EP0153711A2 - Visseuse à moteur avec roue dentée de serrage à pas fin - Google Patents

Visseuse à moteur avec roue dentée de serrage à pas fin Download PDF

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Publication number
EP0153711A2
EP0153711A2 EP85101941A EP85101941A EP0153711A2 EP 0153711 A2 EP0153711 A2 EP 0153711A2 EP 85101941 A EP85101941 A EP 85101941A EP 85101941 A EP85101941 A EP 85101941A EP 0153711 A2 EP0153711 A2 EP 0153711A2
Authority
EP
European Patent Office
Prior art keywords
power
pawl
arm
piston
tensioning wheel
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.)
Granted
Application number
EP85101941A
Other languages
German (de)
English (en)
Other versions
EP0153711B1 (fr
EP0153711A3 (en
Inventor
Hans-Bernd Mierbach
Gustav Frohn
Olaf Blockisch
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.)
Enerpac Tool Group Corp
Original Assignee
Applied Power Inc
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 Applied Power Inc filed Critical Applied Power Inc
Publication of EP0153711A2 publication Critical patent/EP0153711A2/fr
Publication of EP0153711A3 publication Critical patent/EP0153711A3/de
Application granted granted Critical
Publication of EP0153711B1 publication Critical patent/EP0153711B1/fr
Expired legal-status Critical Current

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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
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/004—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose of the ratchet type
    • B25B21/005—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose of the ratchet type driven by a radially acting hydraulic or pneumatic piston

Definitions

  • the invention relates to a power wrench with a power arm and a reaction arm, which can be pivoted relative to one another about an axis, with a fine-toothed toothing, rotatable about the axis tensioning wheel, with a cooperating with this tensioning wheel, multi-toothed pawl, the engages in a swivel direction of the power arm in an engagement position in several teeth of the tensioning wheel and slips over the teeth of the tensioning wheel in the other pivoting direction and with a hydraulic power cylinder comprising a cylinder and a piston which is arranged between the two arms.
  • Such power wrenches are known from several publications, for example from DE-OS 30 08 381.
  • the cylinder bore is in the power arm, the piston is supported on the reaction arm via an articulated arm. Due to the fine grading of the teeth of the tensioning wheel and pawl, only small swivel angles of the force arm with respect to the reaction arm are necessary in order to effect a rotary drive of the tensioning wheel.
  • a toothing is referred to as fine-stepped if there are three or more teeth in an angular range of twenty degrees, this angular range is typical of the pivoting angle range of a power arm relative to the reaction arm.
  • the pawl is supported on the power arm via an articulated arm which is located in a channel.
  • the transmission of the reaction forces is unfavorable, it takes place over a long outward and a long return path, which necessitates readjustment by means of a grub screw.
  • a disadvantage of the known power screwdriver is the relatively large number of individual parts from which it is composed. Furthermore, the piston which protrudes from the power arm in the pivoted-out position must be protected against contamination. Dirt can also accumulate unintentionally within the piston, which is open to one side and in which the articulated arm is located.
  • the power arm has a drive head which is located within the cylinder bore and engages in a recess in the piston and that the cylinder bore runs transversely, in particular at right angles to the connecting line between the axis and the drive head.
  • the driving force of the piston acting on the power arm acts practically at an angle of 90 degrees on the power arm.
  • the power arm can be particularly constructive just be trained.
  • the power transmission takes place largely symmetrically, the piston is located in mirror image to a connecting line between the axis and the drive head of the power arm.
  • a largely closed construction is achieved in which the power arm is located entirely within the reaction arm, which has a suitable recess for this.
  • the piston has at least one, preferably two partially cylindrical, concave, first contact surfaces in the region of its recess, the center of which is located on the axis line.
  • the drive head likewise has at least one, preferably convex, partially cylindrical, second contact surface.
  • the center of these second contact surfaces not only shifts axially when desired, but also somewhat radially when the power arm moves. In order to keep this radial displacement as small as possible, it is averaged on both sides of the axis line, so that the center of the drive head in the middle position of the power arm extends beyond the axis, while in the edge positions of the power arm it is below this axis line.
  • strongly eccentric gradients can also be selected for the second contact surfaces, in which the center point of the circular arc is far from the axis line of the cylinder - and the graduation is selected such that starting from a central position of the power arm during a movement to the left or right the point of contact between the drive head and the first contact surface remains essentially on the axis line of the cylinder.
  • the force arm is essentially fold-symmetrical to a straight line running through the axis and the center of its drive head, its general course being approximately pear-shaped.
  • the force arm preferably has a cutout for a pawl, this cutout has a reaction surface with a snap-in flank and an essentially radial transmission area which adjoins it flush.
  • the Einrastflanke ensures due to slanted course for the fact that the locking pawl in a pivotal direction of the - 'K raftarms necessarily in engagement with the teeth of the S pannrades is pressed, the actual power transmission is then performed in a particularly short distance over the substantially radial transmission area is in the immediate vicinity of the circumference of the tensioning wheel.
  • the pawl is advantageously connected to the power arm via a spring. Furthermore, it has the form of a D-reiviertel moon, wherein the reaction surface has the same diameter as the outer circle of the pawl, the toothing of the pawl is located on the boundary line with the larger diameter of the locking pawl.
  • the power wrench has a reaction arm 1 and a power arm 2, which are arranged so as to be pivotable relative to one another about an axis 3.
  • the reaction arm 1 has a partially cylindrical guide surface 4, which extends over approximately 180 ° and on which a corresponding outer surface of the force arm 2 lies in register.
  • the power arm 2 in turn has a cylindrical guide surface 6 which extends over approximately 270 ° and serves to guide and mount a tensioning wheel 7. This can thus be rotated about the axis 3 at least in one direction of rotation with respect to the force arm 2, the latter in turn can be pivoted by an angle of approximately ⁇ 10 ° from the shown central position with respect to the fixed reaction arm 1.
  • the tensioning wheel 7 has a hexagon socket for the transmission of a power-driven screwing movement to a nut, a screw bolt or the like.
  • the tensioning wheel 7 also has fine-toothing, for example there are four teeth within the total pivoting range of the power arm of approximately 20 °.
  • a pawl 8 in the form of a three-quarter moon interacts with these teeth, the one, lower, larger radius of which is provided with a plurality of teeth, for example five teeth.
  • the design and shape of these teeth of the pawl 8 corresponds to the design and shape of the teeth of the tensioning wheel 7.
  • the power arm is essentially pear-shaped, it goes upwards into a spherical drive head 9, which extends through a little more than 180 ° Circular arc is limited to a center 10 which lies on an axis running parallel to axis 3.
  • the force arm 2 is essentially fold-symmetrical with respect to a straight line connecting this center 10 with the passage of the axis 3.
  • a cylinder 11 is arranged in the reaction arm 1, the axis line 12 of which extends at right angles to the connection line mentioned between the center point 10 and the point of passage of the axis 3.
  • the center 10 is in the shown central position of the power arm 2 somewhat above the axis line 12, it cuts the axis line on the way to the left or right end position.
  • a piston 13 is guided, which is designed as a plunger. Together with the cylinder 11, it forms a hydraulic power cylinder that applies the force required for a screw connection.
  • the piston 13 has approximately in its central region a recess 14 into which the drive head 9 of the power arm 2 engages in a largely adapted form.
  • the recess 14 forms two concave contact surfaces 15 which run across the axis line 12, hereinafter referred to as first contact surfaces, on which the drive head 9 is supported with its second-dimensionally-mentioned second contact surface 16 around the center 10.
  • first contact surfaces on which the drive head 9 is supported with its second-dimensionally-mentioned second contact surface 16 around the center 10.
  • the course, in particular of the second contact surface can be so be chosen that the point of contact of the contact surfaces 15, 16 remains essentially on the axis line.
  • a circular arc with a larger radius must be selected for the course of the second contact surface 16, the center point of which lies outside the drive head 9.
  • the piston is sealed off from the cylinder 11 by means of a seal 17; beyond this seal there is a pressure medium space 18 which can be filled with hydraulic fluid via a channel and a suitable connecting piece 19.
  • the piston has an axial bore 21, which is made from its end surface 20 facing away from the pressure medium chamber and in which a helical compression spring 22 is arranged for the piston return. Because of the axial bore 21, a relatively long helical compression spring 22 can be selected. This is supported with its other end on a nut 23 which is screwed into the open end of the cylinder 11, for this purpose an internal thread is provided in the cylinder 11. A pin 24 with a plate-like end piece is pressed against the end of the axial bore 21 of the piston 13 by the helical compression spring 22. It is located at least partially within a sleeve 25 which is encompassed by the helical compression spring 22 and is held in the nut 23. The nut 23 has a through bore 26 for the pin 24. Overall, a practically tight construction is achieved to the outside.
  • the pawl 8 has the shape of a flat circular disc which has an edge-side, concave recess with the diameter of the teeth of the tensioning wheel 7. Overall, this creates the three-quarter moon shape already mentioned.
  • the boundary line with the larger diameter, that is the diameter of the teeth of the tensioning wheel'7; does not extend to the center of the delimitation circle 27 of the pawl 8, but is at a distance from it which is one tenth of the diameter of the delimitation circle 27.
  • a pawl spring 29 is arranged slightly above a horizontal through the center of the limiting circle 27 and in the left edge area on a pin 28, which is largely in a channel of the power arm 2 and is held there with its other end.
  • the recess A has in its left area a reaction surface with which the pawl 8 interacts. It is composed of a largely radial transmission area 30 and an adjoining snap-in flank 31.
  • the transmission area 30 is partially cylindrical, it extends over approximately 90 ° and merges tangentially into the latching flank 31, which intersects the connecting line from the center 10 and axis 3 at an angle of approximately 70 °.
  • Shown in the drawing is a drive position as it occurs when the pressure medium space 18 is filled with hydraulic fluid under pressure, which moves the piston 13 further to the right.
  • the pawl 8 is in the engaged position, it rests on the transmission area 30. This transmits the actuating forces to the pawl 8, the power transmission takes place at a favorable angle and over a short distance.
  • the working stroke described is ended when the piston 13 has taken the drive head 9 to the right into the right end position and the pin 24 can be seen in the through bore 26.
  • the return stroke movement of the piston 13 takes place under the action of the helical compression spring 22 as soon as the pressure medium chamber 18 is depressurized.
  • the pawl 8 initially remains in the engagement position shown.
  • the pawl spring 29 expands and strives to pull the pawl 9 back.
  • a spring can protrude into the recess A, which engages under and picks up the pawl 8 or its rod 32 if the pawl 8 remains too far relative to the transmission area 30.
  • a spring can protrude into the recess A, which engages under and picks up the pawl 8 or its rod 32 if the pawl 8 remains too far relative to the transmission area 30.
  • Also can be arranged parallel to axis 3 Project neter pin from the power arm 2 into the recess 14, which optionally causes a ramp and frees the pawl 8 from its engagement with the teeth of the tensioning wheel 7.
  • the pawl 8 When the pivoting movement continues, the pawl 8 thus slips over the teeth of the tensioning wheel 7 until the piston 13 is in its left end position. In this state, the pawl 8 is generally not in an engaged position, as shown in the drawing. Rather, it is only preloaded into this engagement position due to the inclined engagement flank 31 and the tensile force of the pawl spring 29. An intervention is restored when a new working stroke begins. The latching flank and the pawl spring 29 then pull the pawl 8 into the engaged position as soon as the teeth of the pawl 8 and the toothing of the tensioning wheel 7 are in the correct position relative to one another. Then the processes already described run again.
  • the transmission area 30 and / or the snap-in flank 31 can be delimiting surfaces of separate parts, which can be held on the power arm 2 by means of suitable screws and can be adjusted slightly in relation to this, in order to have an adjustment possibility in the event of wear.
  • the power wrench consists of relatively few individual parts, which are also easy to manufacture. A large part can even be designed as simple sheet metal stampings. Due to the arrangement of the cylinder 11 in the stationary reaction arm 1, in contrast to the known power screwdriver, it is avoided that the hydraulic line connected to the connecting piece 19 moves with each stroke.
  • a double-acting piston can also be used, in which case there is also a pressure medium space on the other side.
  • the drive head 9 could be ensured that the drive head 9 always rests against the top of the inner surface of the recess 14 ′ if it was ensured that the force arm 2 could shift somewhat relative to the reaction arm 1, namely in the longitudinal direction of this force arm 2.
  • the guide surface should be 4 of the reaction arm 1 only extend over 180 ° and would then have to be continued a few millimeters tangentially, so that the force arm 2 can move somewhat upwards and between 4 and 5 a small gap can arise if the piston 13 moves the force arm to the left or right, at least from the middle position shown, presses.
  • the drive head 9 could either be held positively in the piston 13 or be preloaded by a spring on the upper wall of the recess 14. In this way it is achieved that in the geometry shown in the area of the drive head 9, its center 10 always remains on the axis line 12.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Transmission Devices (AREA)
EP85101941A 1984-02-28 1985-02-22 Visseuse à moteur avec roue dentée de serrage à pas fin Expired EP0153711B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3407126 1984-02-28
DE19843407126 DE3407126A1 (de) 1984-02-28 1984-02-28 Kraftschrauber mit einem, eine feinstufige verzahnung aufweisenden spannrad

Publications (3)

Publication Number Publication Date
EP0153711A2 true EP0153711A2 (fr) 1985-09-04
EP0153711A3 EP0153711A3 (en) 1985-10-09
EP0153711B1 EP0153711B1 (fr) 1988-10-12

Family

ID=6228994

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85101941A Expired EP0153711B1 (fr) 1984-02-28 1985-02-22 Visseuse à moteur avec roue dentée de serrage à pas fin

Country Status (6)

Country Link
US (1) US4709600A (fr)
EP (1) EP0153711B1 (fr)
JP (1) JPS61501256A (fr)
DE (2) DE3407126A1 (fr)
ES (1) ES8606805A1 (fr)
WO (1) WO1985003897A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2562458A1 (fr) * 1984-04-07 1985-10-11 Wagner Paul Heinz Cle de puissance
EP0163009A3 (en) * 1984-06-01 1987-05-06 Applied Power Inc. Power-driven wrench with an action arm and a reaction arm, preferably constructed as a housing
GB2182592A (en) * 1985-10-22 1987-05-20 Hydra Tight Ltd Hydraulic torque wrench
US5203238A (en) * 1989-10-27 1993-04-20 Raymond Engineering Inc. Low profile rack and pinion wrench
DE4210511A1 (de) * 1992-03-31 1993-10-07 Wagner Paul Heinz Druckmittelbetätigter Kraftschrauber
DE4210512A1 (de) * 1992-03-31 1993-10-07 Wagner Paul Heinz Druckmittelbetätigter Kraftschrauber

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6148695A (en) 1999-08-03 2000-11-21 Hu; Bobby Ratchet wheel with asymmetric arcuate concave teeth or non-arcuate concave teeth and ratcheting tools with such ratchet wheel
US6431031B1 (en) 1999-12-16 2002-08-13 Bobby Hu Reversible ratcheting tool with a smaller head
US6568299B2 (en) 1999-12-16 2003-05-27 Bobby Hu Reversible ratcheting tool with a smaller head
TW418748U (en) 2000-01-11 2001-01-11 Hu Hou Fei Ratchet wrench
TW408653U (en) * 2000-02-03 2000-10-11 Hu Hou Fei Ratcheting tool
JP3515763B2 (ja) 2000-03-13 2004-04-05 厚飛 胡 小ヘッドと改善駆動トルクを具えたリバーシブルラチェット工具
TW428513U (en) 2000-07-21 2001-04-01 Hu Hou Fei Locating device of a direction switch and ratchet tools using the same
TW437521U (en) 2000-08-22 2001-05-28 Hu Hou Fei Ratchet driven tool
TW444633U (en) 2000-09-01 2001-07-01 Hu Hou Fei Ratchet tool
US6745647B2 (en) 2000-11-29 2004-06-08 Mei-Chen Wang Wrench having a universal-joint ratchet wheel
TW489701U (en) 2001-02-19 2002-06-01 Hou-Fei Hu A ratchet driven wrench capable of easily manufacturing and fabricating
US6807882B2 (en) 2001-05-07 2004-10-26 Bobby Hu Wrench with a simplified structure
US6722234B2 (en) 2001-05-14 2004-04-20 Bobby Hu Easy-to-operate and easy-to-assemble ratcheting-type wrench
US20030131691A1 (en) * 2001-06-20 2003-07-17 Norwolf Tool Works Compact hydraulic torque wrench and reaction arm
US20050011313A1 (en) * 2001-06-20 2005-01-20 Norwolf Tool Works Compact hydraulic torque wrench reaction arm
TW483377U (en) 2001-07-13 2002-04-11 Hou-Fei Hu Micro small torque wrench with constant torque value
TW483365U (en) 2001-07-13 2002-04-11 Hou-Fei Hu High torque wrench
US6647832B2 (en) 2001-07-27 2003-11-18 Bobby Hu Wrench having two rigid supporting areas for a pawl
US6539825B1 (en) 2001-09-20 2003-04-01 Yen-Wen Lin Single direction ratcheting wrench with stuck prevention and ratcheting direction indication
TW503802U (en) 2001-10-17 2002-09-21 Hou-Fei Hu Invertible ratchet wrench
US6450066B1 (en) 2001-10-19 2002-09-17 Bobby Hu Head of a wrench handle
US6520051B1 (en) 2001-12-27 2003-02-18 Bobby Hu Head of a wrench handle
US6715381B2 (en) * 2002-01-22 2004-04-06 John K. Junkers Adjustable reaction arm for torque power tool, and torque power tool provided therewith
TW506308U (en) 2002-02-08 2002-10-11 Hou-Fei Hu Improved structure for ratchet wrench
US6945141B2 (en) 2002-04-22 2005-09-20 Bobby Hu Reversible ratchet type wrench
TW567123B (en) 2002-07-22 2003-12-21 Hou-Fei Hu Ratchet wrench capable of fast rotation
TWI245684B (en) 2002-08-05 2005-12-21 Yan-Wen Lin Simple ratchet wrench
US6912933B2 (en) * 2003-04-11 2005-07-05 Brian Knopp Hydraulic torque wrench system
US7497147B2 (en) * 2006-09-12 2009-03-03 Unex Corporation Torque tool for tightening or loosening connections, and method of tightening or loosening the same
US9550282B2 (en) * 2014-04-22 2017-01-24 John D. Davis Compact hydraulic torque wrench cartridge
USD1042067S1 (en) * 2023-02-28 2024-09-17 Primesource Consulting Llc Limited clearance tool

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2112693A (en) * 1937-06-16 1938-03-29 Independent Pneumatic Tool Co Portable hammer wrench
DE2626923A1 (de) * 1976-06-16 1977-12-29 Mock Geraetebau Gmbh & Co Kg Vorrichtung zum anziehen und loesen von schraube-mutter-verbindungen
FR2362704A1 (fr) * 1976-08-23 1978-03-24 Harmat Nominees Pty Ltd Cle dynamometrique
US4201099B1 (en) * 1978-08-14 1993-12-07 K. Junkers John Hydraulic wrench
DE3008381A1 (de) * 1980-03-05 1981-09-10 Wagner, Paul-Heinz, 5203 Much Drehwerkzeug
US4339968A (en) * 1980-07-21 1982-07-20 Willard Krieger Hydraulic torque multiplier wrench
US4409865A (en) * 1981-01-15 1983-10-18 Unex Corporation Continuous ratchet drive
SU1082610A1 (ru) * 1982-12-27 1984-03-30 Skripnyak Ilya K Гайковерт
DE3323904A1 (de) * 1983-07-02 1985-01-10 Paul-Heinz 5203 Much Wagner Drehwerkzeug

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2562458A1 (fr) * 1984-04-07 1985-10-11 Wagner Paul Heinz Cle de puissance
EP0163009A3 (en) * 1984-06-01 1987-05-06 Applied Power Inc. Power-driven wrench with an action arm and a reaction arm, preferably constructed as a housing
GB2182592A (en) * 1985-10-22 1987-05-20 Hydra Tight Ltd Hydraulic torque wrench
US5203238A (en) * 1989-10-27 1993-04-20 Raymond Engineering Inc. Low profile rack and pinion wrench
DE4210511A1 (de) * 1992-03-31 1993-10-07 Wagner Paul Heinz Druckmittelbetätigter Kraftschrauber
DE4210512A1 (de) * 1992-03-31 1993-10-07 Wagner Paul Heinz Druckmittelbetätigter Kraftschrauber
US5311797A (en) * 1992-03-31 1994-05-17 Paul-Heinz Wagner Pressure-operated power wrench

Also Published As

Publication number Publication date
US4709600A (en) 1987-12-01
ES8606805A1 (es) 1986-05-16
DE3407126A1 (de) 1985-08-29
DE3565487D1 (en) 1988-11-17
JPS61501256A (ja) 1986-06-26
ES540821A0 (es) 1986-05-16
EP0153711B1 (fr) 1988-10-12
WO1985003897A1 (fr) 1985-09-12
EP0153711A3 (en) 1985-10-09

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