US3759334A - Impact socket wrench tool - Google Patents

Impact socket wrench tool Download PDF

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Publication number
US3759334A
US3759334A US00195278A US3759334DA US3759334A US 3759334 A US3759334 A US 3759334A US 00195278 A US00195278 A US 00195278A US 3759334D A US3759334D A US 3759334DA US 3759334 A US3759334 A US 3759334A
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US
United States
Prior art keywords
socket wrench
impact
wrench
impact device
driving motor
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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
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US00195278A
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English (en)
Inventor
J Theurer
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.)
Franz Plasser Bahnbaumaschinen Industrie GmbH
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Franz Plasser Bahnbaumaschinen Industrie GmbH
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    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01B—PERMANENT WAY; PERMANENT-WAY TOOLS; MACHINES FOR MAKING RAILWAYS OF ALL KINDS
    • E01B29/00—Laying, rebuilding, or taking-up tracks; Tools or machines therefor
    • E01B29/24—Fixing or removing detachable fastening means or accessories thereof; Pre-assembling track components by detachable fastening means
    • E01B29/28—Fixing or removing detachable fastening means or accessories thereof; Pre-assembling track components by detachable fastening means the fastening means being of screw-and-nut type; Apparatus therefor, adapted to additionally drilling holes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
    • B23P19/00—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes
    • B23P19/04—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes for assembling or disassembling parts
    • B23P19/06—Screw or nut setting or loosening machines

Definitions

  • a socket wrench capable of reciprocatory sliding motion in the direction of its axis is rotatable thereabout by a preferably hydraulic driving motor.
  • a vibratory impact device is mounted between the motor and the wrench to impart reciprocatory impacts to the rotating wrench, and a slip clutch between the motor and the impact device prevents vibrations from reaching the motor.
  • the present invention relates to improvements in an impact socket wrench tool wherein the wrench is rotatable by a driving motor and a vibratory impact device is mounted between the driving motor and the wrench.
  • this invention is directed to a mobile machine for simultaneously fastening a pair of rail fastening bolts arranged on respective sides of a track rail, wherein a pair of such tools are mounted on a mobile frame.
  • the socket wrench is capable of rotary motion about the axis thereof and of reciprocatory sliding motion in the direction of the axis.
  • the vibratory impact device various designs of which are also well known, effectuates the reciprocatory sliding motion during rotation of the wrench.
  • socket wrench may be replaced by a screwdriver bit to provide a power-driven impact screwdriver, or by a drilling bit to provide a power-driven impact drill so that the tool of the invention may be used either as a screwdriver for fastening screws or as a drill for tapping holes in railroad ties, for instance.
  • socket wrench includes screwdriver or drilling bits used in equivalent rotary impact tools well known in this art.
  • socket wrenches in track work which are driven directly by hydraulic motors. Since most mobile track maintenance machines have hydraulic drive systems for various tools, use may be made of these systems for driving the wrenches without requiring an additional power plant while, at the same time, enabling the torque to be accurately controlled by pressure relief valves arranged in the hydraulic fluid delivery lines.
  • the efficiency of such power-driven wrenches has also proven to be limited, particularly in respect of loosening weather-beaten bolts or nuts. To overcome this, it was necessary to provide a relatively powerful hydraulic motor, requiring a considerable increase in the capacity of the hydraulic system particularly in such machines which use a plurality of power.- driven wrenches.
  • the driving motor for rotating the socket wrench, screwdriver or drilling bit may be not only pneumatically or electrically but also hydraulically operated so that the advantages of hydraulic drives may be used for the first time in such impact tools while holding the dimensions of the driving motor to a minimum.
  • the above and other objects of this invention are accomplished by arranging between the driving motor, which is preferably hydraulically driven, and the impact device a means for absorbing vibrations of the vibratory impact device, this means preventing the vibrations from reaching the driving motor.
  • This means may be a slip or disk clutch of a known type.
  • the means for absorbing vibrations or preventing them from reaching the driving motor does not serve to limit the torque of the socket wrench but is used solely to prevent the transmission of the reciprocatory impacts or vibrations from the impact device to the motor.
  • this vibration blocking means may be used in power-driven impact wrenches of all types, in addition to the slip clutch designed to limit the torque of the wrench but it is of primary advantage with hydraulic driving motors, in which combination it makes it possible for the first time to use a hydraulic driving motor with an impact device, as explained hereinabove.
  • the exact ad justment of the torque of the wrench may be effected in a known manner by mounting pressure relief valves in the hydraulic fluid delivery line to the driving motor, such adjustment being calculated accurately as a function of the hydraulic fluid pressure which determines the rotational speed of the driving motor as well as the vibratory motion of the impact device.
  • a hydraulic drive furthermore, requires only a fraction of the driving power required, for instance, for the compressor of a compressed air drive, thus making the use of such tools-even more advantageous in mobile track working apparatus.
  • slip clutches are preferred, other means for absorbing or blocking vibrations of the vibratory impact device, including hydraulically operated means, may be used in the tool of the present invention.
  • the relative rotational movement between the coupling parts of the tool involves only a few millimeters per impact or axial movement and the coupling parts are at rest in relation to each other between impacts. In other words, there is no continuous slippage so that the clutch disk linings are not overheated as is the case with the use of such clutches for limiting the torque.
  • the slip clutches are subject to very little wear in the tools of this invention so that the tools have a long life.
  • the torque for fastening bolts or nuts is limited to about 20 kpm and loosening of rusted connections may require a torque of 200 kpm or more, it is generally sufficient to arrange the slip clutch fora torque of about 4 kpm.
  • Such a coupling requires very little space and thus makes it possible to provide a very compact power-driven wrench with all the indicated advantages. Since the slip clutch is not used to determine an exact torque but merely serves to absorb or block vibrations, changes in the friction coefficient of the clutch disk linings make no substantial difference in the operation of the tool.
  • the socket wrench is slidingly movable in the direction of its axis into driving engagement with the impact device and driving motor against the bias of a spring so that it will not be rotated when the socket first engages the bolt head or nut and thus avoids damaging the same.
  • the sliding stroke may be adjustable. This arrangement also makes it possible to increase the rotary speed of the wrench and thus its efficiency.
  • the rotational speed of the wrench is about 90 rpm while the initial speed of the wrenches of this invention may be about 2,000 to 3,000 rpm, which speed is reduced by the impact device to about 600 to 1,000 rpm.
  • the axially slidable socket wrench may be coupled to the driving motor directly by the parts of the impact device, in which case the housing of the impact device is continuously rotated by the driving motor and is coupled with the wrench only after the wrench has engaged the bolt head or nut and has been axially moved inwardly.
  • the life of the impact device will be increased if a jaw clutch is mounted between the impact device and the vibration absorbing or blocking means so that the impact device is at rest until the wrench has been coupled to the driving motor by the axial sliding motion thereof.
  • the impact socket wrench tool of the present invention may be used with advantage as an individual tool, it will be particularly useful in conjunction with a mobile machine for renewing track, where space considerations are of the utmost importance.
  • a plurality of such pairs of socket wrench tools may be mounted on a common frame spaced from each other in the direction of the track and for relative movement in respect of each other and the frame.
  • a single relatively small hydraullic supply system including a motor-driven hydraulic pump, may then be used for all the driving motors of the tools since hydraulic motors for such tools require relatively little hydraulic fluid for effective operation.
  • a registering boss may be associated with each pair of tools to cooperate with a part of the rail fastening means.
  • a pair of hydraulically-driven wrench tools are mounted on a wheelbarrow-type carriage.
  • the carriage comprises a running gear and a carrier beam having two ends mounted on the running gear for vertical and horizontal pivoting movement, the running gear being positioned intermediate the carrier ends.
  • Handle means is provided at one of the carrier ends while a hydraulic pump and motor means for driving the pump are mounted on the other carrier end.
  • the pump delivers hydraulic fluid to the driving motors of each tool mounted on the carriage.
  • FIG. 1 is a longitudinal section of an impact socket wrench tool according to this invention
  • FIG. 2 is a side view of a mobile machine for fasten ing rail fastening bolts by means of such impact socket wrench tools
  • FIG. 3 is a side view of a manually movable machine of this type.
  • an impact socket wrench tool comprising essentially three coaxially arranged and associated parts, i.e., a replaceably mounted socket wrench 3, a hydraulically driven driving motor 1 for rotating the socket wrench, and a vibratory impact device 2 mounted between the driving motor and the socket wrench for effectuating reciprocatory sliding motion during rotation of the wrench, the wrench being capable of rotary motion about the axis thereof and of the reciprocatory sliding motion in the direction of the axis.
  • a slip clutch in the form of a disk clutch 4 is arranged between the driving motor 1 and the impact device 2 for absorbing vibrations of the vibratory impact device, one part 4a of the clutch being keyed to the shaft of motor 1 for rotation therewith and the other clutch part 4b being keyed to a stub shaft 22 coupled to the impact device for rotation with the stub shaft.
  • a protective casing 5 surrounds the clutch 4, one end of the casing being bolted to the hydraulic motor 1 while the other casing end is bolted to housing 7 which surrounds the impact device 2.
  • a closure disk 6 is interposed between the casing 5 and housing 7, the closure disk having a central bore receiving the clutch part 4b and stub shaft 22 which is rotatably journaled in the central bore of the closure disk.
  • the slip clutch 4 is capable of transmitting a torque of about 4 kpm although the socket wrench 3 may be subjected to a torque as high as 200 kpm, or more, which may be required to remove heavily rusted bolts.
  • a torque of about 4 kpm although the socket wrench 3 may be subjected to a torque as high as 200 kpm, or more, which may be required to remove heavily rusted bolts.
  • Such high torques are achieved with a hydraulic motor of 2,000 to 3,000 rpm and the impact obtained by the impact device 2.
  • Each of the series of repeated impacts imparted to the wrench by the impact device 2 causes the disks of the clutch to slip a little, i.e., a few millimeters, whereby the vibrations of the impact tool are so absorbed as not to be transmitted to the hydraulic motor, thus protecting the operation of the motor from the vibrations.
  • the disk clutch does not continuously slip during normal operation of the tool so that the wear of the clutch disks is very low.
  • a wrench holder 8 is rotatably joumaled in the lower end of housing 7 by means of roller bearings 9. 9a, 9b.
  • a socket wrench rod 10 is mounted in the holder end adjacent the impact device 2 for reciprocatory sliding motion in the direction of the tool axis, the rod 10 having a hexagonal portion 10a engaging the holder so as to be non-rotatory in relation thereto and thus rotating therewith.
  • the hexagonal end of the socket wrench rod 10 carries one coupling part 2a of the impact device 2 while the other impact device part 2b, which carries the impact claws, is coupled to the disk clutch 4, a jaw clutch 11 being provided in the illustrated embodiment between the disk clutch 4 and the other impact device part 2b.
  • the impact claw carrying impact device part 2b is rotated continuously by the hy-- draulic motor 1 and the impact device parts 2a, 2b serve simultaneously as coupling between the motor and the socket wrench, i.e., when the socket wrench 3 is engaged with a bolt head to cause axial inward movement of the wrench, the coupling part 2 is moved into engagement with impact device part 2b'so as to rotate therewith.
  • the impact device parts 20, 2b are in constant engagement and the impact device is engaged with the hydraulic motor and rotated thereby upon the axial inward movement of the socket wrench and the corresponding engagement of jaw clutch 11.
  • the axial sliding movement of the socket wrench 3 may be preferably adjustably limited by a suitable stop (not shown).
  • a helical compression spring 12 is mounted on rod 10 to bias the socket wrench 3 outwardly, one end of the spring resting against annular spring seat 13 supported by holder 8 and the other spring end pressing against annular spring seat 14.
  • the spring seat 14 is slidably mounted on rod 10 and engages a slide ring 15 engaged with the socket wrench 3 which is slidably journaled in wrench holder 8 but is non-rotatary in relation thereto so as to rotate with the holder.
  • the socket wrench is replaceably mounted in the tool, the mounting including telescoping sleeves 17, 18 which surround the wrench holder 8, sleeve 18 being attached to impact device housing 7 while sleeve 17 is attached to the holder by screws 16, a helical spring 19 being mounted between the telescoping sleeves and locking balls 20 being arranged in an annular space 21 between the socket wrench 3 and the sleeve 17 to exert a radial pressure on the wrench and maintain it in the holder.
  • the sleeve 17 may be moved axially into sleeve 18 to release the radial pressure on balls 20 so as to enable the wrench 3 to be removed from the holder.
  • the outwardly biased socket wrench 3 is at rest when it is engaged with a bolt head until the tool is moved down to depress the wrench and move it axially inwardly in respect of wrench holder 8 against the bias of compression spring 12.
  • This causes a corresponding axial movement of the rod 10 and the impact device 2, which is coupled therewith, to engage clutch 11 and thus to couple the wrench to driving motor 1.
  • the bolts will not be damaged by rotating tool parts when they are first engaged.
  • the wrench after the bolt has been fastened or unfastened, depending on the direction of rotation of the wrench, and the tool is lifted again to permit the wrench to be outwardly biased under the pressure of spring 12, the wrench will be at rest again so taht no jamming will occur due to torque forces applied to the bolt.
  • FIG. 2 shows a mobile machine for simultaneously fastening a pair of rail fastening bolts 28 arranged on respective sides of a track rail 26, as is common to fasten the rails of a railroad track to the ties 27.
  • the machine comprises a partially illustrated frame 24 mounted for mobility on the track by means of running gears 25. If desired, such a'mobile machine may be used in conjunction with suitable machinery for renewing the track, wherein it is necessary first to remove rail fastening bolts 28 from the old rails and then to fasten the bolts on the new rails.
  • the machine frame 24 has guide rails 29 extending in the direction of the track and cross rails extending transversely thereof to enable a plurality of tool carriers 30 to be moved relatively to each other and to the frame, the tool carriers being spaced from each other and each vertically adjustably supporting a pair of impact socket wrench tools 23 arranged for simultaneous engagement with a respective pair of rail fastening bolts 28.
  • the tools are of the type described hereinabove and illustrated in FIG. 1.
  • two tool carriers 30 are associated with each rail 26 and are movably mounted on the frame spaced from each other in the direction of the track so that work may be done simul taneously on two successive rail fastening means, each carrier running on rollers 31 on the track rails so that the tools may be centered above the respective rail fastening bolts 28, working being done simultaneously on eight bolts by this arrangement.
  • a registering boss or dog 32 is associated with each pair of socket wrench tools 23 to cooperate with a part of the rail fastening means.
  • a hydraulic motor 33 is operatively connected with each registering boss so as to lift the same when the machine is moved along the track and lower it into engagement with a cooperating rail fastening means part when the machine is at rest.
  • Each carrier is individually positionable so as to take into account differing crib widths, the spacing between two carriers associated with the same rail 26 being automatically adjustable by an interconnecting hydraulic motor 34 or any other suitable adjustable spacing device, such as a threaded spindle drive.
  • the machine frame 24 may continue to move along the track while the tool carriers remain at rest, i.e., while the tools are operated, since the carriers 30 may be continuously moved along guide rails 29. After each operation, the coupled tool carriers 30 may be rapidly moved to the next pair of ties by means of a drive 35 operatively connected to one of the carriers.
  • FIG. 3 shows a manually movable machine of this general type, wherein wheelbarrow-like carriage 39 supports a pair of hydraulically driven socket wrench tools 36 of the same type as shown in FIG. 1 for simultaneously working on a pair of rail fastening bolts 28 arranged on respective sides of track rail 26.
  • the carriage 39 comprises a running gear 39b and a carrier beam 39a is mounted on the running gear for vertical and horizontal pivoting movement about a universal pivot 39c.
  • the running gear is positioned intermediate the ends of the carrier, and handle 40 is mounted on one end of the carrier beam while the pump 37 for delivering hydraulic fluid to the driving motors of the tools 36 and a motor 38 for driving the pump 37 are mounted on the other carrier end.
  • a means 41 for adjusting the driving motor torque is provided, the illustrated means comprising a control in the hydraulic fluid delivery line to adjust the fluid pressure delivered to the driving motors and thus the rotational speed of the motors.
  • a control line operated by lever 42 mounted on handle 40 enables an operator to adjust the control 41.
  • An impact socket wrench tool comprising 1. a socket wrench capable of rotary motion about the axis thereof and of reciprocatory sliding motion in the direction of the axis,
  • the impact socket wrench tool of claim 1 further comprising a compression spring means mounted between the wrench and the impact device to couple the wrench resiliently to the impact device and driving motor.
  • the impact socket wrench tool of claim 4, wherein the impact device comprises two cooperating parts, one of the impact device parts being coupled to the wrench and the other impact device part being coupled to the driving motor.
  • the impact socket wrench tool of claim 4 further comprising a jaw clutch between the impact device and the vibration absorbing means.
  • a mobile machine for simultaneously fastening a pair of rail fastening bolts arranged on respective sides of a track rail comprising 1. a frame mounted for mobility on the track, and
  • each tool comprising a. a socket wrench capable of rotary motion about the axis thereof and of reciprocatory sliding motion in the direction of the axis,
  • a vibratory impact device mounted between the driving motor and the socket wrench for effectuating the reciprocatory sliding motion during r0- tation of the wrench
  • the mobile machine of claim 7 further comprising means for adjusting the driving motor torque.
  • the frame is a wheelbarrow-like carriage, and further comprising a pump for delivering hydraulic fluid to the driving motors and motor means driving the pump.
  • wheelbarrow-like carriage comprises a running gear, a carrier having two ends mounted on the running gear for vertical and horizontal pivoting movement, the running gear being positioned intermediate the ends of the carrier, handle means at one of the carrier ends, and the pump and motor means being mounted on the other carrier end.
US00195278A 1970-12-17 1971-11-03 Impact socket wrench tool Expired - Lifetime US3759334A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT1135070A AT312652B (de) 1970-12-17 1970-12-17 Schalagschraubmaschine, insbesondere für Schienenbefestigungsschrauben

Publications (1)

Publication Number Publication Date
US3759334A true US3759334A (en) 1973-09-18

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ID=3628229

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US00195278A Expired - Lifetime US3759334A (en) 1970-12-17 1971-11-03 Impact socket wrench tool

Country Status (18)

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US (1) US3759334A (it)
JP (1) JPS5511478B1 (it)
AT (1) AT312652B (it)
AU (1) AU462654B2 (it)
CA (1) CA951151A (it)
CH (1) CH546128A (it)
DE (1) DE2147383C2 (it)
ES (1) ES397522A1 (it)
FR (1) FR2118600A5 (it)
GB (1) GB1346337A (it)
HU (1) HU170484B (it)
IT (1) IT940673B (it)
NL (1) NL171475C (it)
RO (1) RO59317A (it)
SE (1) SE376269B (it)
SU (1) SU700071A3 (it)
YU (1) YU35175B (it)
ZA (1) ZA717318B (it)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4183265A (en) * 1974-11-12 1980-01-15 Ingersoll-Rand Company Controlled torque air motor
US5398616A (en) * 1993-08-06 1995-03-21 Oak Industries, Inc. Automatic rail fastener applicator
US5577447A (en) * 1995-06-12 1996-11-26 Oak Industries, Inc. Automatiac railway fastener remover
US5671679A (en) * 1996-04-24 1997-09-30 Nordco Inc. Fully automatic, multiple operation rail maintenance apparatus
US6733414B2 (en) 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
US20150343579A1 (en) * 2014-05-30 2015-12-03 Fanuc Corporation Nut runner with core runout preventing mechanism
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
US10471573B2 (en) 2016-01-05 2019-11-12 Milwaukee Electric Tool Corporation Impact tool
CN112119189A (zh) * 2018-05-29 2020-12-22 罗贝尔铁路建筑机械有限责任公司 用于拧紧和松开轨道上的螺母和螺钉的冲击扳手
US20220250216A1 (en) * 2018-02-19 2022-08-11 Milwaukee Electric Tool Corporation Impact tool
US11484997B2 (en) * 2018-12-21 2022-11-01 Milwaukee Electric Tool Corporation High torque impact tool
US11707818B2 (en) 2019-09-20 2023-07-25 Milwaukee Electric Tool Corporation Two-piece hammer for impact tool
US11964368B2 (en) * 2022-05-02 2024-04-23 Milwaukee Electric Tool Corporation Impact tool

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT326714B (de) * 1973-11-28 1975-12-29 Plasser Bahnbaumasch Franz Schlagschraubmaschine, insbesondere für schienenbefestigungsschraueen
IT1221161B (it) * 1984-02-24 1990-06-21 Danieli Off Mecc Gruppo di lavoro perfezionato per imbullonatrice ed imbullonatrice adottante tale gruppo di lavoro
DE102007018282B4 (de) * 2007-04-18 2019-10-02 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Zweifachschraubvorrichtung
GB2594113A (en) * 2020-12-03 2021-10-20 Rolls Royce Plc Nuclear power plant system

Citations (4)

* Cited by examiner, † Cited by third party
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US2049273A (en) * 1932-10-06 1936-07-28 Robert H Pott Impact tool
US2707892A (en) * 1953-01-21 1955-05-10 Jones & Lamson Mach Co Impact-type chuck wrench
US3585817A (en) * 1969-08-19 1971-06-22 Black & Decker Mfg Co Adjustable clutch construction
US3628461A (en) * 1968-10-25 1971-12-21 Plasser Bahnbaumasch Franz Machine for working on rail fastening elements

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2339531A (en) * 1941-12-12 1944-01-18 Cleveland Pneumatic Tool Co Nut setter
DE1085182B (de) * 1957-07-22 1960-07-14 Matisa Materiel Ind Sa Auf einem Eisenbahngleis fahrbare Maschine zum Ein- und Ausdrehen von Schwellenschrauben
DE1265677B (de) * 1958-12-24 1968-04-04 Rheinstahl Henschel Ag Vorrichtung zum gleichzeitigen Einschrauben mehrerer ausgerichtet zugefuehrter kopfloser Schrauben, insbesondere Stiftschrauben
DE1212572B (de) * 1961-05-03 1966-03-17 Roger Lacan Schraubmaschine zum Eindrehen von Schwellenschrauben od. dgl.
DE1478809A1 (de) * 1962-09-15 1969-02-20 Bosch Gmbh Robert Motorisch angetriebener Drehschlagschrauber

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2049273A (en) * 1932-10-06 1936-07-28 Robert H Pott Impact tool
US2707892A (en) * 1953-01-21 1955-05-10 Jones & Lamson Mach Co Impact-type chuck wrench
US3628461A (en) * 1968-10-25 1971-12-21 Plasser Bahnbaumasch Franz Machine for working on rail fastening elements
US3585817A (en) * 1969-08-19 1971-06-22 Black & Decker Mfg Co Adjustable clutch construction

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4183265A (en) * 1974-11-12 1980-01-15 Ingersoll-Rand Company Controlled torque air motor
US5398616A (en) * 1993-08-06 1995-03-21 Oak Industries, Inc. Automatic rail fastener applicator
US5465667A (en) * 1993-08-06 1995-11-14 Oak Industries, Inc. Modular railway maintenance system
US5577447A (en) * 1995-06-12 1996-11-26 Oak Industries, Inc. Automatiac railway fastener remover
US5671679A (en) * 1996-04-24 1997-09-30 Nordco Inc. Fully automatic, multiple operation rail maintenance apparatus
US6733414B2 (en) 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
US9902029B2 (en) * 2014-05-30 2018-02-27 Fanuc Corporation Nut runner with core runout preventing mechanism
US20150343579A1 (en) * 2014-05-30 2015-12-03 Fanuc Corporation Nut runner with core runout preventing mechanism
US10471573B2 (en) 2016-01-05 2019-11-12 Milwaukee Electric Tool Corporation Impact tool
US20220250216A1 (en) * 2018-02-19 2022-08-11 Milwaukee Electric Tool Corporation Impact tool
CN112119189A (zh) * 2018-05-29 2020-12-22 罗贝尔铁路建筑机械有限责任公司 用于拧紧和松开轨道上的螺母和螺钉的冲击扳手
CN115042117A (zh) * 2018-05-29 2022-09-13 罗贝尔铁路建筑机械有限责任公司 用于拧紧和松开轨道上的螺母和螺钉的冲击扳手
US11787017B2 (en) 2018-05-29 2023-10-17 Robel Bahnbaumaschinen Gmbh Impact wrench for tightening and loosening nuts and screws on a track
US11484997B2 (en) * 2018-12-21 2022-11-01 Milwaukee Electric Tool Corporation High torque impact tool
US20230080957A1 (en) * 2018-12-21 2023-03-16 Milwaukee Electric Tool Corporation High torque impact tool
US11938594B2 (en) * 2018-12-21 2024-03-26 Milwaukee Electric Tool Corporation High torque impact tool
US11707818B2 (en) 2019-09-20 2023-07-25 Milwaukee Electric Tool Corporation Two-piece hammer for impact tool
US11964368B2 (en) * 2022-05-02 2024-04-23 Milwaukee Electric Tool Corporation Impact tool

Also Published As

Publication number Publication date
JPS5511478B1 (it) 1980-03-25
AU462654B2 (en) 1975-07-03
DE2147383A1 (de) 1972-07-13
IT940673B (it) 1973-02-20
AT312652B (de) 1974-01-10
YU278671A (en) 1980-03-15
CH546128A (de) 1974-02-28
SU700071A3 (ru) 1979-11-25
RO59317A (it) 1976-01-15
NL171475C (nl) 1983-04-05
DE2147383C2 (de) 1982-06-16
CA951151A (en) 1974-07-16
AU3679671A (en) 1973-06-14
NL171475B (nl) 1982-11-01
GB1346337A (en) 1974-02-06
YU35175B (en) 1980-09-25
SE376269B (it) 1975-05-12
ES397522A1 (es) 1974-05-16
HU170484B (it) 1977-06-28
ZA717318B (en) 1972-07-26
NL7112939A (it) 1972-06-20
FR2118600A5 (it) 1972-07-28

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