US3636789A - Gear drive with means for the removal of the play of the toothed profile - Google Patents

Gear drive with means for the removal of the play of the toothed profile Download PDF

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Publication number
US3636789A
US3636789A US75352A US3636789DA US3636789A US 3636789 A US3636789 A US 3636789A US 75352 A US75352 A US 75352A US 3636789D A US3636789D A US 3636789DA US 3636789 A US3636789 A US 3636789A
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US
United States
Prior art keywords
drive
gears
gear
shaft
double
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
US75352A
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English (en)
Inventor
Manfred Geiger
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.)
Rheinmetall Industrie AG
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Rheinmetall GmbH
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Publication of US3636789A publication Critical patent/US3636789A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F41—WEAPONS
    • F41A—FUNCTIONAL FEATURES OR DETAILS COMMON TO BOTH SMALLARMS AND ORDNANCE, e.g. CANNONS; MOUNTINGS FOR SMALLARMS OR ORDNANCE
    • F41A27/00—Gun mountings permitting traversing or elevating movement, e.g. gun carriages
    • F41A27/06—Mechanical systems
    • F41A27/18—Mechanical systems for gun turrets
    • F41A27/20—Drives for turret movements
    • 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
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • 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
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/121—Arrangements for adjusting or for taking-up backlash not provided for elsewhere using parallel torque paths and means to twist the two path against each other
    • 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
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/126—Self-adjusting during operation, e.g. by a spring
    • F16H2057/127—Self-adjusting during operation, e.g. by a spring using springs
    • 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

Definitions

  • ABSTRACT A gear drive with means for removal of the play of the toothed profile, in particular laying mechanism for armored turrets, rotary ring gun carriages or the like of weapons, which comprises a double pinion shaft axially displaceable by means of a pressure medium and equipped with oblique toothing of opposite spiral directions including pinions of equal size.
  • Counter gears are coaxially disposed and mounted independently from each other.
  • the pinions are in mesh at least directly with the counter gears.
  • Each of the counter gears are connected each with a further gear by means of a shaft.
  • the further gears are of equal size and disposed directly adjacent each other.
  • a still further counter gear is disposed outside of the drive housing, and the further gears mesh as driven gears jointly the still further gears.
  • the present invention relates to a gear drive with means for the removal of the play of the toothed profile, in particular, laying mechanism for armored turrets, rotary-ring gun carriages or the like of weapons.
  • the perfect working of laying mechanism (height and/or side), in particular, with stabilizing devices depends extensively from the play-free transmission of the rotary movement of the driving motor over the laying mechanism to the turret or the gun carriage.
  • Drives are also known, in which a radially divided worm is in mesh with a counter gear, whereby the one-half of the worm is rigidly connected with a shaft, while the other half of the worm is axially displaceable on this shaft and is disposed capable of being arrested by nuts.
  • Drives are known likewise with output division, in which a pinion of the driving shaft meshes with a gear of the driven shaft and simultaneously a second pinion, axially displaceable on the driving shaft, obliquely toothed and capable of being arrested by nuts, with a correspondingly obliquely toothed spur gear and rigidly secured with the driven shaft.
  • the perfect operation depends extensively from the play-free transmission of the rotary movement from the driving motor over the laying mechanism to the turret and, the gun carriage.
  • the drives used before particular requirements are made to the surface quality of the toothed profiles, as well as the maintenance of smallest tolerances in the gear production,in order to reduce to a minimum the play of the tooth profiles of the individual drive steps.
  • the largest play of the tooth profiles occurs, however, of necessity by the summary of theindividual plays within the drive between the driving gear and the counter gear, which is mostly designed as a tooth segment and a tooth ring, respectively, thus outside of the actual laying mechanism. Jointly with rotary errors of the toothing in tooth segments and tooth rings, respectively, and by mounting errors, the play of the toothed profile can amount up to several tenths of a millimeter.
  • the teeth of the one gear are pressed into the tooth gaps of the counter gear such, that a'high friction force, a strong wear at the teeth between the driven part andthe drive of the turret and of the gun carriage drive, respectively, and also a heavy run of thedrive is created, which makes itself recognizable in particular in case of a low number of revolutions, for example, during fine laying, disadvantageously in case of sudden movements.
  • a drive designed in this manner stands by use of a suitable pressure medium for the axial displacement of the doublepinion shaft with continuous play freedom with the gear and tooth ring, respectively, to be driven and warrants a quiet run which is low on noise and low on friction even under extreme operational conditions.
  • a laying mechanism of the type in accordance with the present invention in view of. the narrow space conditions in weapons in their outer dimensions, in accordance with a further feature of the present invention, of the two coaxial counter gears, one is secured to a solid shaft and the other to a hollow shaft surrounding this solid shaft, whereby the driven gears are disposed at the ends projecting from the driving housing.
  • the pressure medium for the axial displacement of the double pinion shaft is a spring, which supports itself, on the one hand, on the doublepinion shaft and, on the other hand, on a bushing threaded with the driving housing and surrounding the spring.
  • This spring can be designed, by example, as a helical pressure spring or as a cup spring package.
  • the spring force by example, the helical pressure spring is settable for the axial displacement of the doublepinion shaft by means of threaded bushing. A securing against nonintended loosening or setting of the threaded bushing can be provided thereby in addition.
  • the drive can be driven by a hydraulic or pneumatic driving motor, which is connected by means of a conduit with a cylinder secured to the drive housing, in which a piston is subjected to a pressure medium on the cylinder side and engages on the drive side the double-pinion shaft.
  • the double-pinion shaft can be driven in addition also by means of one or a plurality of spur gear steps, which in turn are likewise designed play-free in known manner.
  • the drive can thereby take place by a loose gear joining the movement on a shaft, which gear is put to a rotational movement on the driving side by means of a spur gear and transmits this rotary movement to another spur gear, which is rigidly connected with the double-pinion shaft and whereby the connecting line between the three axle center points result in a triangle.
  • the play freedom of this driving step prearranged to the double-pinion shaft takes place such, that the shaft of the loosely rotating gear is mounted floatingly and is designed to be movable by one or a plurality of screws to the driving axle and to the axle of the double-pinion shaft and in play-free engagement of the two profiles are designed securably in this position.
  • FIG. 1 is a longitudinal or axial section of a two-stepped drive designed in accordance with the present invention
  • FIG. 2 is a fragmentary axial section of the drive disclosed in FIG. 1, in which the double-pinion shaft is axially displaced by means of a spring;
  • FIG. 3 is a schematic showing at an enlarged scale of the play-free engagement of the driven gears meshing with a counter gear
  • FIG. 4 is a fragmentary elevation, partly in section, indicating the displacing of the double-pinion shaft in accordance with FIG. 1, however, by means of a hydraulic or pneumatic medium;
  • FIG. 5 is an axial section of a preferred embodiment indicating a four-step drive in an arrangement similar to that shown in FIG. 1;
  • FIG. 6 is a side elevation of the embodiment in accordance with FIG. 5 seen in the direction of the arrow, the housing end wall being partly broken away, for the purpose of a better demonstration.
  • the gear drive designed in accordance with the present invention comprises a drive housing 1 in which a double-pinion shaft 2 is mounted.
  • the latter is driven over a knurled toothing 20 by means of a handwheel or a motor (not shown) and on which two pinions 2b and 2c of equal size and with equal oblique toothing disposed in opposite spiral directions are rigidly arranged.
  • the double-pinion shaft 2 is designed displaceably in axial direction by means of a helical pressure spring 3.
  • the spring 3 which does not participate in a rotary movement of the shaft 2, supports itself thereby, on the one hand, by means of a spring plate 4 and a ball bearing 5 at a collar of the double-pinion shafi and, on the other hand, on a threaded bushing 6, which is screwable onto a flange formed on the drive housing.
  • the pinion 2b meshes with a spur gear 8 secured to the solid shaft 7.
  • the shaft 7 is mounted by means of a ball bearing 9 inside of the drive housing and by means of a second ball bearing 10 outside of the drive housing to an arm 11 rigidly connected with the drive housing.
  • a gear 12 characterized as a driven pinion is mounted at the end of the shaft 7 projecting from the drive housing, which gear 12 is screwed to a flange 13 formed on the shaft 7.
  • the pinion 2c stands in mesh with a spur gear 14 which is secured to a hollow shaft 15 surrounding the solid shaft 7, which hollow shaft 15 in turn is mounted by means of ball bearings 16 and 17 within the drive housing.
  • the gear 18 At the end of the hollow shaft 15 on the output side is secured the gear 18 corresponding with the gear 12.
  • Both driven gears 12 and 18 engage a counter gear 19 which is directly connected with a laying device.
  • FIG. 4 shows in contradiction to FIG. 2, the possibility of axial displacement in accordance with FIG. 1, however, by means of a hydraulic or pneumatic medium.
  • a drive motor 21 is driven by means of a conduit 20.
  • the return flow of the driving means takes place through a conduit 22.
  • a special valve 23 which is settable in known manner, the direction of rotation of the motor 21 can be reversed.
  • From the conduit 20 branches a conduit 24 which terminates by means of a control valve 25 in a cylinder 26 closed on one side and flanged to the drive housing 101 and in which cylinder 26 is disposed a piston 27, which presses by means of the pressure means 28 over a ball bearing to the double-pinion shaft 102 guided in the drive housing 101.
  • the double-pinion shaft 102 engages with its oppositely obliquely toothed pinions 102k and 1020 in correspondingly toothed counter gears 108 and 114, which correspond with the gears 8 and 14 in FIG. 1 and leads to the driven part of the drive, whereby the double-pinion shaft 102 is connected by means of the knurl toothing 102a forcibly with the motor 21.
  • a limit of the axial stroke of the piston 27 is obtained by a collar 101a, which projects into the cylinder 26 from the driving side.
  • FIGS. 5 and 6 show in contradiction to FIG. 1 a fourstep drive, however, with the same effect as in connection with the device disclosed in FIG. 1.
  • a pinion shaft 30 mounted in the drive housing 29 drives with its straight toothed pinion 30a by means of a spur gear 31 a spur gear 33 secured to a double-pinion shaft 32.
  • the double-pinion shaft 32 is, in the same manner as shown in the embodiment of FIG. 1, under the influence of a spring 34, the pressure force of which is settable by means of a threaded bushing 35 threaded with the drive housing 29, and displaceable in axial direction. Concerning the operation of the spring, reference is made to the description of FIG. 1.
  • the spur gear 31 is movable with its shaft in a guide (not shown) radially in the direction towards the pinion 30a and the spur gear 33 is movable by means of a setscrew 36 and after play-free engagement of the toothed profiles of the mentioned gears securable by means of a counter nut 37 in this position.
  • the drive takes place from the double-pinion shaft 32 over the oppositely obliquely toothed pinions 32a and 32b to correspondingly toothed spur gears 38 and 39, which are connected each with a pinion 40 and 41.
  • the pinion 32a meshes with a spur gear 43 secured'to the solid shaft 42 by means of the drive step 38 and 40.
  • the shaft 42 is mounted by means of a ball bearing 44 inside of the drive housing and by means of a second ball bearing 45 outside of the drive housing in an arm 46 rigidly connected with the drive housing.
  • a gear 47 is mounted which is characterized as a driven pinion, which gear 47 is screwed to a flange 48 formed on the shaft 42.
  • the pinion 32b is in mesh with a spur gear 49 by means of the drive step 39 and 41.
  • This wheel 49 is secured on a hollow shaft 50 surrounding the solid shaft 42, which hollow shaft 50 in turn is mounted within the drive housing by means of ball bearings 51 and 52.
  • a gear 53 is secured on the end of the hollow shaft 50 at the output side of the drive a gear 53 corresponding with the gear 47, Both driven gears 47 and 53 engage jointly in a gear rim 54 which runs on a wire ball bearing 55.
  • said pinions being in mesh at least directly with said counter gears
  • each of said counter gears being connected each with a further gear by means of a shaft
  • said further gears being of equal size and disposed directly adjacent each other
  • one of said coaxial counter gears is secured to said solid shaft, and the other of said coaxial counter gears is secured to said hollow shaft, and
  • said spring supports itself on said double-pinion shaft at one end and on a threaded bushing screwed to the drive housing and surrounding said spring at the other end.
  • the gear drive as set forth in claim 1, which includes a pressure-fluid driven drive motor
  • a piston movable in said cylinder and subjected on the cylinder side to a pressure fluid and engages on the drive side said double-pinion shaft.
  • said drive is designed play-h e.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Gears, Cams (AREA)
US75352A 1969-10-18 1970-09-25 Gear drive with means for the removal of the play of the toothed profile Expired - Lifetime US3636789A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691952545 DE1952545A1 (de) 1969-10-18 1969-10-18 Stirnradgetriebe mit Mitteln zur Beseitigung des Zahnflankenspiels

Publications (1)

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US3636789A true US3636789A (en) 1972-01-25

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US75352A Expired - Lifetime US3636789A (en) 1969-10-18 1970-09-25 Gear drive with means for the removal of the play of the toothed profile

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Country Link
US (1) US3636789A (fr)
BE (1) BE757592A (fr)
CH (1) CH536447A (fr)
DE (1) DE1952545A1 (fr)
FR (1) FR2066030A5 (fr)
GB (1) GB1320735A (fr)
NL (1) NL7014364A (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4036074A (en) * 1975-10-01 1977-07-19 Bodnar Ernest R Anti-backlash gear system
US4331040A (en) * 1980-04-21 1982-05-25 Usm Corporation Anti-backlash gearing
US4417482A (en) * 1982-02-08 1983-11-29 The Falk Corporation Diaphragm mounted gear drive detuner
US4441401A (en) * 1982-09-27 1984-04-10 Ex-Cell-O Corporation Rack and pinion weapon elevation mechanism
US4719813A (en) * 1983-10-28 1988-01-19 Lazar Chalik Gear assembly
US5257543A (en) * 1992-09-03 1993-11-02 Borg-Warner Automotive, Inc. Gear transmission with an anti-rattle system
CN1117227C (zh) * 1997-12-30 2003-08-06 梅勒菲尔股份有限公司 传动设备
US20060205557A1 (en) * 2002-11-22 2006-09-14 Joachim Arndt Method for effecting low-loss torque transmission in planetary gears
CN105221673A (zh) * 2015-11-05 2016-01-06 中国船舶重工集团公司第七二四研究所 一种双传动链零齿隙行星齿轮减速器
US20200025502A1 (en) * 2009-03-31 2020-01-23 Npc Robotics Corporation Motor-less cartridge ring gear engagement module for actuating rotation of a turret
CN114378363A (zh) * 2022-01-27 2022-04-22 福建恒而达新材料股份有限公司 自适应消隙齿轮箱及圆锯机
US11391357B2 (en) * 2019-07-30 2022-07-19 Industrial Technology Research Institute Adjustment device for bevel gear, automatic adjustment system for bevel gear and adjustment methods for bevel gear

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT337742B (de) * 1974-12-09 1977-07-11 Voest Ag Einrichtung zur verhinderung der ubertragung von konverterschwingungen
DE2940323C2 (de) * 1979-10-04 1983-12-29 BHS-Bayerische Berg-, Hütten- und Salzwerke AG, 8000 München Doppelschrägverzahntes, zweistufiges Stirnrädergetriebe
US4554842A (en) * 1983-04-25 1985-11-26 Cincinnati Milacron Inc. Anti-backlash mechanism for machine drive
EP0552584B1 (fr) * 1992-01-22 1996-05-08 MOOG GmbH Entraînement pour arme de pointage
DE4326155B4 (de) * 1992-08-10 2004-03-11 Volkswagen Ag Zahnradstufe mit Zahnspielbeseitigung
DE10239968A1 (de) * 2002-08-30 2004-03-04 Zf Lenksysteme Gmbh Spielfreies Planetenradgetriebe
DE102011079621B4 (de) * 2011-07-22 2015-04-30 Schaeffler Technologies Gmbh & Co. Kg Getriebe mit Verstellmittel zur Einstellung des Spiels sowie Verfahren zum Verstellen des Spiels eines Getriebes
DE102013010504A1 (de) 2013-06-25 2015-01-08 Rheinmetall Waffe Munition Gmbh Getriebe zur Drehrichtungsumschaltung

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4036074A (en) * 1975-10-01 1977-07-19 Bodnar Ernest R Anti-backlash gear system
US4331040A (en) * 1980-04-21 1982-05-25 Usm Corporation Anti-backlash gearing
US4417482A (en) * 1982-02-08 1983-11-29 The Falk Corporation Diaphragm mounted gear drive detuner
US4441401A (en) * 1982-09-27 1984-04-10 Ex-Cell-O Corporation Rack and pinion weapon elevation mechanism
US4719813A (en) * 1983-10-28 1988-01-19 Lazar Chalik Gear assembly
US5257543A (en) * 1992-09-03 1993-11-02 Borg-Warner Automotive, Inc. Gear transmission with an anti-rattle system
CN1117227C (zh) * 1997-12-30 2003-08-06 梅勒菲尔股份有限公司 传动设备
US7291088B2 (en) * 2002-11-22 2007-11-06 Joachim Arndt Method for effecting low-loss torque transmission in planetary gears
US20060205557A1 (en) * 2002-11-22 2006-09-14 Joachim Arndt Method for effecting low-loss torque transmission in planetary gears
US20200025502A1 (en) * 2009-03-31 2020-01-23 Npc Robotics Corporation Motor-less cartridge ring gear engagement module for actuating rotation of a turret
US10775124B2 (en) * 2009-03-31 2020-09-15 Npc Robotics Corporation Motor-less cartridge ring gear engagement module for actuating rotation of a turret
CN105221673A (zh) * 2015-11-05 2016-01-06 中国船舶重工集团公司第七二四研究所 一种双传动链零齿隙行星齿轮减速器
CN105221673B (zh) * 2015-11-05 2017-11-24 中国船舶重工集团公司第七二四研究所 一种双传动链零齿隙行星齿轮减速器
US11391357B2 (en) * 2019-07-30 2022-07-19 Industrial Technology Research Institute Adjustment device for bevel gear, automatic adjustment system for bevel gear and adjustment methods for bevel gear
CN114378363A (zh) * 2022-01-27 2022-04-22 福建恒而达新材料股份有限公司 自适应消隙齿轮箱及圆锯机
CN114378363B (zh) * 2022-01-27 2023-10-13 福建恒而达新材料股份有限公司 自适应消隙齿轮箱及圆锯机

Also Published As

Publication number Publication date
FR2066030A5 (fr) 1971-08-06
GB1320735A (en) 1973-06-20
NL7014364A (fr) 1971-04-20
CH536447A (de) 1973-04-30
DE1952545A1 (de) 1971-04-29
BE757592A (fr) 1971-03-16

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