US3847229A - Portable impact wrench - Google Patents

Portable impact wrench Download PDF

Info

Publication number
US3847229A
US3847229A US00363711A US36371173A US3847229A US 3847229 A US3847229 A US 3847229A US 00363711 A US00363711 A US 00363711A US 36371173 A US36371173 A US 36371173A US 3847229 A US3847229 A US 3847229A
Authority
US
United States
Prior art keywords
clutch
housing
sleeve
combination
tool holder
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
US00363711A
Other languages
English (en)
Inventor
K Wanner
W Schmid
H Karl
J Falchle
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Application granted granted Critical
Publication of US3847229A publication Critical patent/US3847229A/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
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms

Definitions

  • the tool holder is rotatable stepwise in a single direction by a group of three sleeves the first of which is rotatable on but moves lengthwise with the cylinder and is normally held against rotation by a claw clutch one element of which is fixed to the housing.
  • An intermediate sleeve has inclined teeth or threads meshing with complementary threads or teeth of the first sleeve so that the intermediate sleeve rotates back and forth in response to rearward and forward movements of the first sleeve.
  • a third sleeve is rotatable in the housing and is connected with the intermediate sleeve by a one-way clutch. The tool holder is movable axially in but shares all angular movements of the third sleeve.
  • Another element of the claw clutch is biased against the fixed element by a helical spring and has axially parallel teeth mating with complementary teeth of the first sleeve so that the latter can move axially but is normally held against rotation.
  • the bias of the spring may be changed, terminated and/or assisted by a projection which can be manipulated by hand so that-the user can apply his muscle power in order to increase the resistance of the other clutch element to disengagement from the fixed clutch element when the tool holder resists rotation with the third sleeve.
  • the means for rotating the tool holder includes a first sleeve which rotatably surrounds the output member, a one-way clutch which transmits torque from the first sleeve to the tool holder while the first sleeve rotates in a given direction, and a device which rotates the first sleeve in response to reciprocation of the output member.
  • This device has a second sleeve which is provided with inclined teeth or threads mating with complementary teeth orthreads on the first sleeve.
  • the second sleeve is rigid with or forms part of the output member and tends to rotate the output member whenever the first sleeve rotates whereby the parts of the crank assembly must stand very high torsional stresses resulting in pronounced wear and relatively short useful life of the drive. In other words, the drive must take up and stand all such stresses which develop when the tool in the tool holder is rotated against the resistance.
  • the safety clutch is designed oradjusted to become disengaged in response to a relatively low torque to thus insure that the impact wrench can be properly manipulated by a relatively weak person, e.g., an adolescent or a tinker using the power tool once an a while in his basement workshop or garage.
  • a relatively weak person e.g., an adolescent or a tinker using the power tool once an a while in his basement workshop or garage.
  • the drive is still called upon to take up the torsional stresses because the safety clutch is provided between the reciprocable output member and the sec'ond'sleeve.
  • An object of the invention is to provide a portable impact wrench, especially an impact wrench which can be used as a drill, screwdriver and/or for analogous purposes, and whose drive comprises an electric motor serving to transmit motion to a reciprocable output member of the drive by way of a crank assembly, wherein the torque which develops when the tool and its holder rotate or resist rotation need not be taken up by the drive so that the latter is subjected to less pronounced wear than in heretofore known power tools.
  • Another object of the invention is to provide a portable impact wrench whose operation is safer than that of conventional impact wrenches and which is more versatile than the aforediscussed conventional wrenches.
  • a further object of the invention is to provide in a portable impact wrench novel and improved means for rotating the tool in stepwise fashion and novel and improved means for preventing damage to the impact wrench when its tool jams or is held, against angular movement for other reasons.
  • An additional object of the invention is to provide a portable impact wrench with novel and improved means for selecting the resistance which the tool holder must offer to rotation in order to deactivate the torque transmitting means for the tool holder.
  • Still another object of the invention is to provide a portable impact wrench with a device which enables the operator to determine, at his will and with his own muscle power, the exact magnitude of resistance which the tool holder must offer to rotation in order to terminate its angular movement while the output member of the drive continues to actuate the impeller which propels the tool forwardly.
  • a further object of the invention is to provide a portable impact wrench wherein the torque transmitting connection between the drive and the tool holder can be established, adjusted and/or terminated at the will of the operator and while the impact wrench is in actual use.
  • the invention is embodied in a portable impact wrench, drill, screwdriver or the like which comprises a housing, drive means provided in the housing and including a driving member or outputmember which is movable forwardly and rearwardl-y (preferably in response to rotation of the rotor of an electric motor which moves the output member by way of a crank assembly), a tool holder which is rotatably and reciprocably mounted in the housing in front of the output member, impeller means provided in the housing and being operative to strike against an anvil at the rear end of the tool holder in response to forward movements of the output member, and torque transmitting means for normally rotating the tool holder in response to forward movements of the output member.
  • the torque transmitting means comprises an input element which rotatably surrounds and is movable with the output member forwardly and rcarwardly, blocking means provided in the housing for normally holding the input element against rotation (the blocking means preferably comprises a claw clutch a first element of which is fixedly mounted in the housing and a second element of which is provided with axially parallel teeth in mesh with complementary teeth of the input element so that the latter can move axially of the second clutch element, and biasing means including one or more springs and/or a manually held part for holding the second clutch element in engagement with the first clutch element), an intermediate element which is rotatably mounted in the housing and has an annulus of inclined teeth or threads mating with complementary inclined teeth or threads of the input element so that the intermediate element rotates in opposite directions in response to forward and rearward movements of the output member as long as the blocking means holds the input element against rotation, an output element which is rotatably mounted in the housing in such a way that the tool holder can move axially of but cannot rotate relative to the output element, and
  • the drive means is not required to take up any torsional stresses irrespective of whether the tool holder rotates or is held against rotation, for example, due to jamming of the tool in or on a workpiece.
  • the impact wrench preferably further comprises a device for changing the bias of the aforementioned spring or springs; such device may constitute or include the aforementioned manually held part so that the operator can apply his muscle power in order to assist the spring or springs in preventing disengagement-of the safety clutch until the resistance which the tool holder offers to rotation reaches a value which might render further operation of the impact wrench dangerous.
  • FIG. 1 is a fragmentary partly elevational and partly longitudinal vertical sectional view of a portable impact wrench which embodies the invention.
  • FIG. 2 is a sectional view as seen in the direction of arrows from the line IIIi of FIG. 1.
  • the impact wrench of FIG. 1 comprises a housing or support 1 including a handle 1a and a cylindrical barrel lb.
  • the rear portion of the housing 1 contains a motor M (e.g.,- an electric motor) forming part of a drive which further includes a reciprocable tubular output member or cylinder 6 movable forwardly and rearwardly in the barrel lb.
  • the rotor R of the motor M reciprocates the cylinder 6 by way of a crank assembly including a rotary crank arm 5 having a crank pin 5a and a connecting rod 10 which is mounted on thecrank pin 5a at one end and the other end of which is coupled to the rear end of the cylinder 6 by means of a vertical shaft 9.
  • the shaft 9 is mounted in'a rear end wall 11 of the cylinder 6.
  • the reference character 8 denotes a cylindrical bore provided in the barrel 1b for the cylinder 6.
  • the latter comprises a larger-diameter rear portion 7, a smaller-diameter front portion 15, an a rearwardly and outwardly flaring intermediate portion 28 between the portions 7 and 15.
  • the cylinder 6 surrounds an impeller 12 having at its rear end a piston 13 which is reciprocable in the portion 7.
  • the front portion or shank 14 of the impeller 12 is reciprocable in the smaller diameter portion 15 of the cylinder 6.
  • the shank 14 can strike against an anvil at the rear end of a turnable and reciprocable tool holder 19 having a socket 62 for reception of a suitable tool 20 (e.g., a boring tool,
  • the piston 13 can move into and out of register with apertures 16 which are provided in the larger-diameter portion 7 of the cylinder 6.
  • the chamber 107 in the portion 7 is then sealed from the atmosphere and its volume decreases while the cylinder 6 moves forwardly under the action of the connecting rod 10.
  • the cushion of air which is entrapped in the chamber 107 urges the impeller 12 forwardly so that the shank l4 bears against the anvil 60 and moves the tool holder 19 and the tool 20 forwardly with the result that the tip of the tool penetrates into or moves with a workpiece.
  • the tool may penetrate into a wall which is to be provided with a hole.
  • the torque-transmitting means for rotating the tool holder 19 while the latter moves forwardly comprises a sleeve-like output element 22 which allows the tool holder to move axially but prevents the tool holder from rotating relative thereto.
  • the output element 22 is rotatable in the barrel lb and is coupled to an intermediate sleevelike element 24 by a one-way clutch 52.
  • the element 24 is rotatable but cannot move axially in the housing 1.
  • the tool holder 19 moves forwardly when its anvil 60 is struck by the shank 14 of the impeller 12. The rearward movement of the tool holder 19 takes place in response to rebounding of the tool 20 on the adjacent material of the workpiece.
  • a sleeve-like input element 26 of the torque transmitting means surrounds the smaller-diameter portion 15 of the cylinder 6 with a relatively small clearance.
  • the front end portion of the input element 26 is coupled to the portion 15 by a ring 27 and the rear portion of the input element 26 forms a collar which abuts against the intermediate portion 28 of the cylinder 6.
  • the input element 26 invariably shares all forward and rearward movements of the cylinder 6.
  • the just mentioned flange at the rear end of the input element 26 has an annulus of axially parallel external teeth 26a whose root diameter is at least equal to but preferably at least slightly greater than the outer diameter of the portion 7.
  • the front end portion of the input element 26 has an annulus of inclined external teeth or threads 26b which mate with similarly inclined internal threads or teeth 24b of the intermediate element 24 which is coupled to the output element 22 by means of the aforementioned one-way clutch S2.
  • the axially parallel teeth 26a at the rear end of the input element 26 mate with internal teeth 29a of a sleeve-like clutch element 29 which surrounds the portion 7 of the cylinder 6 and whose front end portion is provided with one or more claws 30 engaging complementary claws at the rear end of a ring-shaped clutch element 31 fixedly mounted in the housing 1.
  • the claws 30 are normally held in engagement with the claws of the clutch element 31 by a strong helical spring 34 which surrounds the portion 7 and reacts against a split ring 35 in the barrel 1b.
  • the foremost convolution of the spring 34 bears against an annular retainer 33 which abuts against the rear end face of the clutch element 29.
  • the reference character 38 denotes a distancing ring which is inserted in front of the split ring 35 to increase the bias of the spring 34.
  • the distancing ring 38 can be removed, replaced with a distancing ring of greater or smaller axial length, or used together with one or more additional distancing rings 38 of identical or different axial length.
  • the distancing ring or rings can be installed between the split ring 35 and the rearmost convolution of the spring 34 and/or between the foremost convolution of this spring and the retainer 33. The latter resembles a cylindrical sleeve which surrounds the rear end portion of the clutch element 29.
  • the front end portion of the clutch element 29 has a collar 36 which is immediately adjacent to the claws 30 and defines with the front end portion of the retainer 33 an annular compartment or space 37 for the eccentric projection or pin 39 of a stud 40'which can be rotated to thereby change the bias of the spring 34 and hence the force which is needed to disengage the claws 30 of the clutch element 29 from the complementary claws of the fixedly mounted clutch element 31.
  • the stud 40 extends radially of and into the housing 1 and is surrounded by a cylindrical sleeve 41 the upper end portion of which meshes with the barrel lb. The stud 40 can rotate within but cannot move axially of the sleeve 41 which can be said to'constitute a'component part of the housing 1.
  • the user of the impact tool In order to change the angular position of the stud 40 and to therebychange the bias of the spring 34 by way of the projection 39, the user of the impact tool must manipulate a handle 42 which surrounds the sleeve 41 and is movable angularly with the stud 40.
  • the handle 42 can be pulled downwardly, as viewed in FIG. 1 (i.e., away from the barrel 1b) by stressing a helical spring 44 which bears against a washer 45 surrounding a threaded stem 40a-of'the stud and abutting against a nut- 46.
  • the spring 44 When the user exerts-a pull in the direction indicated by arrow A.
  • the spring 44 is compressed and the handle 42 moves relative to the sleeve 41 and stud 40.
  • a locking bolt 48 of the handle 42 is moved to a level below a fixed stop 49 of the barrel lb so that the handle 42 is free to turn with the stud 40 andto thereby change the angular position of the projection39 in the annular compartment 37.
  • the handle 42 is rotated in a direction to move the projection 39 toward and into engagement with the collar 36, the sleeve-like clutch element 29 is held by hand (muscle power) against movement away from the tool holder 19 and its claws 30 remain in engagement with the claws of the fixed clutch element 31, i.e., the operators hand assists the bias of the spring 34.
  • the user can hold the handle 42 by hand in suchangular position that the clutch element 29 is held against disengagement from the fixed clutch element 31 by the spring 34 as well as by that force which the user applies to hold the projection 39in engagement with the collar 36.
  • each forward stroke of the cylinder 6 results in a mere axial movement of the holder 19 and tool 20.
  • the barrel 1] is preferably provided with a second stop (not shown) which may be similar to the stop 49 and against which the locking bolt 48 abuts when the pin 39 of the stud 40 stresses the spring 34v and allows the clutch element 29 to become disengaged from the clutch element 31.
  • the intermediate element 24 can rotate the tool holder 19 through the one-way clutch 52 and output element 22 only while the claws 30 of the clutch element 29 engage the claws of the clutch element 31. The apparatus is then operated as a simple impact hammer withoutany rotation of the tool 20.
  • each forward and rearward movement of the cylinder 6 results in a rotary movement of the intermediate element 24 because the inclinedteeth 24b mate with the inclined teeth 26b of the input element 26 which latter moves back and forthwith the cylinder 6 and is held against rotation by the teeth 26a, 29b as long as the claws 30 engage the claws of the fixed clutchelement 31.
  • the extent of angular movement of the intermediate element 24 is determined by the inclination'of the teeth 26b, 24b;
  • the aforementioned oneway clutch 52 causes the output-element 22(and-hcnce the tool holder l'9'and tool 20) to rotatewhile the intermediate element 24 rotates in a first direction (in response to a forward movement of the cylinder 6).
  • the clutch 52 is ineffective when the intermediate element 24 rotates in the opposite direction (in response to a rearward movement of the cylinder 6) so that thematcrial into which the tool 20 is caused'to penetrate then prevents the holder 19 and input element 22 from rotating with the element 24.
  • FIG. 2 The construction of'the one-way clutch 52 is shown in FIG. 2.
  • This clutch is installed in aflange 53 at the rear end of the output element 22.
  • the flange 53 is provided with tangential bores 54for clutch pins 55 which are biased outwardly by helical springs 56 so that they extend into suitably configuratedinternal notches 57 of the intermediate element 24.
  • Each notch-57 is bounded 'by a surface'57a against which the respective pin 55 bears while the intermediate element 24rotates in a first direction (counterclockwise, as viewed in FIG. 2) whereby the intermediate element 24 rotates the output element 22 and tool holder 19.
  • Each notch 57 is further bounded by a suitably inclined surface 57b along which the respective pin 55 slides while the inter mediate element 24 rotates in a second direction (clockwise, as viewed in FIG. 2).
  • the springs 56 insure that the pins 55 invariably bear against the adjacent internal surface of the intermediate element 24.
  • each pin 55 can move from a preceding notch 57 into the next-following or further notch.
  • the housing 1 allows the intermediate element 24 to rotate back and forth but holds this element against appreciable axial movement.
  • the hollow front portion or socket 62 of the tool holder 19 which receives the shank of the tool 20 is reciprocable and rotatable in an axial bore 61 of the barrel 1b.
  • the rear portion of the tool holder 19 is movable axially in but cannot rotate relative to the output element 22.
  • An external annular groove 63 of the tool holder 19 immediately behind the socket 62 receives a portion of an elastic cushion 64 which is installed in the barrel lb.
  • the axial length of the groove 63 determines the extent of axial displacement of the tool holder 19.
  • An important advantage of the improved impact wrench is that, when the tool 20 jams in the material of the workpiece, the torque is transmitted to the housing 1 by way of the input element 26, clutch element 29, claws 30, the corresponding claws of the clutch element 31 and clutch element 31.
  • the cylinder 6 need not take up any torsional stresses and this also holds true for all other parts of the drive means for the impeller 12.
  • Such construction protects the crank assembly between the electric motor M and the cylinder I 6 against torsional stresses. Consequently, the wear upon the parts of the crank assembly is minimal and its useful life is much longer than in heretofore known impact wrenches.
  • the claws 30 of the clutch element 29 become disengaged from the claws of the fixed clutch element 3]. with the result that the tool 20 ceases to turn as long as the claws 30 remain disengaged from the complementary claws.
  • the minimum torque which is needed to disengage the clutch 29, 31 is determined by the bias of the spring 34.
  • the bias of the spring 34 can be assisted by the operator if the handle 42 is manipulated in the aforedescribed manner so that the projection 39 bears against the collar 36 and thus participates in retention of claws 30 in engagement with the claws of the 'fixed clutch element 31.
  • the user can decide to intentionally disengage the clutch element 29 from the fixed clutch element 31 by moving the locking bolt 48 against the aforementioned second stop on the barrel 1!: so that the clutch element 29 has sufficient freedom of axial movement to disengage its claws 30 from the claws of the clutch element 31.
  • the device then merely acts as a hammer by causing the impeller 12 to strike against the anvil 60 in response to each forward stroke of the cylinder 6.
  • the clutch 29, 31 constitutes a safety device or blocking means which insures that the operator cannot be injured when the resistance which the tool 20 offers to rotation exceeds a permissible value.
  • the parts 3948 also constitute a safety device because it enables the operator to select that torque which can be handled by the operator without risking an injury.
  • the minimum resistance which the tool 20 must offer to disengage the clutch 29, 31 is preferably low so that the impact wrench can be properly and safely manipulated by arelatively weak person.
  • the projection 39 enables the operator to select a relatively high torque, i.e., the tool 20 must offer a very high resistance to rotation before the clutch element 29 becomes disengaged from the clutch element 31.
  • the aforementioned positioning of the second stop' for the locking bolt 48 prevents-an accidental or unintentional change in the bias of the spring 34 so that the minimum torque which is needed to disengage the clutch element 29 from the clutch element 31 remains unchanged until the operator decides to move the projection 39 away from the collar 36.
  • the operator must decide to move the handle 42 axially and to change the angular position of the stud 40; otherwise the magnitude of selected torque remains unchanged.
  • the impact wrench can be provided with means for adjusting the position of one or both stops so that the user can select an optimum torque for a particular operatron.
  • the claws 30 and the complementary claws of the clutch element 31 are preferably conical. This is desirable because such claws can transmit substantial torque while taking up a small amount of space.
  • the provision of a single projection 39 which can change the bias of the spring 34, disengage the spring 34 from the clutch element 29 or serve to transmit muscle power for retention of the clutch element 29 in engagement with the clutch element 31 contributes to simplicity, compactness, convenience of manipulation and lower cost of the impact wrench.
  • the spring 44 cooperates with the locking bolt 48 to insure that the angular position of the handle 42 cannot be changed accidentally, i.e., the operator knows that he must exercise great care whenever the handle 42 is moved against the opposition of the spring 44 because the projection 39 is then likely to change its angular position under the bias of the spring 34 or in response to disengagement of the clutch element 29 from the clutch element 31.
  • crank assembly is not subjected to any torsional stresses, even if the input element 26 has substantial freedom of radial movement with respect to the output member 6 and even if the teeth 26a, 29a and/or 24b, 26b are not machined with a high degree of precision. Moreover, a damaged or worn element 26 and/or 24 can be replaced by a fresh one with minimal losses in time and at a cost which is a small fraction of the cost of the output member 6.
  • a combination comprising a housing; drive means provided in said housing and including an output member movable forwardly and rearwardly; a tool holder rotatably and reciprocably mounted in said housing in front of said output member; impeller means provided in said housing and operative to strike against said tool holder in response to forward movements of said output member; and means for normally rotating said tool holder in response to forward movements of said output member, including an input element rotatably surrounding and movable with said output member, blocking means provided in said housing for normally holding said input element against rotation, an intermediate element rotatably mounted in said housing, said elements having tubular portions telescoped into each other and provided with mating inclined teeth or threads so that the forward and rearward movements of said input element result in rotation of said intermediate element in opposite directions, an output element rotatably mounted in said housing, said tool holder being movable axially relative to and being rotatable with said output element, and one-way clutch means provided between said intermediate element and said output element
  • said drive means further comprises an electric motor having a rotor and a'crank assembly connected between said rotor and said output member for converting the rotary movements of said rotor into reciprocatory movements of said output member.
  • said blocking means comprises a clutch having a first clutch element rigid with said housing, a second clutch element rotatably and axially movably mounted in said housing, said clutch elements having complementary male and female portions, and means for biasing said second clutch element against said first clutch element, said second clutch element having first axially parallel teeth and said input element having second axially parallel teeth mating with said first teeth so that said input element is rotatable with said first clutch element relative to said output member only when said second clutch element is disengaged from said first clutch element.
  • said means for biasing comprises a manually operable biasing device.
  • said means for biasing further comprises prestressed resilient means and said biasing device comprises means for changing the stressing of said resilient means and for disengaging said resilient means from said second clutch element.
  • each of said clutch elements is an annulus and said annuli having adjacent end faces provided with said claws.
  • said means for biasing comprises a prestressed spring provided in said housing and arranged to normally bear against said second clutch element so as to urge the claws thereof into engagement with the claws of said first clutch element, and a biasing device having a projection movable relative to said housing to thereby change the stressing of said spring or to disengage said spring from said second clutch element.
  • said biasing means further comprises a handle which is accessible from without said housing and is operable by hand to thereby move said projection relative to said housing.
  • a combination as defined in claim 9, wherein said projection is movable by hand to at least one position in which the force furnished by the hand maintains the claws of said second clutch element in engagement with the claws of said first clutch element.
  • said biasing device further comprises a handle rotatably mounted in said housing and being operable by hand to thereby move said projection relative to said housing and to maintain said projection in said one position.
  • said biasing device further comprises at least one stop provided in said housing and cooperating with locking means provided on said handle to maintain said handle in a selected angular position, said handle being movable radially of said clutch elements to thereby disengage said locking means from said stop and further comprising resilient means yieldably opposing the movement of said handle radially of said clutch elements in a direction to disengage said locking means

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Drilling And Boring (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
US00363711A 1972-06-16 1973-05-24 Portable impact wrench Expired - Lifetime US3847229A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2229388A DE2229388C3 (de) 1972-06-16 1972-06-16 Von Hand zu führender Bohrhammer

Publications (1)

Publication Number Publication Date
US3847229A true US3847229A (en) 1974-11-12

Family

ID=5847927

Family Applications (1)

Application Number Title Priority Date Filing Date
US00363711A Expired - Lifetime US3847229A (en) 1972-06-16 1973-05-24 Portable impact wrench

Country Status (10)

Country Link
US (1) US3847229A (ru)
JP (1) JPS5543867B2 (ru)
BR (1) BR7304440D0 (ru)
CH (1) CH559853A5 (ru)
DE (1) DE2229388C3 (ru)
ES (1) ES415946A1 (ru)
FR (1) FR2189175B3 (ru)
GB (1) GB1438516A (ru)
IT (1) IT989220B (ru)
NL (1) NL7308361A (ru)

Cited By (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4236588A (en) * 1977-06-27 1980-12-02 Hilti Aktiengesellschaft Hammer drill with a lockable tool holder
US4442906A (en) * 1980-11-18 1984-04-17 Black & Decker Inc. Percussive drills
US5379848A (en) * 1991-10-25 1995-01-10 Robert Bosch Gmbh Drill hammer
US5601149A (en) * 1994-02-25 1997-02-11 Hitachi Koki Company Limited Noise reduction mechanism for percussion tools
WO1997010929A1 (en) * 1995-09-21 1997-03-27 Chicago Pneumatic Tool Company Power hand tool with rotatable handle
US5816341A (en) * 1995-11-27 1998-10-06 Black & Decker Inc. Hammer mechanism
US5868208A (en) * 1993-12-29 1999-02-09 Peisert; Andreas Power tool
US5871059A (en) * 1995-02-28 1999-02-16 Makita Corporation Mechanism for preventing idling strikes in power-driven striking tools
US5896934A (en) * 1997-09-08 1999-04-27 Chicago Pneumatic Tool Company Reciprocating tool having a piston retainer
EP0922539A2 (en) * 1997-12-11 1999-06-16 Tamrock Oy Arrangement in connection with a hydraulic breaking apparatus
US6073705A (en) * 1997-10-06 2000-06-13 Makita Corporation Power-driven striking tool having a mechanism for setting the circumferential angle of tool bits attached to the striking tool
US6109364A (en) * 1995-11-24 2000-08-29 Black & Decker Inc. Rotary hammer
US6196330B1 (en) * 1998-07-25 2001-03-06 Hilti Aktiengesellschaft Manually operable drilling tool with dual impacting function
US6269888B1 (en) * 1999-08-13 2001-08-07 Hand Tools International, Llc Reciprocating and rotary power tool
US20030132015A1 (en) * 2001-04-28 2003-07-17 Gerhard Meixner Hammer drill and/or chipping hammer
US20030178213A1 (en) * 2001-05-11 2003-09-25 Gerhard Meixner Hand machine tool
US6733414B2 (en) 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
US20050016745A1 (en) * 2001-09-12 2005-01-27 Norbert Hahn Tool holder for hammer
US20050269117A1 (en) * 2004-06-08 2005-12-08 Hitachi Koki Co., Ltd. Striking tool
US20060081386A1 (en) * 2004-10-20 2006-04-20 Qiang Zhang Power tool anti-kickback system with rotational rate sensor
US20060201688A1 (en) * 2005-02-24 2006-09-14 Cheryl Jenner Hammer drill with a mode changeover mechanism
US20070084613A1 (en) * 2004-10-20 2007-04-19 Qiang Zhang Power tool anti-kickback system with rotational rate sensor
US20080011102A1 (en) * 2006-07-13 2008-01-17 Schell Craig A Control scheme for detecting and preventing torque conditions in a power tool
US20080021590A1 (en) * 2006-07-21 2008-01-24 Vanko John C Adaptive control scheme for detecting and preventing torque conditions in a power tool
US20080029283A1 (en) * 2006-08-07 2008-02-07 Hilti Aktiengesellschaft Hand-held power tool with pneumatic percussion mechanism
US20090065225A1 (en) * 2007-09-07 2009-03-12 Black & Decker Inc. Switchable anti-lock control
US20100000748A1 (en) * 2008-07-03 2010-01-07 Makita Corporation Hammer drill
US7980324B2 (en) 2006-02-03 2011-07-19 Black & Decker Inc. Housing and gearbox for drill or driver
US8286723B2 (en) 2010-01-07 2012-10-16 Black & Decker Inc. Power screwdriver having rotary input control
US8418778B2 (en) 2010-01-07 2013-04-16 Black & Decker Inc. Power screwdriver having rotary input control
US20130195570A1 (en) * 2010-04-16 2013-08-01 Husqvarna Ab Core drilling machine and a handle assembly for a core drilling machine
USD703017S1 (en) 2011-01-07 2014-04-22 Black & Decker Inc. Screwdriver
US20140138112A1 (en) * 2012-11-19 2014-05-22 Makita Corporation Impact tool
US9266178B2 (en) 2010-01-07 2016-02-23 Black & Decker Inc. Power tool having rotary input control
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
US9475180B2 (en) 2010-01-07 2016-10-25 Black & Decker Inc. Power tool having rotary input control
CN110280806A (zh) * 2019-07-25 2019-09-27 马鞍山市润启新材料科技有限公司 一种板材手持钻孔机
US10589413B2 (en) 2016-06-20 2020-03-17 Black & Decker Inc. Power tool with anti-kickback control system

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2804223C2 (de) * 1978-02-01 1983-09-08 Metabowerke GmbH & Co, 7440 Nürtingen Zusatzhandgriff für eine motorisch angetriebene, insbesondere axiale Schläge ausführende Handwerkzeugmaschine
DE2844109A1 (de) * 1978-10-10 1980-04-24 Bosch Gmbh Robert Handwerkzeugmaschine, insbesondere bohr- und/oder schlaghammer
DE3014694A1 (de) * 1980-04-16 1981-10-22 Hilti AG, 9494 Schaan Bohrhammer mit gehaeuse und handgriff
DE3335795A1 (de) * 1983-10-01 1985-04-18 Black & Decker Inc., Newark, Del. Bohrhammer
DE3540964A1 (de) * 1985-11-19 1987-05-21 Bosch Gmbh Robert Motorisch angetriebenes handwerkzeug fuer bohrenden oder schlagbohrenden betrieb
JPS62174886U (ru) * 1986-04-25 1987-11-06
DE10323606B4 (de) * 2003-05-20 2005-04-14 Robert Bosch Gmbh Elastische Döpperführung
SE529929C2 (sv) * 2006-05-09 2008-01-08 Atlas Copco Tools Ab Portabelt verktyg med en frihjulslåsning av drivaxeln
CN102784949A (zh) * 2011-05-19 2012-11-21 博世电动工具（中国）有限公司 电动工具及其传动机构

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US875869A (en) * 1906-09-14 1908-01-07 Rolland S Trott Rock-drill.
US3463246A (en) * 1966-12-28 1969-08-26 Metabowerke Kg Rotary percussive power tool with changeable drive
US3650336A (en) * 1970-05-05 1972-03-21 Rockwell Mfg Co Power driven device

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US875869A (en) * 1906-09-14 1908-01-07 Rolland S Trott Rock-drill.
US3463246A (en) * 1966-12-28 1969-08-26 Metabowerke Kg Rotary percussive power tool with changeable drive
US3650336A (en) * 1970-05-05 1972-03-21 Rockwell Mfg Co Power driven device

Cited By (67)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4236588A (en) * 1977-06-27 1980-12-02 Hilti Aktiengesellschaft Hammer drill with a lockable tool holder
US4442906A (en) * 1980-11-18 1984-04-17 Black & Decker Inc. Percussive drills
US5379848A (en) * 1991-10-25 1995-01-10 Robert Bosch Gmbh Drill hammer
US5868208A (en) * 1993-12-29 1999-02-09 Peisert; Andreas Power tool
US5601149A (en) * 1994-02-25 1997-02-11 Hitachi Koki Company Limited Noise reduction mechanism for percussion tools
US5871059A (en) * 1995-02-28 1999-02-16 Makita Corporation Mechanism for preventing idling strikes in power-driven striking tools
WO1997010929A1 (en) * 1995-09-21 1997-03-27 Chicago Pneumatic Tool Company Power hand tool with rotatable handle
US5687802A (en) * 1995-09-21 1997-11-18 Chicago Pneumatic Tool Company Power hand tool with rotatable handle
US5924497A (en) * 1995-09-21 1999-07-20 Chicago Pneumatic Tool Company Power hand tool with rotatable handle
US6109364A (en) * 1995-11-24 2000-08-29 Black & Decker Inc. Rotary hammer
US5816341A (en) * 1995-11-27 1998-10-06 Black & Decker Inc. Hammer mechanism
US5896934A (en) * 1997-09-08 1999-04-27 Chicago Pneumatic Tool Company Reciprocating tool having a piston retainer
US6098723A (en) * 1997-09-08 2000-08-08 Chicago Pneumatic Tool Company Reciprocating tool having a piston retainer
US6073705A (en) * 1997-10-06 2000-06-13 Makita Corporation Power-driven striking tool having a mechanism for setting the circumferential angle of tool bits attached to the striking tool
EP0922539A2 (en) * 1997-12-11 1999-06-16 Tamrock Oy Arrangement in connection with a hydraulic breaking apparatus
EP0922539A3 (en) * 1997-12-11 2002-11-20 Sandvik Tamrock Oy Arrangement in connection with a hydraulic breaking apparatus
US6196330B1 (en) * 1998-07-25 2001-03-06 Hilti Aktiengesellschaft Manually operable drilling tool with dual impacting function
US6269888B1 (en) * 1999-08-13 2001-08-07 Hand Tools International, Llc Reciprocating and rotary power tool
US6733414B2 (en) 2001-01-12 2004-05-11 Milwaukee Electric Tool Corporation Gear assembly for a power tool
US20030132015A1 (en) * 2001-04-28 2003-07-17 Gerhard Meixner Hammer drill and/or chipping hammer
US6955230B2 (en) * 2001-04-28 2005-10-18 Robert Bosch Gmbh Hammer drill and/or chipping hammer
US20030178213A1 (en) * 2001-05-11 2003-09-25 Gerhard Meixner Hand machine tool
US6810969B2 (en) * 2001-05-11 2004-11-02 Robert Bosch Gmbh Hand machine tool
US20050016745A1 (en) * 2001-09-12 2005-01-27 Norbert Hahn Tool holder for hammer
US7284622B2 (en) 2001-09-12 2007-10-23 Black & Decker Inc. Tool holder for hammer
US7819203B2 (en) * 2004-06-08 2010-10-26 Hitachi Koki Co., Ltd. Striking tool
US20050269117A1 (en) * 2004-06-08 2005-12-08 Hitachi Koki Co., Ltd. Striking tool
US7410006B2 (en) 2004-10-20 2008-08-12 Black & Decker Inc. Power tool anti-kickback system with rotational rate sensor
USRE44993E1 (en) 2004-10-20 2014-07-08 Black & Decker Inc. Power tool anti-kickback system with rotational rate sensor
USRE44311E1 (en) 2004-10-20 2013-06-25 Black & Decker Inc. Power tool anti-kickback system with rotational rate sensor
US20070084613A1 (en) * 2004-10-20 2007-04-19 Qiang Zhang Power tool anti-kickback system with rotational rate sensor
US20060081386A1 (en) * 2004-10-20 2006-04-20 Qiang Zhang Power tool anti-kickback system with rotational rate sensor
US7681659B2 (en) 2004-10-20 2010-03-23 Black & Decker Inc. Power tool anti-kickback system with rotational rate sensor
US20080110653A1 (en) * 2004-10-20 2008-05-15 Qiang Zhang Power tool anti-kickback system with rotational rate sensor
USRE45112E1 (en) 2004-10-20 2014-09-09 Black & Decker Inc. Power tool anti-kickback system with rotational rate sensor
US7552781B2 (en) 2004-10-20 2009-06-30 Black & Decker Inc. Power tool anti-kickback system with rotational rate sensor
US20060201688A1 (en) * 2005-02-24 2006-09-14 Cheryl Jenner Hammer drill with a mode changeover mechanism
US7314097B2 (en) 2005-02-24 2008-01-01 Black & Decker Inc. Hammer drill with a mode changeover mechanism
US9579785B2 (en) 2006-02-03 2017-02-28 Black & Decker Inc. Power tool with transmission cassette received in clam shell housing
US10987793B2 (en) 2006-02-03 2021-04-27 Black & Decker Inc. Power tool with tool housing and output spindle housing
US7980324B2 (en) 2006-02-03 2011-07-19 Black & Decker Inc. Housing and gearbox for drill or driver
US8205685B2 (en) 2006-02-03 2012-06-26 Black & Decker Inc. Housing and gearbox for drill or driver
US8316958B2 (en) 2006-07-13 2012-11-27 Black & Decker Inc. Control scheme for detecting and preventing torque conditions in a power tool
US20080011102A1 (en) * 2006-07-13 2008-01-17 Schell Craig A Control scheme for detecting and preventing torque conditions in a power tool
US20080021590A1 (en) * 2006-07-21 2008-01-24 Vanko John C Adaptive control scheme for detecting and preventing torque conditions in a power tool
US20080029283A1 (en) * 2006-08-07 2008-02-07 Hilti Aktiengesellschaft Hand-held power tool with pneumatic percussion mechanism
US20090065225A1 (en) * 2007-09-07 2009-03-12 Black & Decker Inc. Switchable anti-lock control
US7931095B2 (en) * 2008-07-03 2011-04-26 Makita Corporation Hammer drill
US20100000748A1 (en) * 2008-07-03 2010-01-07 Makita Corporation Hammer drill
US9266178B2 (en) 2010-01-07 2016-02-23 Black & Decker Inc. Power tool having rotary input control
US9321155B2 (en) 2010-01-07 2016-04-26 Black & Decker Inc. Power tool having switch and rotary input control
US8286723B2 (en) 2010-01-07 2012-10-16 Black & Decker Inc. Power screwdriver having rotary input control
US10160049B2 (en) 2010-01-07 2018-12-25 Black & Decker Inc. Power tool having rotary input control
US9199362B2 (en) 2010-01-07 2015-12-01 Black & Decker Inc. Power tool having rotary input control
US9211636B2 (en) 2010-01-07 2015-12-15 Black & Decker Inc. Power tool having rotary input control
US8418778B2 (en) 2010-01-07 2013-04-16 Black & Decker Inc. Power screwdriver having rotary input control
US9475180B2 (en) 2010-01-07 2016-10-25 Black & Decker Inc. Power tool having rotary input control
US9321156B2 (en) 2010-01-07 2016-04-26 Black & Decker Inc. Power tool having rotary input control
US20130195570A1 (en) * 2010-04-16 2013-08-01 Husqvarna Ab Core drilling machine and a handle assembly for a core drilling machine
US9149876B2 (en) * 2010-04-16 2015-10-06 Husqvarna Ab Core drilling machine and a handle assembly for a core drilling machine
US9289886B2 (en) 2010-11-04 2016-03-22 Milwaukee Electric Tool Corporation Impact tool with adjustable clutch
USD703017S1 (en) 2011-01-07 2014-04-22 Black & Decker Inc. Screwdriver
US20140138112A1 (en) * 2012-11-19 2014-05-22 Makita Corporation Impact tool
US9573262B2 (en) * 2012-11-19 2017-02-21 Makita Corporation Impact tool
US10589413B2 (en) 2016-06-20 2020-03-17 Black & Decker Inc. Power tool with anti-kickback control system
US11192232B2 (en) 2016-06-20 2021-12-07 Black & Decker Inc. Power tool with anti-kickback control system
CN110280806A (zh) * 2019-07-25 2019-09-27 马鞍山市润启新材料科技有限公司 一种板材手持钻孔机

Also Published As

Publication number Publication date
DE2229388C3 (de) 1981-01-22
CH559853A5 (ru) 1975-03-14
FR2189175B3 (ru) 1976-05-14
DE2229388B2 (de) 1980-05-22
ES415946A1 (es) 1976-02-01
BR7304440D0 (pt) 1974-08-15
IT989220B (it) 1975-05-20
GB1438516A (en) 1976-06-09
JPS4951674A (ru) 1974-05-20
NL7308361A (ru) 1973-12-18
DE2229388A1 (de) 1974-01-17
JPS5543867B2 (ru) 1980-11-08
FR2189175A1 (ru) 1974-01-25

Similar Documents

Publication Publication Date Title
US3847229A (en) Portable impact wrench
US3866692A (en) Power tools
DE60303406T2 (de) Schlaghammer mit axialem Anschlag
US4236588A (en) Hammer drill with a lockable tool holder
RU2496631C2 (ru) Инструмент ударного действия
US3828863A (en) Combined portable electric impact wrench and chipping hammer
US3736992A (en) Control collar and bearing support for power tool shaft
US5588496A (en) Slip clutch arrangement for power tool
US5379848A (en) Drill hammer
US6131671A (en) Power-driven tool having a mechanism for setting the rotary angle position of a tool bit
RU2520242C2 (ru) Ударный инструмент
US3685594A (en) Rotary hammer or the like
US6913090B2 (en) Hammer
US3998278A (en) Hammer drill
US3305031A (en) Power hammer
US3720269A (en) Portable torque and impulse transmitting machine
US3207237A (en) Apparatus for applying or dislodging screws and similar threaded fasteners
US7296635B2 (en) Rotary hammer with mode change ring
JP4552843B2 (ja) 打撃工具用アダプター
JP2008279587A (ja) 打撃工具
JP2004276227A (ja) 動力式工具
US3170523A (en) Rotary hammer
US3463246A (en) Rotary percussive power tool with changeable drive
JP2009233814A (ja) 作業工具
JP5103234B2 (ja) 打撃工具