm.
  • the compensator beam 53 acts as a force multiplying lever to exert an increased upward force near the outboard end of the underarm to counteract the normal sagging or drooping reaction which would otherwise occur, due to the unit weight of the underarm and misalignment of the supporting machine frame members as the underarm is extended.
  • correction may be made by adjustment of the screw head 107 to vary the relative position of the cam bar 104 and base member 91 to change the slope of the surface 129 and the resultant force transmitted :to the compensator beam and underarm.
  • means is provided to compensate for extraordinary loads due to the weight of tools, fixtures or attachments mounted on the underarm, and which cause additional deflection or droop thereof.
  • this is achieved by the use of a manually adjustable compensating arrangement situated at the outboard end of the beam 53 to modify the location of the force transmitting connection and the upward or anti-sag force transmitted to the end of the underarm.
  • FIGURES 4B, 6 and 7. An exemplary arrangement of the type referred to is shown in detail in FIGURES 4B, 6 and 7.
  • the left end of the beam 53 is relieved by cutting a portion thereof away, thereby providing a hat surface 147 on each of the flanges 55 and 56 thereof for receipt of a pair of cam follower brackets 149 fastened to the flanges by screws 150.
  • Each bracket carries a cam follower 152 mounted on a pin 154, and each follower 152 abuts and defines a force transmitting connection with a polygonal shaped cam element integral with a cam member156 journaled in the side walls 36, 37 of the underarm.
  • the cam 156 is provided with an appropriate socket 157 for engagement by a wrench or other suitable adjusting tool.
  • the cam 155 is formed with a pair of identical axially spaced five-sided cam elements although it will be appreciated that such cam elements may have any convenient number of sides without departing from the invention disclosed herein.
  • Each pair of the sides or cam surfaces 158, 153, 160, 161, and 162 is presented at a diiferent radial distance from the center 164 of the cam 156.
  • Each such pair of sides is specially formed to compensate for the weight of a particular tool, fixture or attachment mounted on the underarm.
  • Adjustment of the cam 156 may be facilitated by a concentric index dial 163 surrounding the socketed end of the cam and fixed thereto, the dial being suitably marked to correspond to any given assortment of tools, fixtures or attachments to be used on the machine (FIG. 7).
  • cam 156 may be manually rotated about its axis 164, from the underarm alone position, until a corresponding pair of sides, such as sides 158, are presented against the cam followers 152. This shifts the location of the force transmitting connection between the compensator beam 53 and the outboard end portion of the underarm 30. It also results in application of an increased increment of corrective force from the beam to the outboard end portion of the underarm of sufiicient magnitude to offset the added deflection due to the weight of the milling attachment.
  • anti-sag underarm arrangement described herein may also be utilized in other machine configurations with or without a headstock or spindle and whether or not the underarm is spaced from or substantially coaxial with the spindle.
  • a machine tool having a headstock comprising a headstock housing, a spindle mounted in said housing for rotation and for projected axial translation, an extensible underarm slidably mounted in said housing below and spaced from said spindle for longitudinal translation parallel to said spindle, said underarm being adapted to support a tool element adjacent the projecting end of said spindle and in driving relation thereto, a compensator beam mounted within said underarm on a fulcrum intermediate the ends thereof, said compensator beam being bodily movable with said underarm, means connecting said beam and said underarm between said fulcrum and one end of said underarm, cam and follower means interposed between said housing and the other end of said underarm, and means connecting said cam and follower means and said beam between said fulcrum and said other end of said underarm for application of a corrective. force to said beam in proportion to the extension of said underarm.
  • a machine tool having a headstock
  • the combination comprising a headstock housing, a spindlemounted in said housing for rotation and for projected axial translation, said spindle being substantially horizontal, an extensible underarm slidably mounted in said housing below and spaced from said spindle for longitudinal translation parallel to said spindle, said underarm being adapted to support a tool or fixture or attachment adjacent the projecting end of said spindle and in driving relation thereto, a compensator beam mounted within said underarm on a fulcrum intermediate the ends thereof, said compensator beam being bodily movable with said underarm, means connecting said beam and said underarm between said fulcrum and one end of said underarm, a longitudinal cam fixed to said housing and disposed in telescoping relation with said underarm and said compensator beam, follower means mounted on the other end of said underarm and disposed in operative engagement with said longitudinal cam, and means connecting said follower means 0 and said beam for application of force thereto in proportion to the extension of said underarm.
  • a headstock housing comprising a headstock housing, a spindle mounted in said housing for rotation and for projected axial translation, said spindle being substantially horizontal, an extensible underarm slidably mounted in said housing below and spaced from said spindle for longitudinal translation parallel to said spindle, said underarm being adapted to support a tool or fixture or attachment adjacent the projecting end of said spindle and in driving relation thereto,
  • a compensator beam mounted within said underarm on a fulcrum intermediate the ends thereof, said compensator beam being bodily movable with said underarm, means connecting said beam and said underarm between said fulcrum and one end of said underarm, a longitudinal cam fixed to said housing and disposed in telescoping relation with said underarm and said compensator beam, a follower mounted on the other end of said underarm and disposed in operative engagement with said longitudinal cam, means connecting said follower and said beam for application of force thereto in proportion to the extension of said underarm, and cam means for selectively adjusting the point of connection of said compensator beam and said underarm corresponding to particular external loads on said underarm.
  • a spindle mounted in said housing for rotation and for projected axial translation, said spindle being substantially horizontal, an extensible underarm slidably mounted in said housing below and spaced from said spindle for longitudinal translation parallel to said spindle, said underarm being adapted to support a tool or fixture or attachment adjacent the projecting end of said spindle and in driving relation thereto, a compensator beam mounted on and bodily movable with said underarm on a fulcrum intermediate the ends thereof, means connecting said beam and said underarm between said fulcrum and one end of said underarm, a longitudinal cam fixed to said housing and disposed in telescoping relation with said underarm and said compensator beam, a follower mounted on the other end of said underarm and disposed in operative engagement with said longitudinal cam, means connecting said follower and said beam for application of force thereto in proportion to the extension of said underarm, and means for adjustably changing the
  • a spindle mounted in said housing for rotation and for projected axial translation, said spindle being substantially horizontal, an extensible underarm slidably mounted in said housing below and spaced from said spindle for longitudinal translation parallel to said spindle, said underarm being adapted to support a tool or fixture or attachment adjacent the projecting end of said spindle and in driving relation thereto, a compensator beam mounted on and bodily movable with said underarm on a fulcrum intermediate the ends thereof, a force transmitting connection between said beam and one end of said underarm remote from said fulcrum, a longitudinal cam fixed to said housing and disposed in telescoping relation with said underarm and said compensator beam, a follower mounted on the other end of said underarm and disposed in operative engagement with said longitudinal cam, means connecting said follower and said beam for application of force thereto in pro-portion to the extension of said underarm, means for adjust
  • a machine tool of the type which includes a column and a headstock mounted for vertical movement thereon, the combination comprising a horizontal spindle mounted in said headstock for rotation and projected axial translation, an underarm slidably mounted in said headstock and spaced from said spindle for longitudinal translation parallel to said spindle, power means for rotating said spindle and extending and retracting said spindle and said underarm with respect to said headstock, a force multiplying beam fulcrumed within said underarm, means at the headstock end of said underarm for applying a predetermined force to said beam and which includes a stationary cam having a uniformly changing slope, a cam follower for continuously sensing changes in slope of said cam as said underarm is extended and retracted from said headstock, said cam follower being adapted to transmit a change in cam slope in the form of an applied force directed to one end of said beam, said beam being adapted to multiply said applied force and transmit the same to the unsupported end of said underarm for counteracting drooping thereof, said cam comprising
  • a machine tool of the type which includes a column and a headstock mounted for vertical movement thereon, the combination comprising a horizontal spindle, an underarm slidably mounted in said headstock, power transmission means for rotating said spindle and extending and retracting said spindle and said underarm with respect to said headstock, a force multiplying beam fulcrummed on said underarm, camming means for applying a force to one end of said beam in proportion to the unsupported weight of said underarm as it is extended to compensate for sag resulting from such weight, said beam being adapted to multiply and transmit the applied force to the unsupported end of said underarm, means for adjusting said camming means to compensate for changes in position of said headstock and column, and means at the end of said beam opposite said camming means disposed between said beam and said underarm for increas ing the applied force to the unsupported end of said underarm in proportion to external bending forces due to the weight of a tool, fixture or attachment mounted on the underarm.
  • an anti-sag mechanism for countering the tendency of said underarm to droop when extended and comprising, in combination, a beam disposed within said underarm and movable therewith, camming means at the inboard end of said underarm and engaging said beam for applying a predetermined force to the inboard end thereof, such force being applied automatically in accordance with the amount of extension of said underarm and spindle, said beam being adapted to multiply and transmit such force to the outboard end of said underarm, and a second camming means interposed between said beam and said underarm adjacent the outboard end of the latter, said second camming means being adjustable in accordance with externally applied weight loads at the outboard endof said underarm to compensate for underarm deflection due to such externally applied loads.
  • an anti-sag mechanism for countering the tendency of said undearm to droop when extended and comprising, in combination,
  • a beam disposed within said underarm and movable therewith, camming means at the inboard end of said underarm and engaging said beam for applying a predetermined force to the inboard end thereof, such force being applied automatically in accordance with the amount of extension of said underarm, said beam being adapted to multiply and transmit such force to the outboard end of said underarm, and a second camming means interposed between said beam and said underarm adjacent the outboard end of the latter, said second camming means being adjustable in accordance with externally applied weight loads at the outboard end of said underarm to compensate for underarm deflection due, to such externally applied loads.
  • a machine tool having machine frame members including a housing
  • the combination comprising an extensible underarm slidably mounted in said housing for longitudinal translation, said underarm being adapted to support a tool or fixture or attachment adjacent its projecting end, a compensator beam mounted on and bodily movable with said underarm on a fulcrum intermediate the ends thereof, means connecting said beam and said underarm between said fulcrum and one end of said underarm, a longitudinal cam fixed to said housing and disposed in telescoping relation with said underarm and said compensator beam, a follower mounted on the other end of said underarm and disposed in operative engagement with said longitudinal cam, means connecting said follower and said beam for application of force thereto in proportion to the extension of said underarm, and means for adjustably changing the slope of said longitudinal cam to introduce a correction factor for misalignment of one or more of said machine frame members.
  • a machine tool adapted to perform machining operations in positions located horizontally outwardly from support structure of the machine tool
  • the combination comprising machine tool support structure, an elongated arm movably supported by said support structure for longitudinal translation between a retracted position and extended positions in which a machining end of the arm projects different distances from the support structure in a direction having a material horizontal component, means on said machining end of the arm adapted to support machining structure, drive means coacting with said arm to extend and retract the arm longitudinally, a gravity counteracting beam for supporting by bending moment in the beam the weight of the load on said arm and the eflective weight of the portion of the arm that projects from said support structure when the arm is fully extended, said gravity counteracting beam being disposed in generally parallel adjacent relation to said arm and having an outer end disposed near said machining end of said.
  • first load bearing means movable with said arm and supporting said beam at a position spaced inwardly from the machining end of the arm by a distance equal to a major fraction of the length of the portion of the arm which projects from said support structure when the arm is fully extended
  • second load bearing means interconnecting said beam near its outer end with said arm near the machining end of the latter to transmit a vertical gravity counteracting force from the beam to the machining end of the arm
  • actuating means coacting with said beam to controllably apply to the beam a gravity counteracting bending moment that tends to swing said outer end of the beam upwardly about said first load bearing means to apply to said machining end of the arm a gravity counteracting lifting force that is proportional to the gravity counteracting bending moment in the beam
  • one of said first and second load bearing means including relative motion means for providing free movement of adjacent portions of the beam and arm relative to each other in a longitudinal direction with respect to said arm substantially to avoid transmission of horizontal force
  • a machine tool adapted to perform machining operations in positions located horizontally outwardly from support structure of the machine tool
  • the combination comprising machine tool support structure, an elongated arm movably supported by said support structure for longitudinal translation between a retracted position and extended positions in which a machining end of the arm projects different distances from the support structure in a direction having a material horizontal component, means on said machining end of the arm adapted to support machining structure, drive means coacting with said arm to extend and retract the arm longitudinally; a gravity counteracting beam for transmitting, by bending moment in the beam, to the outer end of the arm a variable vertical force which sustains the outer end of the arm against downward displacement by the force of gravity on the arm and its load; said gravity counteracting beam being disposed in generally parallel adjacent relation to said arm and having an outer end disposed near said machining end of said arm, first load bearing means movable with said arm and supporting said beam at a position spaced inwardly from said machining end of the arm by a distance equal to a
  • a machine tool adapted to perform machining operations in positions located horizontally outwardly from support structure of the machine tool
  • the combination comprising machine tool support structure, an elongated arm movably supported by said support structure for longitudinal translation between a retracted position and extended positions in which a machining end of the arm projects different distances from the support structure in a direction having a material horizontal component, means on said machining end of the arm adapted to support machining structure, drive means coacting with said arm to extend and retract the arm longitudinally; a generally straight gravity counteracting beam for transmitting, by bending moment in the beam, to the outer end of the arm a variable vertical force which sustains the outer end of the arm against downward displacement by the force of gravity on the arm and its load; said gravity counteracting beam being disposed in generally parallel adjacent relation to saidarm and having an outer end disposed near said machining end of said arm, first load bearing means movable with said arm and coacting with a medial portion of said beam to pivotally support said beam for pivotal movement about a generally
  • a machine tool adapted to perform machining operations in positions located horizontally outwardly from support structure of the machine tool
  • the combination comprising machine tool support structure, an elongated arm movably supported by said support structure for longitudinal translation between a retracted position and extended positions in which a machining end of the arm projects different distances from the support structure in a direction having a material horizontal component, means on said machining end of the arm adapted to support machining structure, drive means coacting with said arm to extend and retract the arm longitudinally, a gravity counteracting beam for supporting by bending moment in the beam the weight of the load on said arm and the effective weight of the portion of the arm that projects from said support structure when the arm is extended,
  • said gravity counteracting beam being disposed in generallly parallel adjacent relation to said arm and having an outer end disposed near said machining end of said arm to transmit to said machining end of the arm a force that is essentially vertical
  • first load bearing means movable with said arm and supporting said beam at a position spaced inwardly from the machining end of the arm by a distance equal to a major fraction of the length of the portion of the arm which projects from said support structure when the arm is fully extended
  • second load bearing means interconnecting said beam near its outer end with said arm near the machining end of the latter to transmit a vertical gravity counteracting force from the beam to the machining end of the arm
  • actuating means coacting with said beam to controllably apply to the beam a gravity counteracting bending moment that tends to swing said outer end of the beam upwardly about said first load bearing means to apply to said machining end of the arm a gravity counteracting lifting force that is proportional to the gravity counteracting bending moment in the beam; the portion of said beam extending between said
  • a machine tool adapted to perform machining operations in positions located horizontally outwardly from support Structure of the machine tool
  • the combination comprising machine tool support structure, a hollow elongated arm movably supported by said support structure for longitudinal translation between a retracted position and extended positions in which a machining end of the arm projects difierent distances from the support structure in a direction having a material horizontal component, means on said machining end of the arm adapted to support machining structure, drive means coacting with said arm to extend and retract the arm longitudinally; a generally straight gravity counteracting beam for transmitting, by bending moment in the beam, to the outer end of the arm a variable vertical force which sustains the outer end of the arm against downward displacement by the force of gravity on the arm and its load; said gravity counteracting beam being disposed within said arm in generally parallel relation thereto and having an outer end disposed near said machining end of said arm, first load bearing means on said arm coacting with a medial portion of said beam to pivotally support said beam for pivotal movement about
  • a machine tool adapted to perform machining operations in positions located horizontally outwardly from support structure of the machine tool
  • the combination comprising machine tool support structure, an elongated arm movably supported by said support structure for longitudinal translation between a retracted position and extended positions in which a machining end of the arm projects different distances from the support structure in a direction having a material horizontal component, means on said machining end of the arm adapted to support machining structure, drive means coacting with said arm to extend and retract the arm longitudinally, a gravity counteracting beam for supporting by bending moment in the beam the weight of the load on said arm and the effective weight of the portion of the arm that projects from said support structure when the arm is extended, said gravity counteracting beam being disposed in generally parallel adjacent relation to said arm and having an outer end disposed near said machining end of said arm to transmit to said machining end of the arm a force that is essentially vertical, first load bearing means movable with said arm and supporting said beam at a position spaced inwardly from the machining end of the

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Machine Tool Units (AREA)
  • Prostheses (AREA)
US259966A 1963-02-20 1963-02-20 Anti-sag underarm for horizontal boring, drilling and milling machines and the like Expired - Lifetime US3227047A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US259966A US3227047A (en) 1963-02-20 1963-02-20 Anti-sag underarm for horizontal boring, drilling and milling machines and the like
FR963697A FR1389715A (fr) 1963-02-20 1964-02-13 Bras inférieur pour machines horizontales à aléser, percer et fraiser
BE643741D BE643741A (en)van) 1963-02-20 1964-02-13
GB6516/64A GB1039153A (en) 1963-02-20 1964-02-17 Machine tools with cantilever beams
DE19641477348 DE1477348A1 (de) 1963-02-20 1964-02-18 Werkzeugmaschine
CH199564A CH418777A (fr) 1963-02-20 1964-02-19 Machine-outil

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US259966A US3227047A (en) 1963-02-20 1963-02-20 Anti-sag underarm for horizontal boring, drilling and milling machines and the like

Publications (1)

Publication Number Publication Date
US3227047A true US3227047A (en) 1966-01-04

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US259966A Expired - Lifetime US3227047A (en) 1963-02-20 1963-02-20 Anti-sag underarm for horizontal boring, drilling and milling machines and the like

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US (1) US3227047A (en)van)
BE (1) BE643741A (en)van)
CH (1) CH418777A (en)van)
DE (1) DE1477348A1 (en)van)
GB (1) GB1039153A (en)van)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4178834A (en) * 1977-06-23 1979-12-18 The Warner & Swasey Company Machine tool having deflection compensation for tool support arm
US20110255933A1 (en) * 2008-12-24 2011-10-20 Soraluce, S. Coop. System for compensating for the ram drop in a machine-tool
CN102380802A (zh) * 2011-11-03 2012-03-21 芜湖恒升重型机床股份有限公司 一种滑枕挠度变形补偿装置
CN105397559A (zh) * 2015-12-17 2016-03-16 齐齐哈尔二机床(集团)有限责任公司 一种套筒滚子链防断报警装置
CN107433454A (zh) * 2017-09-04 2017-12-05 沈机集团昆明机床股份有限公司 镗铣床的滑枕挠度补偿装置及镗铣床

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106182885B (zh) * 2016-07-15 2018-03-09 合肥工业大学 一种大吨位短行程单柱液压机滑块抗扭转装置
CN111515759A (zh) * 2020-05-29 2020-08-11 江西吉米立机械科技有限公司 一种天车式三轴龙门加工中心机

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2890629A (en) * 1953-12-01 1959-06-16 Giddings & Lewis Machine tool
US2912905A (en) * 1952-05-16 1959-11-17 Const De Machines Outils Et D Bracing device for overhanging machine member
US3097568A (en) * 1961-10-09 1963-07-16 Ingersoll Milling Machine Co Machine tool

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2912905A (en) * 1952-05-16 1959-11-17 Const De Machines Outils Et D Bracing device for overhanging machine member
US2890629A (en) * 1953-12-01 1959-06-16 Giddings & Lewis Machine tool
US3097568A (en) * 1961-10-09 1963-07-16 Ingersoll Milling Machine Co Machine tool

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4178834A (en) * 1977-06-23 1979-12-18 The Warner & Swasey Company Machine tool having deflection compensation for tool support arm
US20110255933A1 (en) * 2008-12-24 2011-10-20 Soraluce, S. Coop. System for compensating for the ram drop in a machine-tool
US9033627B2 (en) * 2008-12-24 2015-05-19 Soraluce, S. Coop. System for compensating for the ram drop in a machine-tool
CN102380802A (zh) * 2011-11-03 2012-03-21 芜湖恒升重型机床股份有限公司 一种滑枕挠度变形补偿装置
CN105397559A (zh) * 2015-12-17 2016-03-16 齐齐哈尔二机床(集团)有限责任公司 一种套筒滚子链防断报警装置
CN107433454A (zh) * 2017-09-04 2017-12-05 沈机集团昆明机床股份有限公司 镗铣床的滑枕挠度补偿装置及镗铣床
CN107433454B (zh) * 2017-09-04 2023-06-30 沈机集团昆明机床股份有限公司 镗铣床的滑枕挠度补偿装置及镗铣床

Also Published As

Publication number Publication date
BE643741A (en)van) 1964-05-29
DE1477348A1 (de) 1969-10-09
GB1039153A (en) 1966-08-17
CH418777A (fr) 1966-08-15

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