US3263449A - Impulse tool - Google Patents

Impulse tool Download PDF

Info

Publication number
US3263449A
US3263449A US325629A US32562963A US3263449A US 3263449 A US3263449 A US 3263449A US 325629 A US325629 A US 325629A US 32562963 A US32562963 A US 32562963A US 3263449 A US3263449 A US 3263449A
Authority
US
United States
Prior art keywords
cavity
spindle
fluid
members
zones
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
US325629A
Other languages
English (en)
Inventor
Kramer Leo
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.)
Thor Power Tool Co
Original Assignee
Thor Power Tool Co
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 to BE656130D priority Critical patent/BE656130A/xx
Application filed by Thor Power Tool Co filed Critical Thor Power Tool Co
Priority to US325629A priority patent/US3263449A/en
Priority to GB46838/64A priority patent/GB1023088A/en
Priority to DE19641503100 priority patent/DE1503100A1/de
Priority to NL6413435A priority patent/NL6413435A/xx
Priority to CH1500064A priority patent/CH447073A/de
Application granted granted Critical
Publication of US3263449A publication Critical patent/US3263449A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/14—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers
    • B25B23/145—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers
    • B25B23/1453—Arrangement of torque limiters or torque indicators in wrenches or screwdrivers specially adapted for fluid operated wrenches or screwdrivers for impact wrenches or screwdrivers

Definitions

  • This invention relates to improvements in rotary, power driven, torque applying tools, such as a wrench or the like for driving nuts, bolts, screws or other fasteners.
  • the torque generating mechanism includes a pair of non-impacting or non-striking, relatively rotatable, eccentrically spaced members, one of which is driven by a motor and the other of which is adapted to mount a tool such as a nut or bolt engaging socket or the like.
  • the space between the two members is filled with oil or other pressure transmitting liquid, and the internal structure is such that as one member rotates relative to the other, the pressure of the oil rapidly increases and decreases in a cyclic manner so as to create a series of impulses.
  • a primary object of the invention is to provide a novel and improved impulse tool of the general character described above.
  • a further object of the invention is to provide, in an impulse tool of the general character described, novel and improved means for obtaining impulses which does not involve the use of an eccentric rotating mass.
  • a more specific object of the invention is to provide, in an impulse tool of the aforementioned general character, an improved impulse generating means having a symmetrical structure and a balanced operation.
  • FIG. 1 is a front end elevational view of a tool comprising one specific embodiment of the invention
  • FIG. 2 is a side elevational view, partially in section, taken along the line 22 of FIG. 1;
  • FIG. 3 is a reduced scale end elevational view of a portion of the internal mechanism of the tool as seen along the line 3-3 of FIG. 2;
  • FIG. 4 is a view similar to FIG. 3 but taken at the op posite end of the internal mechanism along the line 4-4 of FIG. 2;
  • FIG. 5 is an enlarged scale horizontal sectional view of the internal mechanism taken along the line 55 of FIG. 2;
  • FIG. 6 is a transverse sectional view taken along the line 66 of FIG. 5;
  • FIGS. 7-9 are reduced scale sectional views, generally similar to FIG. 6, showing successive operating positions of the internal mechanism of the tool;
  • FIG. 10 is a sectional view generally similar to FIG. 5 but showing a modification of the invention.
  • FIG. 11 is a sectional view taken along the line 11-11 of FIG. 10;
  • FIG. 12 is a sectional view generally similar to FIG. 5 but showing a second embodiment of the invention.
  • FIG. 13 is a sectional view taken along the line 1313 of FIG. 12.
  • FIGS. 14l6 are reduced scale sectional views showing successive operating positions of the second embodiment.
  • the tool has a front casing section 21 and a rear casing section 22 with 3. depending handle portion 23, the front and rear casing sections being detachably connected, as by a plurality of cap screws 24.
  • the rear casing section 22 contains a rotary air-actuated motor of a conventional type designated generally at 26.
  • An air hose (not shown) may be connected to an air inlet connection 27 at the lower end of the handle portion 23, and the air supply to the motor as is controlled by means of a throttle valve assembly 28 movably mounted in the handle portion 23 and operable by a depressible trigger 29 for regulating the operation of the tool.
  • An impulse unit 31 is contained within the front casing section 21, as hereinafter described in greater detail.
  • the impulse unit 31 has a rotatable spindle with an elongated forward shaft portion 32 journaled in a hearing or bushing 33 which is mounted in an opening in the forward end of the casing section 21.
  • the outer terminus of the spindle portion 32 is provided with a square end 34 having a depressible detent 35 for detachably mounting a nut-or bolt-engaging socket or other tool member.
  • the impulse unit 31 comprises a housing assembly, indicated generally at 41, which is adapted to be driven by the air motor 26, and an internal spindle 42 having the forwardly projecting shaft portion 32 heretofore mentioned.
  • the housing assembly 41 includes an outer casing 43 having a flanged forward end 44 and an internally threaded rear end portion 46.
  • a cylinder bushing 47 (FIGS. 5 and 6) having a generally elliptical or oval shaped internal cylinder cavity 48 is tightly fitted within the outer casing 43 and is disposed between a pair of forward and rear cap members 49 and 51 (FIG. 5), respectively, with O-ring seals 52 mounted in suitable grooves in the inner faces of the respective cap members opposite the axial ends of the bushing 47.
  • the forward cap member 49 abuts the flange 44 and has a forwardly projecting tapered bearing portion 53 with a bore 50 which receives the spindle shaft portion 32.
  • a rotary O-ring seal 54 is mounted in an annular groove 55 in the bearing portion 53.
  • An annular locking ring or nut 56 threadedly engages the casing opening 46 and abuts the rear cap member 51 for retaining the impulse unit 31 in unitary assembled relation.
  • the front and rear cap members 49 and 51 are retained in predetermined orientation with respect to the elliptical cavity 48 of the bushing 47 by means of a plurality of roll pins 3 57 and 58 (FIGS. 3 and 4) which are fitted in suitable openings in the bushing and the respective cap members. As seen in FIG.
  • the inner periphery of the locking ring or nut 56 is provided with a plurality of recesses or serrations 59 so that after the nut 56 has been tightened to the desired extent, a set screw 60 can be inserted through one of the recesses 59 and threaded into a selected one of a plurality of threaded sockets 61 in the rear cap member 51 for locking the nut 56 in its tightened position.
  • the spindle 42 has an enlarged central portion 62 with a circular cross-sectional configuration disposed coaxially within the elliptical cylinder cavity 48 of the bushing 47, as best seen in FIG. 6.
  • a short integral stub shaft portion 63 projects rearwardly from the spindle portion 62 and is journaled in a socket 65 provided in a projecting boss portion 66 on the rear cap member 51.
  • the opposite end of the spindle 42 is journaled in the bearing portion 53 of the front cap member 49 by means of the elongated integral shaft portion 32 (FIG. 5) heretofore described.
  • the spindle shaft portions 32 and 63 are coaxial with the axis of rotation of the housing assembly 41.
  • the elliptical cylinder cavity 48 of the bushing 47 is filled with a suitable oil or other pressure transmitting liquid, and a detachable fill plug 71 (FIGS. 3 and 5) is provided in the front cap member 49 for filling the cavity 48 with oil.
  • a removable vent plug 72 (FIG. 3) is also provided in the cap member 49 adjacent the plug 71 for venting air from the cavity 48 during the introduction of oil.
  • the rear cap member 51 has a hexagonal drive connection 73 (FIG. 5) projecting from the boss portion 66 and engaging a driving socket connection 74 (FIG. 2) on the air motor 26.
  • the housing assembly 41 (comprising 43, 47, 49, 51, and 56) of the impulse unit 31 is rotated and, as described in detail below, fluid pressure impulses are generated in and are transmitted through the oil medium to the spindle 42.
  • the elliptical cavity 48 of the bushing 47 is provided with a pair of circumferentially extending recesses or undercuts, as designated at 81 (FIGS. 5 and 6), intermediate the opposite ends of the bushing 47.
  • These circumferential recesses 81 are interrupted by a pair of axially extending lands or seal points 82 diametrically disposed at the longer or major axis of the elliptical cavity 48 and also by a similar pair of lands or seal points 83 disposed at the shorter or minor axis of the cavity.
  • the distance between the lands 82 is appreciably greater than the distance between the lands 83.
  • the diameter of the circular spindle portion 62 is such that there is only a slight clearance between the spindle portion 62 and the lands 83 at the minor axis of the cavity 48.
  • the circular spindle portion 62 is provided with four radially extending slots 86 disposed at equal circumferential spacings around the spindle, and each slot 86 has an elongated blade 87 slidably mounted in closefitting relation therein with the blades 87 extending the full axial length of the spindle portion 62 and spanning the recesses 81, as best seen in FIG. 5.
  • the base or innermost end of each slot 86 is enlarged in the form of a circular axial-1y extending bore 88 (FIG. 6) so that the slot 86 and its connecting bore 88 have a keyhole shape in cross-section.
  • Each bore 88 communicates with the outer periphery of the spindle portion 62 through a pair of fluid pressure loading passages 89 machined in the spindle at one side of the corresponding slot 86.
  • the passages 89 are arranged in opposed relation at adjacent sides of a pair of blades 87 so that the corresponding bores 88 of each pair of blades 87 are placed in fluid communication with the same region of the oil filled cavity 48, for the purpose hereinafter described in greater detail.
  • a pair of compression springs 91 bear against the inner wall portion of each bore 88 and extend into a pair of bores 93 extending from the inner edge of each blade 87 for normally urging the blades 87 outwardly into contact with the wall of the bushing cavity 48.
  • the outer edge of each blade portion 87 is rounded or curved, as at 94, to provide intermittent sealing engagement with the lands 82 and 83 during relative rotation of the housing assembly and the spindle.
  • FIGS. 7-9 a typical operating cycle of the tool will be described. It will be assumed that the housing assembly 41, including the bushing 47, is being driven in a counter-clockwise direction by the air motor 26, as indicated by the arrow.
  • the square end 34 on the forward spindle shaft 32 is assumed to be in engagement through a suitable socket (not shown) with a fastener element (not shown) such as a nut or bolt which is to be tightened.
  • the housing assembly 41 begins to rotate relative to and ahead of the spindle 42.
  • the housing assembly 41 has rotated in a counter-clockwise direction relative to the spindle 42 so that the lands or seal points 82 and 83 have just left the outer ends 94 of the blades 87, which are separately identified as 87a, 87b, 87c, and 87:1.
  • the zones designated at 95 in the elliptical cavity 48 between blades 87a and 870 and between blades 87b and 87d are gradually decreasing in volume, whereas the zones designated at 95 in the cavity 48 between blades 87a and 87d and between blades 87b and 87c are gradually increasing in volume.
  • the oil or other pressure transmitting fluid in the cavity 48 is free to flow between the zones 95 and 95 through the recesses or undercuts 81 so that the pressure throughout the cavity 48 is substantially uniform.
  • the motor 26 continues to accelerate the housing 41 about the spindle 42.
  • FIG. 8 the housing 41 has rotated not quite from its FIG. 7 position so that the lands 82 and 83 are aligned with the blades 87. However, in this position the more closely spaced lands 83 have caused the oppositely disposed pair of blades 87a and 87b to be cammed or depressed substantially fully into their slots 86 and bores 88 and thereby causing the corresponding springs 91 to be substantially fully collapsed. At this point, zones of the cavity 48 are now increasing in volume and zones 95 are decreasing in volume.
  • FIG. 9 (which also corresponds to FIG. 6) the housing 41 has rotated through approximately or one-half revolution from its FIG. 7 position, and just before reaching the FIG. 9 position the zones 95 are again decreasing in volume while the zone 95' are increasing in volume.
  • FIG. 9 position is reached wherein the lands 82 and 83 are again aligned with the blades 87, it will be seen that the inner edge of each blade 87 is subjected, through the passages 89 and the bores 80, to the relatively high fluid pressure of the contracting zones 95.
  • the casing nut 56 is tightened sufliciently to retain the inner faces of the end cap members 4 9 and 51 in dynamic sealing relationship with the opposite axial ends of the spindle portion 62, but the operating clearance therebetween is sufficient to allow a predetermined static leakage between the high and low pressure zones of the cavity 48.
  • This relationship is desirable in order to insure that excessive driving torque from the air motor 26 will not be required in order to rotate the housing assembly 41 beyond one of its dynamic sealing positions such as illustrated in FIGS. 6 and 9.
  • the inner face of one, and preferably both, of the housing cap members, such as the cap 49, may be provided with appropriately located grooves of predetermined dimensions which are capable of transmitting fluid pressure between the high and low pressure sides of the blades 87a and 87b when the operating parts are in dynamic sealed relation.
  • a metering groove for this purpose is described in more detail in my aforementioned copending application Serial No. 250,160.
  • the housing assembly 41 is driven by the air motor 26 and the spindle 42 drives the tool member, it will be appreciated that these functions may be interchanged by minor and obvious modifications of the structure.
  • the rear spindle shaft portion 63 can be connected to the air motor 26 and the forward cap member 49 of the housing assembly 41 can be modified to mount the tool member.
  • an impulse tool in addition to the elimination of impacts or collisions between metal parts, is the facility with which such an impulse mechanism lends itself to the control of output torque of the tool.
  • Certain minor provisions for controlling the pressure differential between the high and low pressure sides of the impulse unit have been described above for the purpose of minimizing the torque requirements of the air motor 26.
  • an adjustable pressure relief valve is preferably provided which will prevent the fluid pressure in the high pressure zones from exceeding a predetermined maximum.
  • FIGS. 5 and 6 One such pressure relief arrangement is shown in FIGS. 5 and 6 and comprises a centrally located axial bore 96 in the spindle portion 62.
  • the bore 96 communicates with an elongate-d smaller diameter bore 97 having a threaded portion 98.
  • the bore 96 is closed by means of a plug or cap 99 which is keyed by a pin 101.
  • the inner end portion of the plug 99 has an axial recess 102 with a plurality of lateral or radial ports 103.
  • the inner axial end of the plug 99 provides an annular shoulder 108 constituting a valve seat for a ball element 109.
  • High pressure fluid from the zones 95 or H communicate with the recess 102 through a pair of radial angular drilled passages 111 in the spindle portion 62.
  • the inner ends of the passages 111 are aligned with the enlarged ports 103 in the plug 99.
  • the ball element 109 is normally retained in seated relation on the shoulder 108 by means of a spring 112 having its inner end operatively engaging the ball 109 through a cap member 113.
  • the opposite end of the spring 112 seats against a flange 114 of a piston member 116 disposed adjacent the forward end of the bore 96.
  • the piston 116 has another flange 117 spaced from the flange 114 with an O-ring seal 118 mounted therebetween.
  • An adjusting screw 121 is mounted in the threaded portion 98 of the small bore 97 and engages the outer end of the piston 116 for regulating the position of the piston 116 within the bore 96 and the degree of compression Of the spring 112.
  • the bore 97 extends forwardly the length of the spindle and is accessible at the front end of the square 34 (FIGS. 1 and 2) so that a suitable elongated tool, such as an Allen wrench can be inserted in the bore 97 for adjustment of the screw 121.
  • the present invention affords an improved impulse generating mechanism in which the relatively rotating parts are mounted coaxially and are in symmetrical or non-eccentric arrangement relative to the common axis of rotation.
  • the mechanism includes (1) a pair of relatively rotatable, coaxial, non-eccentric members having a fluid filled cavity therebetween, (2) a plurality of symmetrically disposed spring-pressed blades or vanes slidably mounted on one of the members and extending into the fluid-filled cavity and (3) a plurality of symmetrically disposed seal points on the other member arranged for periodic engagement with the blades at non-uniform distances from the common axis of rotation.
  • the fluid-filled cavity is intermittently divided into zones which are alternately increasing in volume (low pressure) and decreasing in volume (high pressure).
  • a fluid pressure loading arrangement is also provided for the blades such that, at certain of the periodic conditions of alignment between the blades and the seal points, each blade is subjected to the high fluid pressure of a contracting zone of the fluid-filled cavity whereby to provide a momentary dynamic sealing relation between the relatively rotating members. Consequently, the momentary large pressure increases necessary for impulse generation are obtained.
  • no eccentric forces are developed and the impulse mechanism of the tool operates under a balanced load.
  • Such uniform balanced operation avoids unbalanced forces on the bearings and insures a balanced pressure condition at the housing end plates or caps of the impulse unit. In many cases, the tool operating under balanced load will also be more comfortable and less tiring for the operator.
  • FIGS. 10 and 11 illustrate a modification of the impulse mechanism 31 previously described in that the pressure relief valve for torque control is mounted in the housing means of the impulse unit rather than in the spindle. Otherwise identical parts in FIGS. 10 and 11 are identified by the same reference numerals used in the comparable FIGS. and 6.
  • one of the thick wall portions of the bushing 47 is provided with an axial bore 126 having a plug 127 at its rearward end adjacent the end cap 51.
  • the plug 127 has an axial recess 128 and a plurality of radial apertures or ports 129.
  • a ball element 131 is held in normally seated engagement against an end seat 132 on the plug 127 by means of a spring 133 and a cap 134.
  • the forward end of the spring 133 is engaged by an adjustably positioned piston 136 having spaced flanges 137 and 138 with an O-ring seal 139 therebetween.
  • An adjusting screw 141 is mounted in a threaded opening 142 in the end cap 49 and engages the piston 136.
  • a tension plug 143 is provided in the cap member 49 and engages the threads of the screw 141 for retaining the latter in adjusted position.
  • the spindle shaft portions 32 and 63 are solid and integral with the main spindle portion 62.
  • the spindle portion 62 has a pair of diametric bores 146 and 147 arranged at right angles so as to interconnect the two high pressure zones 95 or H and the two low pressure zones 95' or L, respectively, when the mechanism is in dynamic sealing relation as shown in FIG. 11.
  • the bushing 47 also has a pair of angular passages 148 and 149 extending from the bore 126 at opposite sides of the valve seat 132 to opposite sides of one of the lands 83 and thereby connecting-the bore 126 with the high and low pressure zones and 95', respectively, of the elliptical cavity 43 when the unit is in dynamic sealing position.
  • FIGS. 12 to 16 show another embodiment of the invention which differs from the previously described structure in that: (1) the housing cavity of the impulse unit is circular in cross-section and the spindle body is substantially oval or elliptical in cross section instead of the reverse relationship shown in FIGS. 1 to 11, (2) the slidable blades or vanes are mounted in slots in the housing rather than in the spindle, and (3) the spindle is driven by the air motor of the tool and the housing is utilized as the output portion of the tool instead of the opposite arrangement heretofore illustrated and described.
  • the housing assembly designated at 151, includes an outer casing 152, a rigidly fitted cylinder bushing 153 having a circular cavity 154, a forward end cap 156, a rear end cap 157, and a locking ring 158 threadedly engaging the casing 152 for retaining the impulse unit in assembled relation.
  • a spindle designated generally at 159, has a central body portion 161 of substantially oval or elliptical cross-sectional configuration which is disposed coaxially within the cavity 154.
  • a shaft portion 162 at the forward end of the spindle 159 is journalled in a recess 163 in the end cap 156, and a shaft portion 164 at the rearward end of the spindle 159 is journalled in a bore 166 in the end cap 157.
  • the rear shaft portion 164 of the spindle is provided with a non-circular socket 167 for driving engagement with the air motor of the tool.
  • a plurality of blades or vanes 168 are slidably mounted in slots 169 in the bushing 153 which extend outwardly from the wall of the cavity 154 and terminate in enlarged axially extending bores 171 having connecting pressure loading passages 172 for communicating fluid pressure from the cavity 154 to the outer edges of the blades 168.
  • Each blade 168 has associated therewith a pair of compression springs 173 extending between the outer wall of the corresponding bore 171 and a pair of spaced bores 174 in the outer edge of the blade whereby the blade is normally urged inwardly into contact with the elliptical spindle portion 161.
  • the peripheral surface of the elliptical spindle portion 161 is provided with an encircling recess or undercut 176 which is disposed centrally between the axial ends of the spindle portion 161 and is interrupted by a pair of axially extending lands or seal points 177 disposed at the ends of the major axis of the ellipse and also by a pair of lands or seal points 178 disposed at the minor axis of the ellipse.
  • the major axis dimension of the elliptical spindle portion 161 is such that there is only a slight clearance between the spindle portion 161 and the circular cavity 154.
  • an impulse position is obtained every half revolution when the lands 177 and 178 are in dynamic sealing relation with the blades 168.
  • the spring pressure of the blades 168 against the periphery of the spindle por- 9 tion 161 is sufficient at the outset of operation to effect clockwise rotation of the housing 151 and also the wrench socket or other tool member which is secured to the forward end (not shown) of an axial extension 179 on the end cap 156.
  • the spindle 159 begins to accelerate ahead of the housing 151.
  • the volumes of the upper left quadrant (between blades 168a and 168C) and the lower right quadrant (between blades 1681; and 168d) of the cavity 154 are decreasing and the volumes of the remaining quadrants are increasing.
  • fluid pressure is equalized between adjacent contracting and expanding zones by reason of the recess 176.
  • the lands 177 and 178 are approaching alignment with the respective blades 168, and blades 1680 and 168d are substantially fully depressed by the camming action of the lands 177.
  • a pressure relief valve arrangement for torque control is provided in a bore 181 extending axially of the spindle 159 in essentially the same manner as shown in FIGS. and 6 so that a detailed description is unnecessary.
  • High pressure fluid from the high pressure zones of the cavity 154 communicates with the upstream side of the relief valve bore 181 by means of a pair of drilled passages 182 in the elliptical spindle portion 161, and such fluid is vented from the downstream side of the relief valve through another pair of spindle passages 183 into the low pressure zones of the cavity 154.
  • the spring setting for the relief valve is adjusted by means of a screw 186 threaded into the spindle shaft 162 and accessible from the front end of the tool through an elongated axial passage 187.
  • an improved impulse generating means comprising a rotatable housing member having a symmetrical, non-eccentric, coaxial, internal cavity containing a pressure transmitting fluid, a spindle member rotatably disposed in coaxial non-eccentric relation in said cavity for relative rotation between said housing member and said spindle member, means on one of said members defining a plurality of fluid pressure sealing portions disposed in symmetrically spaced relation around said cavity, a plurality of movable elements carried by the other of said members in symmetrically spaced relation around said cavity, the configurations of said cavity and said spindle member being such that, during relative rotation of said members, said fluid pressure sealing portions and said movable elements are engageable at different distances from the axis of rotation of said members whereby to divide said cavity into a plurality of zones of alternately increasing and decreasing volume,
  • said fluid passage means comprises a plurality of fluid passages in said other member communicating between said cavity and the base portions of said slots behind said blades, and said fluid passages being disposed relative to said members and said blades so as to register said fluid pas-sages with said zones of decreasing volume during said certain predetermined positions of said members.
  • One of said housing or spindle members is provided with adjustable pres-sure relief valve means and is also provided with a plurality of fluid passages communicating said valve means with said zones of increasing volume and with said zones of decreasing volume when said movable elements and said fluid pressure sealing portions are in sealing relation, whereby to prevent fluid pressure in said zones of decreasing volume from exceeding a predetermined maximum.
  • the structure of claim 5 further characterized in that four fluid pressure sealing portions are provided on said housing member in opposed relation at the major and minor axes of the elliptical cavity, and said movable elements comprise four blades slidably mounted in uniformly spaced relation around the periphery of said spindle member.
  • An impulse generating mechanism for use in a rotary tool or the like, comprising a pair of relatively rotatable members having a common axis of rotation, said members being symmetrical relative to said axis and defining a cavity therebetween containing a pressure transmitting fluid, and means on one of said members providing a plurality of points of sealing engagement with the other of said members during relative rotation therebetween, said points of engagement being disposed in symmetrically spaced relation around said axis and the configurations of said members and said cavity being such that, during relative rotation of said members, said points of sealing engagement are disposed at diiferent distances from said axis, whereby to divide said cavity into a plurality of zones of alternately increasing and decreasing volume and thereby generating intermittent substantial fluid pressure increases in sealed-off portions of fluid in said Zones of decreasing volume.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
US325629A 1963-11-22 1963-11-22 Impulse tool Expired - Lifetime US3263449A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
BE656130D BE656130A (enrdf_load_stackoverflow) 1963-11-22
US325629A US3263449A (en) 1963-11-22 1963-11-22 Impulse tool
GB46838/64A GB1023088A (en) 1963-11-22 1964-11-17 Impulse tool
DE19641503100 DE1503100A1 (de) 1963-11-22 1964-11-17 Impulswerkzeug
NL6413435A NL6413435A (enrdf_load_stackoverflow) 1963-11-22 1964-11-18
CH1500064A CH447073A (de) 1963-11-22 1964-11-20 Impulswerkzeug

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US325629A US3263449A (en) 1963-11-22 1963-11-22 Impulse tool

Publications (1)

Publication Number Publication Date
US3263449A true US3263449A (en) 1966-08-02

Family

ID=23268714

Family Applications (1)

Application Number Title Priority Date Filing Date
US325629A Expired - Lifetime US3263449A (en) 1963-11-22 1963-11-22 Impulse tool

Country Status (6)

Country Link
US (1) US3263449A (enrdf_load_stackoverflow)
BE (1) BE656130A (enrdf_load_stackoverflow)
CH (1) CH447073A (enrdf_load_stackoverflow)
DE (1) DE1503100A1 (enrdf_load_stackoverflow)
GB (1) GB1023088A (enrdf_load_stackoverflow)
NL (1) NL6413435A (enrdf_load_stackoverflow)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2547523A1 (fr) * 1983-03-04 1984-12-21 Uryu Seisaku Ltd Clef dynamometrique pneumatique du type a pression d'huile
US4635731A (en) * 1984-12-13 1987-01-13 Chicago Pneumatic Tool Company Impulse tool
EP0243334A1 (en) * 1986-04-22 1987-10-28 Atlas Copco Aktiebolag Hydraulic torque impulse generator with bypass means
EP0254699A1 (en) * 1986-07-24 1988-01-27 Atlas Copco Aktiebolag Hydraulic torque impulse generator
EP0268715A1 (en) * 1986-11-28 1988-06-01 Yokota Industrial Co., Ltd. Two-blade type impulse wrench
US4767379A (en) * 1986-10-03 1988-08-30 Atlas Copco Aktiebolag Hydraulic torque impulse generator
US4836296A (en) * 1988-08-22 1989-06-06 Dresser Industries, Inc. Fluid pressure impulse nut runner
EP0290411A3 (en) * 1987-05-08 1989-07-19 Atlas Copco Aktiebolag Hydraulic torque impulse generator
EP0353106A3 (en) * 1988-07-29 1990-12-19 Uryu Seisaku, Ltd. Oil pressure type impulse torque generator for wrench
US5092410A (en) * 1990-03-29 1992-03-03 Chicago Pneumatic Tool Company Adjustable pressure dual piston impulse clutch
US5172772A (en) * 1991-03-11 1992-12-22 Cooper Industries, Inc. Hydro-impulse screw tool
US11097403B2 (en) 2016-08-25 2021-08-24 Milwaukee Electric Tool Corporation Impact tool
US11260515B2 (en) 2013-06-12 2022-03-01 Makita Corporation Oil unit for impact power tool

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4175408A (en) * 1976-12-10 1979-11-27 Honda Giken Kogyo Kabushiki Kaisha Apparatus for absorbing oil pressure in an impact type tool
DE3347016A1 (de) * 1983-12-24 1985-07-18 Bijon 7433 Dettingen Sarkar Impulsschrauber
US4838133A (en) * 1987-09-29 1989-06-13 Nippon Pneumatic Manufacturing Co., Ltd. Hydraulic pulse wrench
DE4018084C1 (enrdf_load_stackoverflow) * 1990-06-06 1992-01-30 Deutsche Gardner-Denver Gmbh & Co, 7084 Westhausen, De

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US887781A (en) * 1907-10-24 1908-05-19 Anson P Fischer Transmission device.
US1156819A (en) * 1911-10-09 1915-10-12 Hydro Kinetic Transmission Company Clutch.
US1544721A (en) * 1924-05-29 1925-07-07 Harold L Bredlow Combined braking and clutching mechanism
US2169747A (en) * 1937-02-23 1939-08-15 Cleveland Punch & Shear Works Power press
US2564212A (en) * 1948-05-08 1951-08-14 George H Ramsey Power converter
US3116617A (en) * 1961-12-12 1964-01-07 Ingersoll Rand Co Fluid impulse torque tool

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US887781A (en) * 1907-10-24 1908-05-19 Anson P Fischer Transmission device.
US1156819A (en) * 1911-10-09 1915-10-12 Hydro Kinetic Transmission Company Clutch.
US1544721A (en) * 1924-05-29 1925-07-07 Harold L Bredlow Combined braking and clutching mechanism
US2169747A (en) * 1937-02-23 1939-08-15 Cleveland Punch & Shear Works Power press
US2564212A (en) * 1948-05-08 1951-08-14 George H Ramsey Power converter
US3116617A (en) * 1961-12-12 1964-01-07 Ingersoll Rand Co Fluid impulse torque tool

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4553948A (en) * 1983-03-04 1985-11-19 Uryu Seisaku, Ltd. Oil pressure type pneumatic torque wrench
FR2547523A1 (fr) * 1983-03-04 1984-12-21 Uryu Seisaku Ltd Clef dynamometrique pneumatique du type a pression d'huile
US4635731A (en) * 1984-12-13 1987-01-13 Chicago Pneumatic Tool Company Impulse tool
EP0243334A1 (en) * 1986-04-22 1987-10-28 Atlas Copco Aktiebolag Hydraulic torque impulse generator with bypass means
EP0254699A1 (en) * 1986-07-24 1988-01-27 Atlas Copco Aktiebolag Hydraulic torque impulse generator
US4761151A (en) * 1986-07-24 1988-08-02 Atlas Copco Aktiebolag Hydraulic torque impulse generator
US4767379A (en) * 1986-10-03 1988-08-30 Atlas Copco Aktiebolag Hydraulic torque impulse generator
EP0267169A3 (en) * 1986-10-03 1989-07-12 Atlas Copco Aktiebolag Hydraulic torque impulse generator
EP0268715A1 (en) * 1986-11-28 1988-06-01 Yokota Industrial Co., Ltd. Two-blade type impulse wrench
US4884995A (en) * 1987-05-08 1989-12-05 Atlas Copco Aktiebolag Hydraulic torque impulse generator
EP0290411A3 (en) * 1987-05-08 1989-07-19 Atlas Copco Aktiebolag Hydraulic torque impulse generator
EP0353106A3 (en) * 1988-07-29 1990-12-19 Uryu Seisaku, Ltd. Oil pressure type impulse torque generator for wrench
US4836296A (en) * 1988-08-22 1989-06-06 Dresser Industries, Inc. Fluid pressure impulse nut runner
US5092410A (en) * 1990-03-29 1992-03-03 Chicago Pneumatic Tool Company Adjustable pressure dual piston impulse clutch
US5172772A (en) * 1991-03-11 1992-12-22 Cooper Industries, Inc. Hydro-impulse screw tool
US11260515B2 (en) 2013-06-12 2022-03-01 Makita Corporation Oil unit for impact power tool
US11097403B2 (en) 2016-08-25 2021-08-24 Milwaukee Electric Tool Corporation Impact tool
US11897095B2 (en) 2016-08-25 2024-02-13 Milwaukee Electric Tool Corporation Impact tool
US12304034B2 (en) 2016-08-25 2025-05-20 Milwaukee Electric Tool Corporation Impact tool with collapsible member to compensate for thermal expansion

Also Published As

Publication number Publication date
CH447073A (de) 1967-11-15
BE656130A (enrdf_load_stackoverflow)
GB1023088A (en) 1966-03-16
DE1503100A1 (de) 1969-10-16
NL6413435A (enrdf_load_stackoverflow) 1965-05-24

Similar Documents

Publication Publication Date Title
US3263449A (en) Impulse tool
US3116617A (en) Fluid impulse torque tool
US5092410A (en) Adjustable pressure dual piston impulse clutch
US4553948A (en) Oil pressure type pneumatic torque wrench
US5544710A (en) Pulse tool
US3214941A (en) Impulse tool
EP0398655B1 (en) Pressure detecting device for torque control wrench
US4147219A (en) Two-speed offset nutrunner
US3214940A (en) Impulse tool
US5799562A (en) Regenerative braking method and apparatus therefor
US4836296A (en) Fluid pressure impulse nut runner
WO2021222729A1 (en) Rotary impact tool
SE509915C2 (sv) Hydraulisk momentimpulsgeneratoror
US3319723A (en) Axial piston pulse generator
US3156334A (en) Impact tool with hammer rotatable and axially movable within the motor
US3210960A (en) Centrifugal type impulse tool
US3700363A (en) Low inertia motor for fluid operated tool
US3672185A (en) Impulse motor
US3263426A (en) Power tool
US3221515A (en) Gear type impulse tool
US3210959A (en) Torque device
US3212590A (en) Impact wrench
US3212294A (en) Cam type impulse tool
US3717011A (en) Impulse unit
US3210961A (en) Spindle means for an impulse tool