US3186249A - Carriage drive for machine tools - Google Patents

Carriage drive for machine tools Download PDF

Info

Publication number
US3186249A
US3186249A US283307A US28330763A US3186249A US 3186249 A US3186249 A US 3186249A US 283307 A US283307 A US 283307A US 28330763 A US28330763 A US 28330763A US 3186249 A US3186249 A US 3186249A
Authority
US
United States
Prior art keywords
nut
spindle
support
nuts
threads
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US283307A
Other languages
English (en)
Inventor
Lanzenberger Horst
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Application granted granted Critical
Publication of US3186249A publication Critical patent/US3186249A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • B23Q5/00—Driving or feeding mechanisms; Control arrangements therefor
    • B23Q5/54—Arrangements or details not restricted to group B23Q5/02 or group B23Q5/22 respectively, e.g. control handles
    • B23Q5/56—Preventing backlash
    • 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
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/2003—Screw mechanisms with arrangements for taking up backlash
    • F16H25/2006—Screw mechanisms with arrangements for taking up backlash with more than one nut or with nuts consisting of more than one bearing part
    • 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
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • F16H25/2209—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls with arrangements for taking up backlash
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
    • Y10T74/18576—Reciprocating or oscillating to or from alternating rotary including screw and nut
    • Y10T74/18728—Backlash
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19623—Backlash take-up
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/1987—Rotary bodies
    • Y10T74/19893—Sectional
    • Y10T74/19898—Backlash take-up
    • Y10T74/19902—Screw and nut

Definitions

  • An object of the present invention is the provision of the generally improved and more satisfactory drive of this kind.
  • Another object is the provision of a play-free drive which does not subject the lead screw of the drive spindle to excessive spring pressure or other excessive forces, as is done in many prior drives.
  • a further object is the provision of an improved drive so designed as to have freedom from play or backlash under the influence of relatively light springs, and without causing undesirable severe loading of any parts.
  • a still further object is the provision of a drive having means for relieving the play-eliminating or backlasheliminating feature or rendering it inoperative when desired, in a simple and effective manner.
  • FIG. 1 is a somewhat schematic longitudinal section through a drive in accordance with a first embodiment of the present invention
  • FIG. 2 is a view partly in section and partly in elevation, illustrating a fragment of the same
  • FIG. 3 is a view similar to FIG. 1, illustrating a second embodiment of the invention
  • FIG. 4 is a similar view of a third embodiment.
  • FIG. 5 is an elevation of part of the mechanism shown in FIG. 4, with surrounding parts omitted.
  • FIGS. 1 and 2 there is a feed spindle mounted rotatably in the support 12, but held against axial movement therein.
  • the feed spindle is driven from any suitable source, either by hand or by a motor, through a worm 14 meshing with a worm wheel 16 fixed to the spindle.
  • a worm 14 meshing with a worm wheel 16 fixed to the spindle.
  • the spindle is turned in one direction or the other, it is intended to produce feeding movement in one direction or the other of any suitable machine tool part, such as a carriage, indicated schematically and in general at 18.
  • the spindle 10 is developed as a ball roller spindle having the conventional helical ball race 11 receiving the balls 10a.
  • Two nuts 20 and 22 surround the spindle 10 and have interior helical ball races in which the balls 10a run.
  • the first nut 20 is rigidly connected to the carriage or other member 18 which is to be moved by rotation of the spindle 10, so that any axial 3,186,249 Patented June 1, 1965 movement transmitted by the spindle to the nut 20 is thereby transmitted also to the member 18.
  • the second nut 22 is slightly spaced axially from the first nut 20, and is mounted in a suitable cavity in the member 18for limited movement therein both rotatably and axially, although it will be apparent as the description proceeds that the nut 22 is always held in axial contact with its thrust bearing, so the nut does not actually move axially in practice.
  • the nut 22 needs no particular radial support in the member 18, since the balls running in the ball races of the spindle and the nut, respectively, will provide a sufiicient radial support for this nut.
  • the left end of the second nut 22 is connected by a bolt 26 to a bushing 28. Either directly or through the bushing 28, the left end of the nut bears on a thrust bearing 24 mounted in the carriage or driven member 18, so that any leftward movement of the nut 22 (along the feed spindle 10) is transmitted through the thrust bearing 24 to the carriage 18. Since the first nut 20 is fixed both axially and rotationally in the member 18, it is apparent that the member 18 constitutes, in effect, a cage or abutment means limiting the extent to which the two nuts may move axially away from each other, although the second nut 22 may turn to a limited extent on the thrust bearing 24.
  • the bushing 28 is provided at its right end with oblique flanks or steps 30 engaging suitable mating flanks or steps 32 of a bushing 36 which surrounds the nut 22 and is axially movable to a limited extent in a cavity in the surrounding member 18, but which is held against rotation therein, by means of the bolt 34 fixed in the member 18 and extending radially inwardly into a longitudinal or axial slot 40 formed in the bushing 36.
  • the bushing 36 is constantly urged in a leftward direction by spring means preferably formed by a series of annular leaf springs 38 which loosely surround the nut 22 and press leftwardly on the right end of the bushing 36 while reacting rightwardly against a shoulder on the carriage or other driven member 18, as shown.
  • the angle of inclination of the oblique flanks 3t) and 32 is slightly greater than What is called the self-locking angle, or angle or repose, so that the axial pressure of the bushing 36 in a leftward direction (caused by the springs 38) pressing the flanks 32 against the flanks 30, actually causes a rotary force or torque force on the bushing 28 and, of course, on the nut 22, since the nut is pinned to the bushing 28 to turn therewith.
  • the self locking angle, or angle of repose varies according to the character of the metal (or of the two metals if they are dissimilar) as well as upon the condition of lubrication between all associated moving parts, so it is desirable to make the angle of the teeth or flanks 30, 32 sufliciently great so that self-locking will not occur even under lubrication conditions which are less than normal or ideal.
  • This construction provides a relatively simple and inexpensive feed which is completely free from play or backlash, and yet does not impose excessive pressures on the lead screw of the feed spindle.
  • the nut 20 does not turn but is rigidly fastened in the driven member 18.
  • the second nut 22 constantly tends to rotate slightly, under the influence of the springs 38 producing axial pressure on the oblique flanks 30, thereby constantly keeping the nut 22 turned to a position in which it is tight on the threads or ball races of the feed Spindle 10, with the left end of the nut 22 hearing tightly on the thrust bearing 24. Rotation of the feed spindle in one direction (a clockwise direction if viewed from the right-hand end of FIG.
  • FIG. 3 A second embodiment of the invention is illustrated in FIG. 3.
  • the construction is similar in general to the first embodiment, but means are provided for relieving the rotary force or torque on the second nut, whenever, desired. This is helpful because it relieves unnecessary pressure and wear (even though slight) when operating the machine tool under conditions where freedom from play or backlash is not necessary, and also because this arrangement may be helpful in eliminating the extra resistance which is felt (particularly during a hand feeding operation) when the carriage moves from a worn part of the feed spindle to a less worn part.
  • FIG. 1 the lead screw was formed by ball races containing balls.
  • FIG. 3 illustrates the lead screw as being formed by screw threads 11a of trapezoidal cross section, sometimes called an Acme thread. Except for this difference in threads (which is immaterial, as above mentioned) the parts in the second embodiment contain all the features above described in connection with the first embodiment, and operate in the same way, the corresponding parts being designated by the same reference numerals used in the first embodiment.
  • the second embodiment has the further feature of means for relieving the axial pressure of the bushing 36 against the inclined flanks 30 of the bushing 28, whenever desired.
  • annular nut 44 loosely surrounding the feed spindle 10 and having external screw threads 45 engaging internal screw threads in an annular cavity at the left end of the carriage 18.
  • this nut 44 can be turned so as to screw it further into or out of the left end of the carriage 18.
  • the pins 46 When screwed in an inward direction, it presses against the left ends of the pins 46 movable axially in suitable bores in the carriage 18, and presses the right ends of these pins against a leftwardly faced shoulder of the bushing 36, thereby displacing the bushing rightwardly against the force of the springs 38, and relieving the pressure of the oblique flanks 32 on the oblique flanks 30.
  • this feature of the invention may be used with a spindle having any type of thread or lead screw.
  • this feature of relieving the pressure tending to rotate the second nut is particularly valuable and useful with a spindle of the sliding thread type as distinguished from the ball roller thread type, since the resistance when moving from a worn part of the spindle to a less worn part is particularly severe with a sliding thread.
  • FIGS. 4 and 5 A third embodiment of the invention is illustrated in FIGS. 4 and 5.
  • the feed spindle is shown at 48, and is provided with a feeding or lead screw thread 49 of any suitable kind, such as the trapezoidal or Acme thread illustrated, only part of the length of the thread being shown in FIG. 4 in order to simplify the drawing.
  • the thread will, of course, extend through a greater part of the length of the spindle 48, than illustrated.
  • the thread was of the non-self-locking type, but in this third embodiment the proportions of the thread are preferably such that it is a self-locking thread.
  • the feeding motion to be performed in this embodiment of the invention is a relative motion between the support 18a and the spindle 4S, and the motion is secured in this instance, not by turning the spindle, but by turning the nuts around the spindle. It does not matter whether the support 18a is held stationary and the spindle 48 travels longitudinally or axially through the support, or whether the spindle is held axially stationary and the support 18a moves bodily along it, since it is a matter of a relative feeding motion in either case.
  • the threads of the spindle carry two nuts 20a and 22a, serving in principle like the nuts 20 and 22 in the previous embodiments. These nuts are mounted Within the support 18a, and each nut is held against axial movement in one direction relative to the support 18a.
  • the nut 20a reacts rightwardly against a thrust bearing 52 in the support 1801, and the other nut 22a reacts leftwardly against a thrust bearing 54 in the support, these thrust bearings thus serving to limit the extent to which the two nuts may move axially away from each other.
  • the left face of the right-hand nut 20a is provided with a circumferentially extending series of inclined or oblique flanks 3th: which mate with corresponding inclined or oblique flanks 32a at the right end of the sleeve 36a which surrounds the right end of the left nut 22a and is splined thereto at 40, so that the sleeve 36a can move longitudinally or axially on the nut 22a, to the necessary extent, but cannot turn thereon.
  • the inclined flanks 36a and 32a in the present embodiment are inclined at a suflicient angle so that they are not self-locking. As before, the angle should be close to the self-locking angle, but sufficiently greater than the self-locking angle so that there will not be a selflocking action even if the lubrication is poor.
  • the sleeve 36a is constantly pressed rightwardly, into contact with the flanks 30a, by the nest or series of annular leaf springs 56 which correspond in general to the leaf springs 38 in the first embodiment.
  • These leaf springs surround the nut 22a, just to the left of the sleeve 36a, and press rightwardly on the left end of the sleeve 36a, reacting leftwardly against a collar 57 screwed on the perimeter of the nut 22a, the collar advantageously serving also to retain one side of the thrust bearing 54.
  • Both nuts 20a and 22a are rotatable within the housing or support 18a, and are respectively supported radially by suitable bearings such as the roller bearings 20c and 220, respectively.
  • the nut 20a is keyed or otherwise non-rotatably connected to a gear 58, and the other nut 22a is similarly connected to a second gear 60.
  • the nuts are driven, when relative motion of the parts is required, from a drive shaft 62 which is mounted for rotation in the support 18a, on an axis substantially parallel to the spindle 48, and which is driven in any suitable conventional manner, either by hand or by motor.
  • Rotatable on the shaft 62 is a pinion 64 which meshes at all times with the gear 58, and a second pinion 66 which meshes at all times with the gear 60.
  • the respective pinions 64 and 66 are operatively con nected to the shaft 62, to he turned thereby, by suitable conventional means which will cause driving torque to be applied to one pinion when the shaft 62 is turned in one direction and to the other pinion when the shaft is turned in the opposite direction.
  • suitable conventional means may take the form of a conventional electromagnetic change-over clutch, or may be in the form of a pair of conventional one-way roller clutches respectively indicated schematically at 68 and 70, the inner drive ring of each oneway clutch being formed as part of or mounted non- 'which carries the pinions 64 or 66, respectively.
  • two one-way clutches 68 and 70 are arranged to transmit torque in opposite directions, so that when the drive shaft 62 is turned in one direction the clutch 68 will drive the sleeve '72 and pinion 64, and when the shaft 62 is turned in the opposite direction, the clutch 70 will drive the sleeve 74 and pinion 66.
  • the directions of the clutches should be such that they will transmit torque to turn the respective gears 58 and 60, as the case may be, in directions which will turn the immediately driven nut (26a and 22a, as the case may be) in a direction to relieve the pressure of its flanks against the flanks of the screw thread 49 on the spindle 48.
  • the other nut (that is, the nut which is not immediately driven through the appropriate roller clutch or one-way clutch) will then be driven from the first nut by torque transmitted through the oblique flanks 30a and 32a, and will cause the required relative movement between the support 13a and the spindle 4-8, without play or backlash.
  • the drive shaft 62 is turned in a counterclockwise direction when viewed from the right side of FIG. 4, and the clutch 68 is the one which should be operative at this time, causing corresponding driving in a counterclockwise direction of the pinion 64, thereby driving the gear 53 in a clockwise direction when viewed from the right end of FIG. 4.
  • This will cause corresponding clockwise rotation of the first nut 20a, and it will he noted from the direction of the screw threads 49 as seen in FIG.
  • the drive shaft 62 is turned in the opposite or clockwise direction when viewedfrom the right end of FIG. 4, and this time the one-way clutch 70 will be operative to turn the gear 6% in a counterclockwise direction, similarly turning the nut 22a which will thereby relieve its pressure on the threads 49.
  • the rotation of the nut 22a will be transmitted through the sleeve 36a and the oblique flanks 32a and 30a, to the nut 20a, and the action of this nut will press leftwardly on the threads 49, moving the spindle 48 in a leftward direction relative to the support 18a.
  • the angle of inclination of the oblique flanks of the bushing or sleeve, which tend to turn one of the nuts to take up the play is made close to the self-locking angle.
  • the spring force is design d to be sufficient for the active or effective portion of the cutting force in the case of parallel milling or down-cut milling, it will in general also be suflicient for carrying out profiling work or copying work without reversing error or backlash, since normally the active portions of the feeding forces in profiling work, even in the conventional milling phase, will be smaller than the corresponding portions of the cuttingforce in parallel milling or down-cut milling, in view of the slight rigidity of the profiling members.
  • each nut is directly driven only in a direction which will relieve the pressure of the flanks 8 of the nut from the flanks of the lead screw on the spindle, being driven in the opposite direction only indirectly through the other nut and the oblique flanks of the sleeve or bushing.
  • relieving one nut from pressure against the lead screw one avoids the nuts becoming locked with respect to each other.
  • the drive of the nuts may contain an electromagnetic change-over clutch which connects the proper nut to the commondrive shaft, depending upon the direction of rotation of the drive shaft, or this can be accomplished by a pair of one-way clutches mounted to become effective in opposite directions of rotation, which is the specific form disclosed in connection with FIG. 4.
  • the teeth of the driving pinions 64 and 66, respectively is taken up or compensated for by the same spring mechanism which compensates for play or backlash of the nuts on the spindle, with a minimum of clamping force.
  • the angle of inclination or pitch angle of the oblique nonself-locking flanks 30a and 32a should be made somewhat greater than the angle of inclination used when the lead screw is not self-locking, because the occurrence or possibility of self-locking in this construction depends, in addition, upon the friction between the respective gears 58, 65 and 6t), 66.
  • a play-free drive for machine tools comprising a support and a threaded spindle movable relative to each other in a direction longitudinally of the spindle and two threaded nuts operatively connected to the support and engaging the threads of the spindle and bearing against the spindle threads in opposite directions, characterized by stop means for limiting axial movement of the nuts relatively to each other, oblique flanks on one of said nuts, a sleeve surrounding and movable axially on one of said nuts, oblique flanks on said sleeve for mating with the oblique flanks on said one of said nuts, and spring means tending to move said sleeve axially in a direction to press its oblique flanks against the oblique flanks on said one of the nuts to tend to turn said nut which has the oblique flanks, in a direction to cause such nut to become tight on the threads of the spindle and to press axially against said stop means, said stop means
  • said clutch means comprises vyo uni-directional roller clutches, one eflective to transmit torque in one direction and the other eifective to transmit torque in the opposite direction.
  • first nut is rigidly mounted in said support and the second nut is mounted in said support for limited axial and rotary movement therein, and in which said sleeve surrounds and is movable axially on said second nut, further including means holding said sleeve against rotation relative to said support.
  • said means for nullifying the force of said spring means comprises an annular screw threaded member and a plurality of pins moved axially by said threaded member and pressing axially against said sleeve to move said sleeve against the force of said spring means.
  • said means for nullifying the force of said spring means comprises an annular screw threaded member and a plurality of pins moved axially by said threaded member and pressing axially against said sleeve to move said sleeve against the force of said spring means.
  • a machine tool feed drive free from play comprising a support and a screw-threaded spindle capable of feeding movement relatively to each other in either direction longitudinally of said spindle, a first nut mounted for rotation in said support and engaging the threads of said spindle, a second nut also mounted for rotation in said support in axially spaced relation to the first nut and also engaging the threads of said spindle, thrust bearings operatively interposed between said nuts and said support to limit the extent to which said nuts may move axially relative to each other, and means tending to turn the two nuts relative to each other in opposite directions effective to tighten the nuts against the respective thrust bearings and against the threads of the spindle.
  • a machine tool feed drive free from play comprising a support and a screw-threaded spindle capable of feeding movement relatively to each other in either direction longitudinally of said spindle, a first nut mounted for rotation in said support and engaging the threads of said spindle, a second nut also mounted for rotation in said support in axially spaced relation to the first nut and also engaging the threads of said spindle, thrust bearings operatively interposed between said nuts and said support to limit the extent to which said nuts may move axially relative to each other, and means tending to turn the two nuts relative to each other in opposite directions effective to tighten the nuts against the respective thrust bearings and against the threads of the spindle, said means tending to turn the two nuts relative to each other including oblique jaw teeth on the first nut facing obliquely toward the second nut, a sleeve mounted on the second nut for axial sliding movement thereon and held against rotation relative thereto, said sleeve having oblique jaw teeth mating with
  • a machine tool feed drive free from play comprising a support and a screw-threaded spindle capable of feeding movement relatively to each other in either direction longitudinally of said spindle, a first nut mounted stationarily in said support and engaging the threads of said spindle, a second nut mounted for limited rotation in said support in axially spaced relation to the first nut and also engaging the threads of said spindle, a thrust bearing operatively interposed between said second nut and said support to limit the extent to which said nuts may move axially relative to each other, and means tending to turn the second nut relative to the support and the first nut in a direction effective to tighten the second nut against said thrust bearing and against the threads of the spindle.
  • a machine tool feed drive free from play comprising a support and a screw-threaded spindle capable of feeding movement relatively to each other in either direction longitudinally of said spindle, a first nut mounted stationarily in said support and engaging the threads of said spindle, a second nut mounted for limited rotation in said support in axially spaced relation to the first nut and also engaging the threads of said spindle, a thrust bearing operatively interposed between said second nut and said support to limit the extent to which said nuts may move axially away from each other, and means tending to turn the second nut relative to the support and the first nut in a direction effective to tighten the second nut against said thrust bearing and against the threads of the spindle, said means tending to turn the second nut including oblique jaw teeth on the second nut, a sleeve mounted on the second nut for axial sliding movement thereon and held against rotation relative to said support, said sleeve having oblique jaw teeth mating with the jaw

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Gears, Cams (AREA)
  • Gear Transmission (AREA)
US283307A 1962-05-30 1963-05-27 Carriage drive for machine tools Expired - Lifetime US3186249A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DED39053A DE1301218B (de) 1962-05-30 1962-05-30 Spielausgleicheinrichtung fuer den Support einer Werkzeugmaschine

Publications (1)

Publication Number Publication Date
US3186249A true US3186249A (en) 1965-06-01

Family

ID=7044506

Family Applications (1)

Application Number Title Priority Date Filing Date
US283307A Expired - Lifetime US3186249A (en) 1962-05-30 1963-05-27 Carriage drive for machine tools

Country Status (4)

Country Link
US (1) US3186249A (de)
CH (1) CH416267A (de)
DE (1) DE1301218B (de)
GB (1) GB1007512A (de)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3372605A (en) * 1965-10-19 1968-03-12 Orner Harry Ball-bearing screw and nut mechanism
US3393575A (en) * 1966-05-31 1968-07-23 Trw Inc Ball screw actuator
US3393576A (en) * 1966-05-31 1968-07-23 Trw Inc Ball screw actuator
US3479897A (en) * 1967-08-16 1969-11-25 Saginaw Products Corp Variably preloaded ball nut and screw assembly
EP0060705A3 (en) * 1981-03-16 1983-07-27 Oki Electric Industry Company, Limited Carrier moving mechanism
US4872795A (en) * 1988-09-09 1989-10-10 Dana Corporation Nut assembly with rotatable sleeve for taking up backlash
US5467661A (en) * 1994-04-25 1995-11-21 Thomson Saginaw Ball Screw Company, Inc. Ball nut and screw assembly with backdrive control
DE19718731A1 (de) * 1997-05-02 1998-11-12 Conrad Apparatebau Gmbh Linearführung für ein wechselnden Beanspruchungen unterworfenes Bauteil
US5839321A (en) * 1997-05-16 1998-11-24 Ball Screw & Actuators Co. Backlash compensating assembly
US5906133A (en) * 1997-12-10 1999-05-25 Trw Inc. Lash adjustment assembly
US20040011153A1 (en) * 2002-04-15 2004-01-22 John Drake Internal recirculating ball screw and nut assembly
WO2006044698A3 (en) * 2004-10-13 2007-01-04 Tritex Corp Spiral compression anti-backlash nut
US20070258789A1 (en) * 2004-10-01 2007-11-08 Michael Bogue Antiback-Lash Nut
EP1637771A3 (de) * 2004-09-16 2007-11-21 KN Karl Neff Dienstleistungen Gewindetrieb
US20070277638A1 (en) * 2006-04-27 2007-12-06 William Kirk Screw Drive with an Antibacklash Mechanism and Method of Preventing Backlash in a Screw Drive
CN102139331A (zh) * 2010-12-31 2011-08-03 江苏亚威机床股份有限公司 一种折弯机上的板料定位装置
CN102528526A (zh) * 2012-01-11 2012-07-04 江苏高精机电装备有限公司 可伸缩式摆动镗铣头
US9279487B1 (en) * 2009-09-30 2016-03-08 David B. Guglietti Ball screw and parts
US10857912B2 (en) * 2017-09-29 2020-12-08 Faurecia Sièges d'Automobile Screw-based adjustment mechanism, rail comprising such an adjustment mechanism, and seat comprising such a rail

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2132310A (en) * 1982-12-23 1984-07-04 Yiu Ming Cheng Machine tool apparatus
DE4112350A1 (de) * 1991-04-16 1992-01-02 Erwin Palige Kugelrollspindellaeufer-motor
DE102005061613B4 (de) * 2005-12-21 2007-10-04 Ehinger Giesserei Und Werkzeugmaschinenfabrik Gmbh Werkzeugmaschine zum Bearbeiten von Verzahnungen
CN112503148A (zh) * 2020-11-19 2021-03-16 中国科学院上海光学精密机械研究所 一种可调预压的精密导向丝杆位移机构

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2224257A (en) * 1936-10-08 1940-12-10 Wanderer Werke Vorm Winklhofer Mechanism for eliminating backlash
US2328732A (en) * 1942-12-02 1943-09-07 Mckinney Tool And Mfg Company Universal backlash prevention device
US2385194A (en) * 1944-07-31 1945-09-18 Lockheed Aireraft Corp Device for eliminating backlash
US2919596A (en) * 1958-02-24 1960-01-05 Gorton George Machine Co Anti-backlash nut

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2205634A (en) * 1939-08-05 1940-06-25 Associated Patents Inc Screw and nut driving connection

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2224257A (en) * 1936-10-08 1940-12-10 Wanderer Werke Vorm Winklhofer Mechanism for eliminating backlash
US2328732A (en) * 1942-12-02 1943-09-07 Mckinney Tool And Mfg Company Universal backlash prevention device
US2385194A (en) * 1944-07-31 1945-09-18 Lockheed Aireraft Corp Device for eliminating backlash
US2919596A (en) * 1958-02-24 1960-01-05 Gorton George Machine Co Anti-backlash nut

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3372605A (en) * 1965-10-19 1968-03-12 Orner Harry Ball-bearing screw and nut mechanism
US3393575A (en) * 1966-05-31 1968-07-23 Trw Inc Ball screw actuator
US3393576A (en) * 1966-05-31 1968-07-23 Trw Inc Ball screw actuator
US3479897A (en) * 1967-08-16 1969-11-25 Saginaw Products Corp Variably preloaded ball nut and screw assembly
EP0060705A3 (en) * 1981-03-16 1983-07-27 Oki Electric Industry Company, Limited Carrier moving mechanism
US4872795A (en) * 1988-09-09 1989-10-10 Dana Corporation Nut assembly with rotatable sleeve for taking up backlash
US5467661A (en) * 1994-04-25 1995-11-21 Thomson Saginaw Ball Screw Company, Inc. Ball nut and screw assembly with backdrive control
DE19718731A1 (de) * 1997-05-02 1998-11-12 Conrad Apparatebau Gmbh Linearführung für ein wechselnden Beanspruchungen unterworfenes Bauteil
DE19718731C2 (de) * 1997-05-02 2002-06-27 Conrad Appbau Gmbh Linearführung für ein wechselnden Beanspruchungen unterworfenes, rotierendes Bearbeitungswerkzeug
US5839321A (en) * 1997-05-16 1998-11-24 Ball Screw & Actuators Co. Backlash compensating assembly
US5906133A (en) * 1997-12-10 1999-05-25 Trw Inc. Lash adjustment assembly
US20040103734A9 (en) * 2002-04-15 2004-06-03 John Drake Internal recirculating ball screw and nut assembly
US7013747B2 (en) 2002-04-15 2006-03-21 White Stroke Llc Internal recirculating ball screw and nut assembly
US20040011153A1 (en) * 2002-04-15 2004-01-22 John Drake Internal recirculating ball screw and nut assembly
EP1637771A3 (de) * 2004-09-16 2007-11-21 KN Karl Neff Dienstleistungen Gewindetrieb
US7841251B2 (en) 2004-10-01 2010-11-30 Tritex Corporation Antiback-lash nut
US20070258789A1 (en) * 2004-10-01 2007-11-08 Michael Bogue Antiback-Lash Nut
WO2006044698A3 (en) * 2004-10-13 2007-01-04 Tritex Corp Spiral compression anti-backlash nut
US20070277638A1 (en) * 2006-04-27 2007-12-06 William Kirk Screw Drive with an Antibacklash Mechanism and Method of Preventing Backlash in a Screw Drive
US9279487B1 (en) * 2009-09-30 2016-03-08 David B. Guglietti Ball screw and parts
CN102139331A (zh) * 2010-12-31 2011-08-03 江苏亚威机床股份有限公司 一种折弯机上的板料定位装置
CN102139331B (zh) * 2010-12-31 2016-02-17 江苏亚威机床股份有限公司 一种折弯机上的板料定位装置
CN102528526A (zh) * 2012-01-11 2012-07-04 江苏高精机电装备有限公司 可伸缩式摆动镗铣头
CN102528526B (zh) * 2012-01-11 2013-10-30 江苏高精机电装备有限公司 可伸缩式摆动镗铣头
US10857912B2 (en) * 2017-09-29 2020-12-08 Faurecia Sièges d'Automobile Screw-based adjustment mechanism, rail comprising such an adjustment mechanism, and seat comprising such a rail

Also Published As

Publication number Publication date
DE1301218B (de) 1969-08-14
CH416267A (de) 1966-06-30
GB1007512A (en) 1965-10-13

Similar Documents

Publication Publication Date Title
US4542661A (en) Rotary-to-linear converter with rolling balls, and two-speed feed mechanism incorporating the same
US3803927A (en) Coaxial force and movement mechanism for a machine tool
US4322986A (en) Variable ratio rack and pinion gear
US3094011A (en) Motion transmission mechanism of the screw and nut type
US2385194A (en) Device for eliminating backlash
US3543598A (en) Driving means for vertical ball-roll spindles
US4317511A (en) Overload release clutch
US3498153A (en) Steering gear with rotary ball nut
US3932961A (en) Grinding machine
US3659474A (en) Worm gear for driving machine-tool slides, in particular in milling machines
US3119307A (en) Automatic backlash eliminator
US3640024A (en) Device for adjusting the position of a grinding wheel relative to a workpiece
US3350952A (en) Arrangement for conveying power in a play-free manner from the main drive of chip-removing machine tools
US2905008A (en) Means for preloading a ball spline assembly
US2653691A (en) Antifriction screw reversible brake mechanism
US1955954A (en) Back-lash compensator
US3124998A (en) raehrs
GB481507A (en) Milling machine
GB1364423A (en) Automatic adjusters
US2760397A (en) Precision adjustment means for power machines
US2959976A (en) Backlash eliminator
US2002991A (en) Backlash remover
US3031897A (en) Machine tool anti-backlash motion transmitting mechanism
US2995958A (en) Rotatable tool-holder or work-holder for a machine-tool
US1718469A (en) Device for taking up the play in gears