US3108506A - Rotary impact tools - Google Patents

Rotary impact tools Download PDF

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Publication number
US3108506A
US3108506A US64119A US6411960A US3108506A US 3108506 A US3108506 A US 3108506A US 64119 A US64119 A US 64119A US 6411960 A US6411960 A US 6411960A US 3108506 A US3108506 A US 3108506A
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United States
Prior art keywords
handle
spring
inertia member
teeth
stampings
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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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US64119A
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English (en)
Inventor
Oscar J Swenson
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Individual
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Individual
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Publication date
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Priority to US64119A priority Critical patent/US3108506A/en
Priority to GB37043/61A priority patent/GB996603A/en
Priority to DE19611503040 priority patent/DE1503040A1/de
Priority to AT793561A priority patent/AT244879B/de
Priority to CH1220861A priority patent/CH376864A/fr
Application granted granted Critical
Publication of US3108506A publication Critical patent/US3108506A/en
Anticipated expiration legal-status Critical
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B13/00—Spanners; Wrenches
    • B25B13/46—Spanners; Wrenches of the ratchet type, for providing a free return stroke of the handle
    • B25B13/461—Spanners; Wrenches of the ratchet type, for providing a free return stroke of the handle with concentric driving and driven member
    • B25B13/462—Spanners; Wrenches of the ratchet type, for providing a free return stroke of the handle with concentric driving and driven member the ratchet parts engaging in a direction radial to the tool operating axis
    • B25B13/463—Spanners; Wrenches of the ratchet type, for providing a free return stroke of the handle with concentric driving and driven member the ratchet parts engaging in a direction radial to the tool operating axis a pawl engaging an externally toothed wheel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B19/00—Impact wrenches or screwdrivers

Definitions

  • This invention relates to an improved impact-producing tool preferably of manually operated type such, for examples, as Aare shown in my U.S. Patents Nos. 2,661,- 647, December 8, 1953; 2,844,982, July 29, 1958, and 2,954,714, October 4, 1960l (SN. 773,229).
  • the power spring, ⁇ as in the tool of the present application is a helical coil compression spring disposed lengthwise of and fully enclosed by a tubular portion of a handle member of the wrench; but said handle member in the patent required several parts adapted for heavy duty operation.
  • the handle member is considerably simplified for easier manufacture and is otherwise especially adapted to serve ⁇ for light duty wrenching service.
  • bjects or novel lfeatures of the present invention include provision of an improved pawl and ratchet mechanism and associated part-s enabling the inerti-a member or rotor to be made inexpensively from sintered powdered metal or ⁇ from integrally joined sheet metal stampings; a simplified and inexpensive main or power compression coil spring assembly construction; an improved sheet metal handle construction capable of rapid 'and secure assembly with other parts so as, if desired, to completely enclose all but output shaft portions ofthe tool yand preferably so as to use the force of the power spring in latching or locking of fthe sheet metal components of the handle together.
  • Another object or novel feature is the pnovision of effectual shock absorbing means in the construction of stop members on the handle assembly and the rotor or inertia member, which stop members, when :in abutment, establish, through residual force in the power spring, an initial relative positioning of the handle and rotor after occurrence of each impact operation.
  • Another object is to provide a simple and effectual purpose-conversion means settable to condition the tool hereof selectively for operation as a rotary impact wrench and as an ordinary ratchet wrench.
  • FIG. 1 is a top or lassembly plan view of an impact wrench hereof, partly in axial central section and otherwise generally as the tool would appear with one of two hollow sheet metal handle-constituting members removed.
  • FIG. 2 is ⁇ a fragmentary side elevation of the tool, partly in section as along the line 2 2 on FIG. 1.
  • FIG. 2a isa cross sectional view as indicated at Ztl-2a on FIG. 1.
  • FIG. 2b is a detail view of a spring and rotor connecting piece taken as indicated at 21a-2b on FIG. 1.
  • FIG. 3 is a ⁇ fragmentary view somewhat similar to FIG. 1 showing power-spring-associated modifications land a modified shock absorbing rotor stop construction.
  • FIG. 3a is a fragmentary side elevation of the tool head or output end portion of the -tool according to FIG. 3.
  • FIG. 4 is a sectional view taken along the line y4 4 on FIG. 3 complementing the latter in showing one ⁇ form of latch or lock for holding portions of the handle-forming stampings together.
  • FIG. 5 is a reduced scale view of an inertia member or rotor positioned as in FIG. 2 and partly in central section, the vie-w showing more or less diagrammatioally the manner in which the rotor can be made wholly from identical sheet metal stampings.
  • the tool lor tool assembly SW hereof comprises, as shown by comparison of FIGS. 1 and 2, an outpu-t shaft or tool head T hav-ing a ratchet toothed portion 10 coaxially thereof between its work engaging end portions 9 ⁇ and 11; a handle H extending laterally of the shaft; an annular inertia member or rotor W surrounding the ratchet toothed portion 1G; bearing means (eg. bushings 6, 7 rigid with the handle) guiding the shaft, handle and the Iinertia member for angular movement relative to each other about the 4axis L, FIG.
  • bearing means eg. bushings 6, 7 rigid with the handle
  • the sheet metal half shells Zand 3I (similarly shells 2a and 3a in FIGS. 3 and 3a) are securely and demountably held together in the region of tool head T, preferably in the same manner as in my said patents, namely by spring 3 metal snap rings R in respective grooves formed in the cylindrical portions 5 and 5" of the tool head.
  • the snap rings are yapproximately in abutment with the side plate portions 2 and 3' respectively.
  • Handle Construction Handle H of the present impact wrench SW is constituted or formed mainly by two relatively heavy mutually complementary metallic half shell stampings 2 and 3 of operatingly identical shape and which, as viewed similarly to the showing of shell 3 in FIG. l, are bisymmetrical about the longitudinal axis L of the handle. Between the two ends of the handle the stampings are gradually narrowed from opposite directions, establish ⁇ ing a more or less cylindrical neck at region H; and near the free end portion of the handle remotely of the tool head T the cross section is gradually enlarged and then diminished to form a generally bulbous hand-hold portion H merging gradually with region H.
  • Portion H is generally oval or at least non-circular in cross section as shown for example in FIG. 2a (cf. FIG. 4).
  • each shell (as at 3a and 3b FIG. l) come substantially into abutment with peripheral surfaces of the rotor W so that only cylindrical peripheral surfaces of the rotor are ever exposed; and the handle-constituting shells 2 and 3 are completed in the region of the rotor by the parallel flat side portons 2' and 3 which partially cover the ends of the rotor and support the bearing bushings 6 and 7 as clearly shown in FIG. 2.
  • the shells 2 and 3 have complemental end wall formations 24 (described later) forming parts of a supporting or base assembly 2t) for a power-spring-forceestablishing screw 22, which assembly includes releasable means (to be described later) for latching or locking the hand-hold portions of the shells 2 and 3 together.
  • Power or main spring S assuming the spring, as shown in FIG. 1, to be subjected to some axial compressive stress, is self-supporting in the hollow handle H between, on the one hand, a push rod or link supported at one end solely by a laterally llexible end portion of the spring (FIGS. 1 and 2b) and which has a rounded head 15a detachably engaging a mating trough shaped seat 16 on the rotor W tangentially or eccentrically of the rotor axis and, on the other hand, the assembly via its screw 22.
  • the screw 22 has a rounded or conical tip 22 seated in a complementary axial socket in a head 17 of a rod or bar 17 which extends a considerable distance within the coils of the rightward or outer end portion of the power spring S and holds those coils in approximate alignment.
  • Push rod 15 (left, FIG. 1;-cf. FIG. 2b), has a shank portion 15' (shown curved), shouldered at 15" for operative abutment with the adjacent end coil of the spring S.
  • the curved portion 15 of push rod 15 and the rod 17, each for approximately their entire lengths, are fairly loose in their associated spring coils or so as to enable or permit free axial exing of the power spring S in a plane normal to the working axis L, FIG. 2, while initially tending to maintain the spring in its illustrated shape or form.
  • Trough device 18 is made preferably, of heat treated metal or similar high wear resistant metal.
  • Trough 18 is of C-shaped cross section (FIG. 2a) being maintained against turning out of its illustrated position about the longitudinal axis of the spring S by a ange assembly portion 18a, 13b which is held in place between the rightward end of the spring S and the head 17 of guide rod 17 by axial force of the spring.
  • Portion 18b of the spring guide assembly may, as shown in FIG. 2a,
  • the head 15a of push rod 15 is preferably partly cylindrical as illustrated in FIG. l; and the mating trough or seat 16 in the rotor W for head 15a extends for the full height of the rotor parallel to axis L thereof. Further, the head 15a of the push rod is elongated (FIG. 2b) parallel to the axis L in a manner tending to stablize the leftward end of the power spring assembly against rotating out of proper position.
  • the spring-force-setting screw 22 (right FIGS. l and 2) is demountably and adjustably supported by threaded engagement with a non-rotary thrust plate 23 of generally cupshaped form, providing a continuous annular (circular or non-circular) flange 25 embracing the margins of inturned mutually complementary ilanges 24' on the respective end wall portions 24 of the handle-constituting shells 2 and 3.
  • the head 22a of the screw having for example a socket for an Allen type wrench, is shown in normal position in FIG. l jammed for example against the thrust plate 23 to hold the power spring in its desired full strength position. Such position can thus be easily changed by selecting diierent length screws 22.
  • FIG. 2 shows at 22x the position of the head of screw 22 when the power spring is fairly completely relaxed.
  • a spring arm 60 is attached to the head 117' and its free end extends through a hole in a slidable exible metal dirt guard plate 61 to show by its position the condition of compression of the power spring (power level).
  • the cushioning stop assembly or unit 36 as shown in FIG. l comprises a metal cap 37 formed as a channel with diverging ilanges; a rigid metallic supporting block or anvil 33 of generally triangular form as shown in FlG. l and an interposed elastic cushion pad 39 such as a channel shaped piece of oil resistant rubber or elastomer the faces of which pad are complementary to inside and outside faces of the cap 37 and block or anvil 38 respectively and bonded thereto.
  • the block or anvil members 38 of the two stop assemblies 36 may be secured to the respective side plate portions 2' and 3 of stampings 2 and 3 by rivets 38a in positions such that the side walls 2b and 3b of the handle members are in tight abutment with the anvil members effectively to integrate the latter with the handle.
  • Self damping characteristics for unit 36 may be had by appropriate selection of material for pad 39.
  • Such construction cushions shock by temporary elastic yielding of the flange portions of member 37 accompanied by damping frictional resistance to movement of the members into full mating contact.
  • the 3 is generally U-shaped providing a iixed arm or anvil portion 38 suitably secured to the associated handle member as by a rivet 38a in tight abutment with side wall portions 2b and 3b and a flexible arm or cushion portion 37 separated by a gap 39' of proper small dimension from the fixed arm.
  • the arms 37 and 38 when brought into abutment t us serve as would a limiting fixed stop to prevent the rotor W from passing a specifically determined point.
  • the dimension of the gap 39' is chosen so as to limit the relative deflection of the spring arms to a distance within the elastic limit of the metal.
  • the force with which the defining surfaces of the gap 39 strike each other is always less than the force of stop SSagainst a fixed abutment (as in patent No. 3) because of the reduction in striking energy resulting from deceleration of the rotor while deflecting the free arm 37 of the spring stop.
  • the pawls 4 have sulicient space in their sockets or recesses da in the rotor W defined in part by respective end portions il so that the pawls can move to disengage the ratchet teeth; and, as more elaborately explained in all three of said patents, the pawls 4 are forced as by the cam surfaces 8 of ⁇ bushings 6 and 7 out oi engagement with the teeth after approximately a 37 angular motion of handle H.
  • Movement of the handle H as mentioned increases the energy in or compression of the power spring S so long as the pawls remain obstructed against angular movement with the handle (tool head 5 remaining stationary); wherefore as soon as the pawls are moved out of abutment with their associated ratchet tooth faces by the cam surfaces 8 as a function of overrunning of the handle relative to the inertia member and tool head, the highly stressed power spring S suddenly turns the rotor W until its pawls 4 forcibly strike the next adjacent set of tooth faces.
  • the rotor W is designed with sufficient inertia so that the just described escapement and torsional impact operation of the tool SW is highly effectual in freeing frozen threaded fasteners and of course in tightening such fasteners to predetermined bolt tension values.
  • Ratchet Wrench Conversion Feature It has been noted that in order for the tool SW to operate as described the stop faces a and 36a must be separated between successive impacts distances somewhat greater than the 30 angular spacing of the ratchet teeth. If such separating movement is blocked then oscillating or indexing movements of the handle (e.g., greater than 30 degrees) will result in pure 30 ratcheting actions of the tool on an associated fastener. Selective blocking at the will of the operator is accomplished as illustrated principally in FIG. l by a pawl or lever pivotally mounted 'on one of the side plate portions 2' or 3 and having an externally exposed operating handle 46. The position of the lever 45 for enabling ordinary ratchet wrench action is indicated at 45x.
  • Rotor Construction The herein disclosed construction of rotor W and associated parts enables the rotor to be economically manuvfactured from sintered powdered metal by conventional ⁇ .means in separable dies as well understood in the metal Working arts, and, alternatively, to be economically made from identical integrally joined sheet metal stampings.
  • the pawls 4 in the present case can get out of their sockets la only by movement tangentially of the central 1core of the rotor for receiving the ratchet wheel y lll it is possible to block all but the operating pivotal movements of the pawls by forming arcuate stop surfaces in the rotor block concentric with the pivot axes of the pawls for abutment with the pawl tips.
  • the tips may but need not be formed complementary to the arcuate surfaces.
  • stampings w can be made of fairly heavy gage sheet metal (due to absence of small radii and sharp corners as well understood) thereby economizing in assembly time and reducing likelihood of warpage of the individual stampings incident to rapid change of temperatures involved in brazing, welding, etc.
  • a manually operable torque transmitting impact tool comprising an output shaft having a circular series of teeth thereon coaxially thereof, a handle having a handhold portion extending laterally of the shaft, an annular inertia member surrounding the teeth, bearing means guiding the shaft, handle and the inertia member for angular movement relative to each other about the axis of the shaft, a pawl movably supported on the inertia member and biased for engagement with the teeth, and a cam ⁇ connected for movement with the handle and operable against the pawl as a function f angular relative movement of the handle and the inertia member in a predetermined direction to enable successive escapements and impacts between the pawl and the teeth
  • the handle comprising two mutually complementary hollow sheet metal stampings having side plate portions overlapping the inertia member, means demountably connecting the side plate portions to the output shaft, cooperating means remotely of the shaft and demountably interconnecting the stampings to unify the handle, a
  • said device is an annular member having a central opening permanently exposed between said end-wall-constituting portions of the stampings, and a spring-force-establishing screw in threaded engagement with a device in operative t abutment with the spring axially thereof, the screw having a head portion accessible through the annular member from a position externally of the handle to enable rotational adjustment of the screw.
  • a torque transmitting impact tool comprising an elongated handle member, a tool head member having a ⁇ series of equally spaced circumferentially disposed teeth, an inertia member, bearing means guiding said members for relative angular movement about a common axis, a ,pawl movably mounted on the inertia member, turning therewith about said axis and spring biased toward the teeth for movement into and out of abutting relationship ywith the teeth, and power spring and cam mechanism 'between the handle member and inertia member and capable of operation as a function of angular overrunning movement of the handle member relative to the inertia member and tool head member to cause escapement and impact-producing reengagement of the pawl with said teeth, said mechanism including a helical spring and means securing one end portion thereof in fixed position on the handle remotely of the inertia member while enabling compression and elongation of the spring, the 0pposite end portion being flexibly movable laterally in
  • a manually operable impact tool comprising a rotary tool head, a hollow handle extending transversely of. tool head axis, an annular inertia member around the tool head, and bearing means guiding the tool head, handle and inertia member for relative angular movement about said axis; a ratchet wheel operatingly integral with the tool head, a pawl movably supported on the inertia member, biased for engagement with the ratchet wheel and disengageable from the ratchet wheel, and cam means rigid with the handle around said axis and operatingly connected with the pawl to disconnect it from, for reengagement with, the ratchet Wheel to impart torque-producing impact to the tool heads; an elongated compression spring within the handle for storing and releasing energy for such impacts, means supporting one elongated end portion of the compression spring in fixed relation to the handle while allowing the spring to contract and expand longitudinally during operation of the tool, an opposite end portion of the spring being free from said spring
  • shock absorbing means include elastic non-metallic cushion material.
  • said one of the stop members comprises a metal channel having flange portions dverging away from the other stop member and a cooperating rigid support having similarly diverging surface portions.
  • said one of said stop members is a metal spring having abutment means limiting the flexing movement thereof under impact.
  • said one of the stop members is a U-shaped piece of spring metal having mutually adjacent but spaced apart arm portions so disposed in the tool that the force involved in such forcible abutment tends to flex one of the arm portions into arrested contact with the other arm portion.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Component Parts Of Construction Machinery (AREA)
  • Amplifiers (AREA)
US64119A 1960-10-21 1960-10-21 Rotary impact tools Expired - Lifetime US3108506A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US64119A US3108506A (en) 1960-10-21 1960-10-21 Rotary impact tools
GB37043/61A GB996603A (en) 1960-10-21 1961-10-16 Torque transmitting impact tool
DE19611503040 DE1503040A1 (de) 1960-10-21 1961-10-20 Drehschlagwerkzeug
AT793561A AT244879B (de) 1960-10-21 1961-10-20 Drehschlagwerkzeug
CH1220861A CH376864A (fr) 1960-10-21 1961-10-21 Outil à percussion à tête dentée rotative

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US64119A US3108506A (en) 1960-10-21 1960-10-21 Rotary impact tools

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US3108506A true US3108506A (en) 1963-10-29

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US64119A Expired - Lifetime US3108506A (en) 1960-10-21 1960-10-21 Rotary impact tools

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US (1) US3108506A (fr)
AT (1) AT244879B (fr)
CH (1) CH376864A (fr)
DE (1) DE1503040A1 (fr)
GB (1) GB996603A (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3180185A (en) * 1961-07-06 1965-04-27 Curtiss Wright Corp Accessory or adjunct for manual impact wrenches
US3184998A (en) * 1963-07-15 1965-05-25 Curtiss Wright Corp Impact wrench with stabilizer handle
US4184552A (en) * 1977-05-17 1980-01-22 Marquette Metal Products Company Manually actuated impact tool
US4243109A (en) * 1979-06-07 1981-01-06 Marquette Metal Products Company Bi-directional rotary impact tool for applying a torque force
US4382476A (en) * 1981-12-03 1983-05-10 Swenson Oscar J Manual torque magnifying impact tool
US4418768A (en) * 1982-09-02 1983-12-06 Swenson Oscar J Manual torque magnifying impact tool
US20060174467A1 (en) * 2005-01-18 2006-08-10 Rastegar Jahangir S Manually operated impact tool
US7258048B2 (en) * 2005-04-16 2007-08-21 Omnitek Partners L.L.C. Manually operated impact wrench
CN104070486A (zh) * 2014-06-19 2014-10-01 何华忠 直打扳手

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113352259A (zh) * 2021-07-13 2021-09-07 宁国市利远精密制造厂 一种手动冲击扳手

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE19341E (en) * 1934-10-16 Ratchet wrench and method of
US2086261A (en) * 1936-06-22 1937-07-06 Independent Pneumatic Tool Co Hammer wrench
US2112693A (en) * 1937-06-16 1938-03-29 Independent Pneumatic Tool Co Portable hammer wrench
US2578687A (en) * 1947-03-10 1951-12-18 Tubing Appliance Company Inc Split ratchet socket wrench
US2661647A (en) * 1950-07-11 1953-12-08 Oscar J Swenson Ratchet type impact tool
US2688268A (en) * 1953-03-31 1954-09-07 Chicago Pneumatic Tool Co Stoper drill with rotary impact attachment
US2776588A (en) * 1954-12-30 1957-01-08 Frank W Livermont Hand-operated impact torque wrench
US2844982A (en) * 1956-06-21 1958-07-29 Oscar J Swenson Ratchet-type, manually actuated, rotary impact tool
US2910901A (en) * 1954-04-15 1959-11-03 Atlas Copco Ab Pneumatic bolt applying and tightening tool
FR1239894A (fr) * 1958-11-12 1960-08-26 Outils à percussion à commande manuelle
US2954714A (en) * 1958-11-12 1960-10-04 Oscar J Swenson Manually actuated rotary impact tool

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE19341E (en) * 1934-10-16 Ratchet wrench and method of
US2086261A (en) * 1936-06-22 1937-07-06 Independent Pneumatic Tool Co Hammer wrench
US2112693A (en) * 1937-06-16 1938-03-29 Independent Pneumatic Tool Co Portable hammer wrench
US2578687A (en) * 1947-03-10 1951-12-18 Tubing Appliance Company Inc Split ratchet socket wrench
US2661647A (en) * 1950-07-11 1953-12-08 Oscar J Swenson Ratchet type impact tool
US2688268A (en) * 1953-03-31 1954-09-07 Chicago Pneumatic Tool Co Stoper drill with rotary impact attachment
US2910901A (en) * 1954-04-15 1959-11-03 Atlas Copco Ab Pneumatic bolt applying and tightening tool
US2776588A (en) * 1954-12-30 1957-01-08 Frank W Livermont Hand-operated impact torque wrench
US2844982A (en) * 1956-06-21 1958-07-29 Oscar J Swenson Ratchet-type, manually actuated, rotary impact tool
FR1239894A (fr) * 1958-11-12 1960-08-26 Outils à percussion à commande manuelle
US2954714A (en) * 1958-11-12 1960-10-04 Oscar J Swenson Manually actuated rotary impact tool

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3180185A (en) * 1961-07-06 1965-04-27 Curtiss Wright Corp Accessory or adjunct for manual impact wrenches
US3184998A (en) * 1963-07-15 1965-05-25 Curtiss Wright Corp Impact wrench with stabilizer handle
US4184552A (en) * 1977-05-17 1980-01-22 Marquette Metal Products Company Manually actuated impact tool
US4243109A (en) * 1979-06-07 1981-01-06 Marquette Metal Products Company Bi-directional rotary impact tool for applying a torque force
US4382476A (en) * 1981-12-03 1983-05-10 Swenson Oscar J Manual torque magnifying impact tool
US4418768A (en) * 1982-09-02 1983-12-06 Swenson Oscar J Manual torque magnifying impact tool
US20060174467A1 (en) * 2005-01-18 2006-08-10 Rastegar Jahangir S Manually operated impact tool
US7255029B2 (en) * 2005-01-18 2007-08-14 Omnitek Partners L.L.C. Manually operated impact tool
US7258048B2 (en) * 2005-04-16 2007-08-21 Omnitek Partners L.L.C. Manually operated impact wrench
CN104070486A (zh) * 2014-06-19 2014-10-01 何华忠 直打扳手

Also Published As

Publication number Publication date
CH376864A (fr) 1964-04-15
AT244879B (de) 1966-01-25
DE1503040A1 (de) 1969-10-30
GB996603A (en) 1965-06-30

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