US3854418A - Improvements in rack-and-pinion systems - Google Patents

Improvements in rack-and-pinion systems Download PDF

Info

Publication number
US3854418A
US3854418A US00336950A US33695073A US3854418A US 3854418 A US3854418 A US 3854418A US 00336950 A US00336950 A US 00336950A US 33695073 A US33695073 A US 33695073A US 3854418 A US3854418 A US 3854418A
Authority
US
United States
Prior art keywords
pinion
rack
resilient
proximal face
face
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
US00336950A
Other languages
English (en)
Inventor
J Bertin
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.)
Bertin Technologies SAS
Original Assignee
Bertin et Cie SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from FR7207481A external-priority patent/FR2174430A5/fr
Priority claimed from FR7233405A external-priority patent/FR2199839A6/fr
Application filed by Bertin et Cie SA filed Critical Bertin et Cie SA
Priority to US505074A priority Critical patent/US3901161A/en
Priority to US505075A priority patent/US3901162A/en
Application granted granted Critical
Publication of US3854418A publication Critical patent/US3854418A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/26—Racks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61B—RAILWAY SYSTEMS; EQUIPMENT THEREFOR NOT OTHERWISE PROVIDED FOR
    • B61B13/00—Other railway systems
    • B61B13/04—Monorail systems
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
    • 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
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/1967—Rack and pinion

Definitions

  • the invention is of use more particularly, but not exclusively, in transport systems of the kind comprising a machine which is moved along a rack by means of a machine-mounted pinion meshing with the rack.
  • the invention is of use inter alia for transport systems in which a ground effect machine is borne and- /or guided along a track with the inter-position of at least one pressure fluid cushion at a pressure above the ambient pressure or of at least one pressure fluid layer at a pressure below the ambient pressure.
  • the rack in a rack-and-pinion system of the kind described, the rack comprises a rigid longitudinal base adapted to withstand the forces which the pinion applies to the rack, and a resilient element in band or strip or similar form adhering to the rigid base over the whole length thereof and which receives the force of the said pinion.
  • the resilient element can be made of a substance based on natural or synthetic rubber or a resilient silicone.
  • the resilient element provides damping which helps to provide a considerable reduction in the noise made by the rack-and-pinion system, besides helping to increase the maximum starting torque by gradual storage thereof in the resilient element, in the form of deformation stresses.
  • the rigid base of the rack can comprise one or more superposed layers which can be secured to one another by any known means.
  • One layer of the rigid base can be a corrugated metal sheet.
  • the space between the same and a subfoundation plate also forming part of the rigid base can be filled with different filling materials to damp vibrations of the metal sheet and of the rack teeth.
  • filling materials there can be mentioned sand, concrete, fibres which may or may not be agglomerated, polyurethane and similar materials.
  • the rigid base may be formed with protruding portions having the rough shape of the teeth.
  • the resilient element can be secured to the rigid base by any known means, for example by adhesion. If required, the resilient element can have projecting or recessed portions adapted to engage with corresponding recessed or projecting portions of an adjacent element forming part of the rack. The resilient element covers the rigid base over the whole of its operative length.
  • the resilient element can be shaped into corrugations adapted to engage the toothed pinion.
  • the resilient element can have a protective lining of a substance, such as metal sheet, which is harder than the resilient element. It can also have provision for reducing the coefficient of friction between the rack and the pinion.
  • FIGS. 1 5 are diagrammatic views, in cross-section and partial cross-section, of rack-and-pinion systems 5 forming part of a transport system comprising a track and a machine movable therealong;
  • FIG. 6 is a view, in a vertical section parallel to the rack, of a pinion meshing with metal teeth borne by a resilient element which forms a damping seating for the teeth, the resilient element itself covering a rigid base;
  • FIG. 7 is a view, in a vertical section parallel to the rack, of a corrugated rigid base covered by a resilient element
  • FIG. 8 is a view similar to FIG. 7 showing a resilient element whose thickness varies along a corrugation
  • FIG. 9 is a view similar to FIGS. 7 and 8 showing the interposition of filling material in the gap between two parts of the rigid base;
  • FIG. 10 is a view similar to FIGS. 7 to 9 of a rack in which the resilient element has a protective covering
  • FIG. 11 is a view similar to FIGS. 7 to 10 of a rack coated with a layer of material which has a low coefficient of friction in its contact with the pinion.
  • FIGS. 1 to 6 show a transport system comprising a ground effect machine borne and guided by a track 17 with the interposition of fluid cushions.
  • the track 17 in shape resembles an inverted T having, for example, a substantially horizontal bearing portion 117 and a susbstantially vertical central guiding portion 217.
  • the fluid cushions are confined by chambers l5, 16, for example of the plenum chamber kind, supplied with fluid at a pressure above the ambient pressure by means (not shown).
  • the machine 25 can be borne and/or guided by means of fluid layers whose pressure is below the ambient pressure.
  • the machine 25 is driven along the track 17 through the agency of two racks 1 each meshing with a pinion 2.
  • Each pinion 2 is rigidly secured to a shaft 9 driven by a motor 6 through a speed reducer 27.
  • Each rack 1 extends parallel to the length of the track 17.
  • FIGS. 3 5 show arrangements in which each rack 1 is disposed at an inclination to the track 17 and meshes with an inclined pinion 2. These arrangements are advantageous, particularly for limiting rolling movement of the machine 25. To this end, the line on which the plane 64 containing the pinion 2 intersects the longitudinal centre-plane of the machine is, with advantage, near the roll axis thereof.
  • each rack l is secured to the central guiding portion 217 of the track 17.
  • FIG. 6 there is shown a rack l meshing with a pinion 2.
  • the rack has a rigid longitudinal base 11 which can withstand the forces applied by the pinion 2 and which in the example shown in FIGS. 1 to 5 forms part of a track 17 co-operating with the machine 25.
  • a resilient element 3 in band or strip or similar form has a substantially planar surface which is connected, for example by adhesion, to a corresponding planar surface of the base 11 over the whole length thereof.
  • the element 3 can be either continuous or comprise a number of sections abutting one another in end-to-end relationship.
  • the element 3 can be made, for example, of natural rubber or a synthetic rubber such as neoprene or perbunan or viton or of a resilient silicone. If required, some resilient synthetic or natural plastic substances are suitable for the element 3.
  • That face of the resilient element 3 which is opposite the face adhering to the base 11 is substantially planar and bears metal teeth 4 co-operating with the pinion 2. Via the teeth 4, therefore, the resilient element 3 receives the force of the moving element 2 and thus acts as a seating providing resilient damping.
  • the element 3 is in engagement with at least one adjacent element, for example, the teeth 4 or the rigid base 11, by way of projecting or recessed parts 12 which co-operate with correspondingly recessed or projecting parts of such adjacent element.
  • the teeth 4 can be integral with one another as shown in the lefthand part of FIG. 6; alternatively, and as shown in the right-hand part of FIG. 6, the teeth 4 can be independent integers and separated from one another by small gaps 31 to improve overall resilience.
  • a resilient mounting of the pinion 2 by means of a resilient ring cooperating coaxially with a hub 7 and with a toothbearing rim 10 which forms part of the pinion.
  • the hub 7 is secured to the shaft 9 by a keyor cotter or the like 8.
  • the ring 5 can be made of the same substance as the resilient element 3.
  • An arrow F indicates the direction of pinion rotation, and an arrow f indicates the direction in which the machine moves.
  • the rigid base of the rack 1 comprises two superposed layers 30, 34 which are connected together by bolts or screws 35.
  • the proximal face (with respect to the pinion 2) of the rigid base 34 is shaped into corrugations 36 of the same ptitch as the teeth of the pinion 2.
  • the resilient element 3 is of substantially constant thickness and is shaped on its distal face (with respect to the pinion) to match the corrugations 36, which it covers externally. On its proximal face (with respect to the pinion 2), the resilient element 3 is thus also shaped into corrugation which engage by direct contact the teeth of the pinion 2.
  • the pinion 2 can be made, preferably, of a material marketed under the name of Nylon 6 or Nylon 66 or a similar material.
  • the arrow F indicates the direction of pinion rotation.
  • FIG. 8 shows a variant of the previous embodiment wherein the layer 30 of the rigid base forms part of the track.
  • the shape of the corrugations 36 is somewhat different and the thickness of the resilient element 3 varies along a corrugation, increasing towards both the crest and root of the corrugation from the region N where the pitch circle of the pinion meets the rack.
  • FIG. 9 shows a variant of the two immediately preceding embodiments wherein the rigid longitudinal base of the rack comprises a subfoundation 40 bearing a corrugated metal sheet 44 which is secured to the subfoundation 40 by means (not shown).
  • the metal sheet 44 is relatively rigid and is corrugated before being positioned and before receiving the resilient element 3.
  • the gap between the elements 40 and 44 is filled with a substance 28 such as sand or concrete or agglomerated or unagglomerated fibres or polyurethane or the like.
  • the corrugated metal sheet 44 is covered by the resilient element 3; however, in the present case there is no direct contact between the resilient element and the pinion teeth, to which end a protective lining 45 for the resilient element is secured thereto, for example by adhesion, thus preventing premature wear of the element 3 as a result of friction and of possible overstressing by the pinion teeth.
  • the lining 45 can be made of a thin but hard material based, for example, on hardened natural or synthetic rubber or on an appropriate hard plastics material.
  • the lining 45 can be a corrugated metal sheeting.
  • the material used for the covering 45 has a low coefficient of friction in the presence of the pinion teeth.
  • the filling material 28 helps inter alia to damp vibrations of the sheet metal 44 and therefore of the rack teeth.
  • the rigid longitudinal base takes the form of a planar sheet metal member 50.
  • a corrugated lining 55 of substantially uniform thickness engages the teeth of the pinion 2.
  • the resilient element 3 takes up all the space between the two sheet metal members 50, 55, to which it is secured, for example by adhesion, over the whole extent of the contacting surfaces.
  • the resilient element 3 can be premoulded, then secured in position; alternatively, it can be moulded directly between the two members 50 and 55.
  • the element 3 can be made of natural or synthetic rubber.
  • the lining 55 may need to be fairly thick so as not to become permanently deformed by the pressure of the pinion teeth; in this case, however, the resilient material used for the element 3 can be relatively flexible.
  • the lining 55 can be made of 4 mm thick mild steel for teeth having a pitch of 30 mm, with rubber having a Shore hardness of 60.
  • FIG. 11 shows the same rack adapted for improved operation without lubrication; to this end, the rack is coated with a substance 56 which has a low coefficient of friction in the presence of the teeth of the associated pinion 2.
  • the metal lining 55 can be treated with, for example, molybdenum disulfide or given the sulfinuz process or covered by a polyethylene film.
  • a low-friction layer 56 can, with advantage, be a 0.2 mm thick film of the substance called Kletene" which is adhesively secured to the lining 55 with the interposition of a 0.4 mm thick intermediate layer of rubber.
  • a rack according to the invention can be embodied by consecutive sections of reduced elementary length, for example, by 40-tooth sections. Joints between consecutive sections can be either at the corrugation roots, as at a place 57 in FIG. 10, or at the corrugation crests as at a place 58 in FIG. 11. It will be appreciated that the rack teeth or corrugations do not contact the pinion teeth at the places 57, 58.
  • the abutting ends of the lining sections 55 are secured to one another, preferably by welding, to which end the resilient element 3 and the antifriction layer 56 are interrupted for some distance on either side of the joins to enable the weld to be made.
  • a rack-and-pinion system including a rack and a toothed pinion in mutual meshing engagement, said rack comprising:
  • a resilient longitudinal element having:
  • proximal face with respect to the pinion, which proximal face is shaped into corrugations adapted to engage the teeth of the pinion.
  • proximal face of the rigid longitudinal base, and said distal face of the resilient longitudinal element which rests thereupon, are also both shaped into corrugations having the same pitch as and coextensive with the said corrugations of said proximal face of the resilient longitudinal element.
  • said rigid longitudinal base comprises a strip of corrugated sheetmetal having a proximal face with respect to the pinion, whereupon the said resilient longitudinal element rests, and a distal face with respect to the pinion.
  • the thickness of the said resilient element is at a minimum in the region where the pitch circle of the pinion meets the rack, and increases from said region towards both the crest and the root of the said corrugation.
  • said rigid longitudinal base comprises a substantially planar strip of sheet-metal which together with said strip of corrugated sheet-metal defines a space, which space is filled with said resilient longitudinal element.
  • said resilient longitudinal element is made of resilient siliconebased material.
  • a rack-and-pinion system for use as a means for driving a machine along a track, said system comprises a toothed pinion carried by the machine and a rack disposed along the track, said pinion and rack being in mutual meshing engagement, said rack comprising:
  • a resilient longitudinal element having;
  • proximal face with respect to the pinion, which proximal face is shaped into corrugations adapted to engage the teeth of the pinion.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Thermal Sciences (AREA)
  • Transportation (AREA)
  • Gears, Cams (AREA)
  • Transmission Devices (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
US00336950A 1972-03-03 1973-03-01 Improvements in rack-and-pinion systems Expired - Lifetime US3854418A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US505074A US3901161A (en) 1972-03-03 1974-09-11 Transport systems equipped with a rack-and-pinion-type propelling mechanism
US505075A US3901162A (en) 1972-03-03 1974-09-11 Systems comprising a cogwheel and a longitudinal reaction member cooperating with the cogs thereon

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7207481A FR2174430A5 (en) 1972-03-03 1972-03-03 Rail transport systems - with rubber layers in rack and pinion drives
FR7233405A FR2199839A6 (OSRAM) 1972-09-21 1972-09-21

Publications (1)

Publication Number Publication Date
US3854418A true US3854418A (en) 1974-12-17

Family

ID=26216955

Family Applications (1)

Application Number Title Priority Date Filing Date
US00336950A Expired - Lifetime US3854418A (en) 1972-03-03 1973-03-01 Improvements in rack-and-pinion systems

Country Status (7)

Country Link
US (1) US3854418A (OSRAM)
JP (1) JPS48100557A (OSRAM)
CA (1) CA972582A (OSRAM)
CH (1) CH569148A5 (OSRAM)
DE (1) DE2309949A1 (OSRAM)
GB (2) GB1424478A (OSRAM)
IT (1) IT981089B (OSRAM)

Cited By (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4030592A (en) * 1976-01-20 1977-06-21 Diagraph-Bradley Industries, Inc. Stencil cutting apparatus
JPS52109214A (en) * 1976-03-10 1977-09-13 Siemens Ag Runnin point rack for driven conveying vehicle
WO1980002534A1 (en) * 1979-05-21 1980-11-27 Centronics Data Computer Self-propelled carriage assembly for printers and the like
US4257286A (en) * 1978-03-22 1981-03-24 Nippon Kogaku K.K. Precision driving apparatus
US4266484A (en) * 1978-02-11 1981-05-12 Hauhinco Maschinenfabrik G. Hausherr, Jochums & Co. Kg Rack-rail assembly for a mining machine
US4498556A (en) * 1982-09-11 1985-02-12 Access Engineering Ltd. Vertically movable, road towable work platform
US4683805A (en) * 1985-03-25 1987-08-04 Flo-Tork, Inc. Rotary actuator having integral piston assembly with floating rack
US4690177A (en) * 1985-07-30 1987-09-01 Lindauer Dornier Gesellschaft Mbh Gripper rod for shuttleless looms
EP0258696A3 (en) * 1986-08-21 1989-12-13 Hasenclever Maschf Sms Forging manipulator
US4944231A (en) * 1988-02-29 1990-07-31 Pipp Mobile Systems, Inc. Mobile storage system with driving assemblies
US5024164A (en) * 1988-02-29 1991-06-18 Pipp Mobile Systems, Inc. Mobile storage system with improved driving assemblies
US5150631A (en) * 1990-09-13 1992-09-29 Webasto Ag Fahrzeugtechnik Flexible thermoplastic rack bar
US5398617A (en) * 1992-12-03 1995-03-21 Fata Automation S.P.A. Overhead rail conveyor system with improved traction having elastically deforming wheel or rail portions
US5540111A (en) * 1992-08-03 1996-07-30 Franklin E. Barnett Drive apparatus and method
US5542357A (en) * 1994-03-18 1996-08-06 Northrop Grumman Corporation Linear turbine propulsion system
WO2000029199A1 (en) * 1998-11-17 2000-05-25 Kimberly-Clark Worldwide, Inc. Apparatus and method for cross-directional stretching of polymeric film and other nonwoven sheet material and materials produced therefrom
EP1089021A3 (fr) * 1999-09-30 2001-06-20 S.A. Defontaine Système de liaison d'une couronne dentée de démarrage sur un support lié à l'arbre de sortie d'un moteur thermique
US6293164B1 (en) 1999-06-30 2001-09-25 Trw Inc. Rack and pinion steering apparatus and method for manufacturing a helical pinion
US20110081208A1 (en) * 2000-08-01 2011-04-07 American Piledriving Equipment, Inc. Automatically adjustable caisson clamp
US20110162859A1 (en) * 2010-01-06 2011-07-07 White John L Pile driving systems and methods employing preloaded drop hammer
US20120304884A1 (en) * 2009-09-30 2012-12-06 Maurer Söhne Gmbh & Co. Kg Transport system having a positive drive
US8434969B2 (en) 2010-04-02 2013-05-07 American Piledriving Equipment, Inc. Internal pipe clamp
US20130160589A1 (en) * 2010-09-24 2013-06-27 Miba Sinter Austria Gmbh Toothed wheel and backlash free gear train
US8496072B2 (en) 2002-09-17 2013-07-30 American Piledriving Equipment, Inc. Preloaded drop hammer for driving piles
US20150034401A1 (en) * 2011-02-21 2015-02-05 Novus Finitor B.V. Levitation System for a Train
US9157408B2 (en) 2009-11-23 2015-10-13 Robert Bosch Gmbh Noise-optimized starter device
US9249551B1 (en) 2012-11-30 2016-02-02 American Piledriving Equipment, Inc. Concrete sheet pile clamp assemblies and methods and pile driving systems for concrete sheet piles
US9371624B2 (en) 2013-07-05 2016-06-21 American Piledriving Equipment, Inc. Accessory connection systems and methods for use with helical piledriving systems
US9874050B2 (en) 2013-09-23 2018-01-23 Knorr-Bremse Gesellschaft Mit Beschrankter Haftung Sliding door module/pivoting sliding door module having floating mounting of a rack of a rack-and-pinion drive
US10273646B2 (en) 2015-12-14 2019-04-30 American Piledriving Equipment, Inc. Guide systems and methods for diesel hammers
US10538892B2 (en) 2016-06-30 2020-01-21 American Piledriving Equipment, Inc. Hydraulic impact hammer systems and methods
US10907719B2 (en) * 2015-11-02 2021-02-02 The Uab Research Foundation Hybrid composite gear with enhanced strength and wear resistance
CN114312128A (zh) * 2022-01-28 2022-04-12 中车长春轨道客车股份有限公司 齿轨轮及转向架
CN116556118A (zh) * 2023-04-13 2023-08-08 株洲中车特种装备科技有限公司 采用钢结构轨道的架空类齿轨车运行时的减振降噪方法
US12129623B2 (en) 2021-03-31 2024-10-29 American Piledriving Equipment, Inc. Segmented ram systems and methods for hydraulic impact hammers

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE466490B (sv) * 1987-08-20 1992-02-24 Interbau Cyprus Ltd En foer godsbefordran avsedd anordning
JPH0771567A (ja) * 1993-09-03 1995-03-17 Nec Corp 歯車装置
DE10023775A1 (de) * 2000-05-15 2001-11-22 Volkswagen Ag Zahnstange mit Oberflächenschutz
DE10258842B4 (de) * 2002-12-17 2011-03-24 Zf Lenksysteme Gmbh Zahnstangenlenkgetriebe
DE102013209376A1 (de) * 2013-05-22 2014-11-27 Bayerische Motoren Werke Aktiengesellschaft Zahnstange für eine Lenkvorrichtung eines Kraftfahrzeugs
AT514882A3 (de) * 2013-09-23 2015-06-15 Knorr Bremse Ges Mit Beschränkter Haftung Schiebetürmodul/Schwenkschiebetürmodul mit fliegender Lagerung einer Zahnstange eines Zahnstangenantriebs
AT514883A3 (de) * 2013-09-23 2015-06-15 Knorr Bremse Ges Mit Beschränkter Haftung Materialpaarung für einen Zahnstangenantrieb eines Schiebetürmoduls/Schwenkschiebetürmoduls
DE102014216727A1 (de) * 2014-08-22 2016-02-25 Zf Friedrichshafen Ag Zahnradelement zur Geräuschreduzierung
DE102021211441A1 (de) * 2021-10-11 2023-04-13 Contitech Antriebssysteme Gmbh Linearantrieb

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2652785A (en) * 1951-10-05 1953-09-22 Walter C Cox Traction mechanism for cog roads
US3229543A (en) * 1962-02-12 1966-01-18 Frank T Johmann Racks

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2652785A (en) * 1951-10-05 1953-09-22 Walter C Cox Traction mechanism for cog roads
US3229543A (en) * 1962-02-12 1966-01-18 Frank T Johmann Racks

Cited By (46)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4030592A (en) * 1976-01-20 1977-06-21 Diagraph-Bradley Industries, Inc. Stencil cutting apparatus
JPS52109214A (en) * 1976-03-10 1977-09-13 Siemens Ag Runnin point rack for driven conveying vehicle
US4266484A (en) * 1978-02-11 1981-05-12 Hauhinco Maschinenfabrik G. Hausherr, Jochums & Co. Kg Rack-rail assembly for a mining machine
US4257286A (en) * 1978-03-22 1981-03-24 Nippon Kogaku K.K. Precision driving apparatus
WO1980002534A1 (en) * 1979-05-21 1980-11-27 Centronics Data Computer Self-propelled carriage assembly for printers and the like
US4498556A (en) * 1982-09-11 1985-02-12 Access Engineering Ltd. Vertically movable, road towable work platform
US4683805A (en) * 1985-03-25 1987-08-04 Flo-Tork, Inc. Rotary actuator having integral piston assembly with floating rack
US4690177A (en) * 1985-07-30 1987-09-01 Lindauer Dornier Gesellschaft Mbh Gripper rod for shuttleless looms
EP0258696A3 (en) * 1986-08-21 1989-12-13 Hasenclever Maschf Sms Forging manipulator
US5024164A (en) * 1988-02-29 1991-06-18 Pipp Mobile Systems, Inc. Mobile storage system with improved driving assemblies
US4944231A (en) * 1988-02-29 1990-07-31 Pipp Mobile Systems, Inc. Mobile storage system with driving assemblies
US5150631A (en) * 1990-09-13 1992-09-29 Webasto Ag Fahrzeugtechnik Flexible thermoplastic rack bar
US5540111A (en) * 1992-08-03 1996-07-30 Franklin E. Barnett Drive apparatus and method
US5398617A (en) * 1992-12-03 1995-03-21 Fata Automation S.P.A. Overhead rail conveyor system with improved traction having elastically deforming wheel or rail portions
US5542357A (en) * 1994-03-18 1996-08-06 Northrop Grumman Corporation Linear turbine propulsion system
US5669308A (en) * 1994-03-18 1997-09-23 Northrop Grumman Corporation Linear turbine propulsion system
US6368444B1 (en) 1998-11-17 2002-04-09 Kimberly-Clark Worldwide, Inc. Apparatus and method for cross-directional stretching of polymeric film and other nonwoven sheet material and materials produced therefrom
WO2000029199A1 (en) * 1998-11-17 2000-05-25 Kimberly-Clark Worldwide, Inc. Apparatus and method for cross-directional stretching of polymeric film and other nonwoven sheet material and materials produced therefrom
GB2361664B (en) * 1998-11-17 2003-04-02 Kimberly Clark Co Apparatus and method for cross-directional stretching of polymeric film and other nonwoven sheet material and materials produced therefrom
GB2361664A (en) * 1998-11-17 2001-10-31 Kimberly Clark Co Apparatus and method for cross-directional stretching of polymeric film and other nonwoven sheet material and materials produced therefrom
US6684727B2 (en) 1999-06-30 2004-02-03 Trw Inc. Rack and pinion steering apparatus
US6293164B1 (en) 1999-06-30 2001-09-25 Trw Inc. Rack and pinion steering apparatus and method for manufacturing a helical pinion
EP1089021A3 (fr) * 1999-09-30 2001-06-20 S.A. Defontaine Système de liaison d'une couronne dentée de démarrage sur un support lié à l'arbre de sortie d'un moteur thermique
US6782773B1 (en) 1999-09-30 2004-08-31 S.A. Defontaine System for coupling a toothed starter ring to a support connected to the output shaft of an internal combustion engine
US20110081208A1 (en) * 2000-08-01 2011-04-07 American Piledriving Equipment, Inc. Automatically adjustable caisson clamp
US8496072B2 (en) 2002-09-17 2013-07-30 American Piledriving Equipment, Inc. Preloaded drop hammer for driving piles
US20120304884A1 (en) * 2009-09-30 2012-12-06 Maurer Söhne Gmbh & Co. Kg Transport system having a positive drive
US8661987B2 (en) * 2009-09-30 2014-03-04 Joerg Beutler Transport system having a positive drive
US9157408B2 (en) 2009-11-23 2015-10-13 Robert Bosch Gmbh Noise-optimized starter device
US8763719B2 (en) 2010-01-06 2014-07-01 American Piledriving Equipment, Inc. Pile driving systems and methods employing preloaded drop hammer
US20110162859A1 (en) * 2010-01-06 2011-07-07 White John L Pile driving systems and methods employing preloaded drop hammer
US8434969B2 (en) 2010-04-02 2013-05-07 American Piledriving Equipment, Inc. Internal pipe clamp
US20130160589A1 (en) * 2010-09-24 2013-06-27 Miba Sinter Austria Gmbh Toothed wheel and backlash free gear train
US9222569B2 (en) * 2010-09-24 2015-12-29 Miba Sinter Austria Gmbh Toothed wheel and backlash free gear train
US10293803B2 (en) 2011-02-21 2019-05-21 Novus Finitor B.V. Levitation system for a train
US20150034401A1 (en) * 2011-02-21 2015-02-05 Novus Finitor B.V. Levitation System for a Train
US9249551B1 (en) 2012-11-30 2016-02-02 American Piledriving Equipment, Inc. Concrete sheet pile clamp assemblies and methods and pile driving systems for concrete sheet piles
US9371624B2 (en) 2013-07-05 2016-06-21 American Piledriving Equipment, Inc. Accessory connection systems and methods for use with helical piledriving systems
US9874050B2 (en) 2013-09-23 2018-01-23 Knorr-Bremse Gesellschaft Mit Beschrankter Haftung Sliding door module/pivoting sliding door module having floating mounting of a rack of a rack-and-pinion drive
US10907719B2 (en) * 2015-11-02 2021-02-02 The Uab Research Foundation Hybrid composite gear with enhanced strength and wear resistance
US10273646B2 (en) 2015-12-14 2019-04-30 American Piledriving Equipment, Inc. Guide systems and methods for diesel hammers
US10538892B2 (en) 2016-06-30 2020-01-21 American Piledriving Equipment, Inc. Hydraulic impact hammer systems and methods
US12129623B2 (en) 2021-03-31 2024-10-29 American Piledriving Equipment, Inc. Segmented ram systems and methods for hydraulic impact hammers
CN114312128A (zh) * 2022-01-28 2022-04-12 中车长春轨道客车股份有限公司 齿轨轮及转向架
CN114312128B (zh) * 2022-01-28 2023-10-27 中车长春轨道客车股份有限公司 齿轨轮及转向架
CN116556118A (zh) * 2023-04-13 2023-08-08 株洲中车特种装备科技有限公司 采用钢结构轨道的架空类齿轨车运行时的减振降噪方法

Also Published As

Publication number Publication date
CH569148A5 (OSRAM) 1975-11-14
CA972582A (en) 1975-08-12
GB1424478A (en) 1976-02-11
JPS48100557A (OSRAM) 1973-12-19
DE2309949A1 (de) 1973-09-06
IT981089B (it) 1974-10-10
GB1424477A (en) 1976-02-11

Similar Documents

Publication Publication Date Title
US3854418A (en) Improvements in rack-and-pinion systems
KR960010221B1 (ko) 궤도차량용 무한궤도 및 궤도조립체
US2986432A (en) Antifriction bearing with a casing of plastic synthetic material acting as elastic yieldable cushion
US4844484A (en) Floating lip seal with reinforced flexible portion
US3924907A (en) Bearing pad and bridge construction
US4671519A (en) Lip sealing ring with tow rows of projections and for a rotary shaft
US4195852A (en) End face seal assembly
US3623590A (en) Moving handrail system
JPH0315056B2 (OSRAM)
US4526482A (en) Hydrodynamic bearing surface for high loads and low viscosity lubricating fluids
US2449421A (en) Track for vehicles
JPS589870B2 (ja) メカニカルシ−ル
JPS5119251A (OSRAM)
CA2132807A1 (en) Track-belt for track driven vehicles
EP0442539A3 (en) Friction facing material amd carrier assembly
US3439959A (en) Endless steel track construction
GB1402829A (en) Flexible strip and means for retaining said strip to a second member
JPH0784905B2 (ja) 相対回転する機械部品の軸封装置
WO1980001902A1 (en) Laterally flexible conveyor belt
US3767214A (en) Freeze-resisting seal ring
US2453209A (en) Drive for track-laying vehicles
US3429420A (en) Conveyor installation and conveyor belt system therefor
US3428375A (en) Bearing having flexible seal arrangement
ATE109844T1 (de) Schiene für schienenfahrzeuge.
US2794662A (en) Seal with side acting spring