EP0460592B1 - Hydro-Impulsschrauber - Google Patents

Hydro-Impulsschrauber Download PDF

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Publication number
EP0460592B1
EP0460592B1 EP91109090A EP91109090A EP0460592B1 EP 0460592 B1 EP0460592 B1 EP 0460592B1 EP 91109090 A EP91109090 A EP 91109090A EP 91109090 A EP91109090 A EP 91109090A EP 0460592 B1 EP0460592 B1 EP 0460592B1
Authority
EP
European Patent Office
Prior art keywords
pulsed
output shaft
housing
wrench according
plates
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
EP91109090A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0460592A1 (de
Inventor
Konrad Karl Dipl.-Ing. Kettner (Fh)
Heinz-Gerhard Dipl.-Ing. Anders
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.)
Gardner Denver Deutschland GmbH
Deutsche Gardner Denver GmbH
Original Assignee
Gardner Denver Deutschland GmbH
Deutsche Gardner Denver 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 Gardner Denver Deutschland GmbH, Deutsche Gardner Denver GmbH filed Critical Gardner Denver Deutschland GmbH
Publication of EP0460592A1 publication Critical patent/EP0460592A1/de
Application granted granted Critical
Publication of EP0460592B1 publication Critical patent/EP0460592B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket

Definitions

  • the invention relates to a hydraulic impulse wrench according to the preamble of claim 1.
  • this hydraulic impulse wrench can only be produced in a complex and costly manner.
  • the bearings of the output shaft are loaded unevenly due to the asymmetrical distribution of the lamellae during the generation of angular momentum, so that the bearing points are considerably stressed and wear out prematurely.
  • a hydraulic impulse wrench is also known (CH-PS 447 073), in which the output shaft has four lamellae arranged at angular intervals of 90 ° to one another and loaded radially outwards by springs. After each 180 ° rotation of the striking mechanism housing, all four slats on sealing strips of the striking mechanism housing come into sealing contact. As a result, the output shaft is rotated in a jerky or pulse-like manner in the direction of rotation of the housing after each 180 ° rotation of the striking mechanism housing. Since after every 180 ° rotation the sealing position is reached, the acceleration path of the output shaft is relatively small, so that the torque generated by the output shaft is correspondingly low.
  • the invention has for its object to design the generic hydraulic pulse screwdriver so that it can be manufactured more easily and inexpensively without the angular momentum generation is negatively affected.
  • the associated sealing strips can be easily produced because the forced control is designed in such a way that the further lamellae fit perfectly against the sealing strips of the striking mechanism housing, even with larger manufacturing tolerances.
  • This makes it possible to arrange the main lamellae and the other lamellae symmetrically to the axis of the output shaft, so that the output shaft and its bearing points are not loaded unevenly when the angular momentum is generated.
  • the hydraulic pulse wrench according to the invention also has a long service life.
  • the hydraulic impulse wrench shown only schematically in FIG. 1 has a housing 1 in which a compressed air motor 2 and a hammer mechanism 3 are accommodated.
  • the design and mode of operation of the compressed air motor 2 is known.
  • the housing 1 of the hydraulic pulse screwdriver can have any suitable design.
  • the compressed air motor 2 has a drive shaft 4 which is only shown schematically in FIG. 1 and which is drive-connected in a known manner to a housing 5 of the striking mechanism 3 (FIG. 2).
  • the housing 5 of the striking mechanism 3 has a cylinder part 6 which has a radially inwardly directed flange 7 on the output side.
  • the cylinder part 6 is provided with a circumferential recess 8 into which a striking mechanism cover 9 is inserted.
  • a cover 10 is placed, which is also inserted into the recess 8 of the cylinder part 6 and whose end face 11 facing away from the striking mechanism cover 9 is preferably flush with the end face 12 of the cylinder part 6.
  • the end cover 10 is provided centrally with a coupling piece 13, with which the housing 5 of the striking mechanism 3 is coupled to the drive shaft 4 of the compressed air motor 2.
  • the end cover 10 lies flat on the striking mechanism cover 9, which is provided centrally with an axially extending annular collar 14. It protrudes into a recess 15, on the inner wall of which the collar 14 rests on the outside.
  • the recess 15 is provided in the end face 16 of the end cover 10 which bears against the striking mechanism cover 9.
  • the striking mechanism cover 9 is advantageously inserted loosely into the recess 8 of the cylinder part 6.
  • the striking mechanism cover 9 then lies with its corresponding end face 17 against a radially extending shoulder surface 18 of the depression 8. So that the striking mechanism cover 9 can be aligned precisely with respect to the cylinder part 6, at least one positioning pin 19 is provided, which projects into corresponding positioning openings 20 and 21 in the cylinder part 6 and in the striking mechanism cover 9.
  • the striking mechanism cover 9 can thereby be mounted in a precisely predetermined position.
  • the end cover 10 is advantageously screwed into the recess 8 of the cylinder part 6.
  • An output shaft 23 passes through the cylinder chamber 22 and is rotatably supported in the cylinder part 6 and in the end cover 10 in a manner not shown.
  • a receptacle 24 On the end of the output shaft 23 protruding from the housing 5 on the output side, a receptacle 24, for example a chuck, is seated in a rotationally fixed manner for screwing tools.
  • the output shaft 23 is rotatable relative to the striking mechanism housing 5.
  • the output shaft 23 In the area between the flange 7 of the cylinder part 6 and the striking mechanism cover 9, the output shaft 23 has the cross-sectional shape shown in FIG. 7. However, as shown in FIGS. 5 and 6, it can also have an approximately circular cross section in this area.
  • the flattenings shown in FIGS. 5 and 6 on the circumference of the output shaft 23 have only been drawn in to better illustrate the sealing position of the control lamellae to be described.
  • the output shaft 23 has a circular cross section in this exemplary embodiment. This area of the output shaft 23 is enlarged in cross section. The smaller end portions 25 and 26 of the output shaft 23 connect to it.
  • the output shaft 23 is rotatably mounted in the flange 7 of the cylinder part 6 and in the striking mechanism cover 9.
  • the end sections 25, 26 are sealed with seals 27 and 28 with respect to the flange 7 and the striking mechanism cover 9.
  • the thickened section of the output shaft 23 lies in the cylinder chamber 22 and has recesses 29 to 32 in its peripheral surface at angular intervals of 90 ° (FIG. 5).
  • a control plate 33 and 34 is housed, while in the two other diametrically opposite recesses 32 and 30, a main plate 35 and 36 is housed.
  • the control blades 33 and 34 extend between the flange 7 of the cylinder part 6 and the striking mechanism cover 9.
  • control blades 33 and 34 are provided with cam-shaped extensions 37, 38 and 39, 40 which Form followers with which the control slats 33 and 34 are positively controlled.
  • the followers 37 and 38 of the control plate 33 are axially shorter than the followers 39 and 40 of the diametrically opposed control plate 34.
  • the followers 37, 38 are radially wider than the followers 39, 40.
  • the followers 37 to 40 extend from the facing one another Long sides 41 and 42 of the control blades 33, 34.
  • Each control plate 33 and 34 is loaded radially outwards by at least one compression spring 43 and 44.
  • the follower members 37 and 38 of the control plate 33 are each assigned a control track 45 and 46 in the flange 7 of the cylinder part 6 and in the striking mechanism cover 9.
  • a control track 47 and 48 in the flange 7 of the cylinder part 6 and in the striking mechanism cover 9 are also assigned to the followers 39 and 40 of the control plate 34.
  • All control tracks 45 to 48 are formed by the side walls of depressions 49 and 50 in the mutually facing sides of the flange 7 of the cylinder part 6 and the striking mechanism cover 9.
  • the control tracks 45 and 47 in the flange 7 and 46 and 48 in the striking mechanism cover 9 are axially offset from one another. As shown in FIG.
  • the respective recesses 49 and 50 are designed in steps to form these control tracks, the control tracks 45 and 46 being provided on the mutually facing sides of the flange 7 and the striking mechanism cover 9, while the control tracks 47 and 48 are arranged on the sides of the depressions facing away from one another and perpendicular to the bottom 51 and 52 of the depressions 49 and 50 connect.
  • the control tracks 45 and 47 and 46 and 48 in the flange 7 and in the striking mechanism cover 9 each lie on the jacket of an imaginary cylinder (FIG. 5). The generatrix of these cylindrical outer surfaces lies parallel to the axis of rotation of the output shaft 23.
  • the control tracks 45 and 46 have a larger diameter than the control tracks 47 and 48.
  • the control tracks 45 and 47 and 46 and 48 are provided so that they are at a point 53 ( Fig. 5) touch.
  • the two diametrically opposed control blades 33 and 34 are positively controlled during operation of the hydraulic impulse wrench in a manner to be described in such a way that, when the housing 5 is rotated 360 °, they are only in one position with associated sealing strips 54 and 55 (Fig. 5) come into sealing contact.
  • the two diametrically opposed main fins 35, 36 are also under the force of at least one, in the exemplary embodiment of two compression springs 56 to 59 (FIG. 4), with which they are pressed radially outward against the inner wall 60 of the cylinder chamber 22.
  • the main fins 35, 36 have a T-shape in view (FIG. 4) and lie with the end faces of their legs on the mutually facing end faces 61 and 17 of the flange 7 of the cylinder part 6 and the striking mechanism cover 9 (FIG. 4).
  • the depressions 32 and 33 are shorter than the axial length of the cylinder chamber 22 and as the depressions 29 and 31 for the control plates 33 and 34.
  • the depressions 29 and 31 extend over the entire axial length of the thickened central portion of the output shaft 23, while the Wells 32 and 30 are limited in the axial direction.
  • the main fins 35, 36 engage with their feet in these recesses, which are longer in the axial direction than the feet of the main fins.
  • the width of the depressions 30, 32 is greater than the thickness of the main lamellae 35, 36 (FIG. 5).
  • the inner wall 60 extends over an axial partial length in the form of an ellipse (FIG. 5). Under the force of the compression springs 56 to 59, the main lamellae 35 and 36 always rest against this elliptically extending inner wall 60 when the housing 5 is rotated.
  • the compressed air motor 2 is started in a known manner.
  • the drive shaft 4 of the compressed air motor 2 drives the housing 5 of the striking mechanism 3 directly via the coupling piece 13.
  • the end cover 10, the striking mechanism cover 9 and the cylinder part 6 with the flange 7 form the housing 5.
  • the output shaft 23 is rotatably carried along by the pressure medium in the cylinder chamber 22.
  • sealing strips 54, 55, 62 and 63 are provided on the inner wall of the cylinder part 6 at angular intervals of 90 ° in each case, which are integrally formed with the cylinder part 6 and whose end faces act as sealing surfaces.
  • Fig. 7 shows the sequence of movements that results when the output shaft 23 is further rotated after the screw head or nut has been seated.
  • the diametrically opposed main lamellae 35, 36 and the likewise diametrically opposed control lamellae 33, 34 lie sealingly on the sealing strips 54, 55, 62, 63.
  • four approximately crescent-shaped, closed rooms 65 to 68 are formed.
  • a high pressure is formed in the rooms 65 and 67, that is to say in the direction of rotation 64 behind the main lamella 35 and 36, while in the two rooms 66 and 64 lying in front of the main lamellae 35, 36 in the direction of rotation 64 68 a low pressure is formed.
  • the sealing strips 54, 55, 62, 63 are released from the main plates 35, 36 and the control plates 33, 34.
  • the main fins 35, 36 are pressed under spring force against the elliptical inner wall 60 so that they abut against this inner wall during the rotation of the housing 5.
  • the two control plates 33 and 34 are pressed with their followers 37 to 40 under spring force against the associated control tracks 45 to 48, each lying on a cylinder jacket and arranged so that the control plates 33, 34 are only in the pulse position (Fig. 5 and 7) on the sealing strips 54, 55 of the housing 5. If the housing 5 has been rotated by 180 ° with respect to the pulse phase, then a position as shown in FIG. 6 and the lower illustration in FIG. 7 results.
  • the main lamellae 35, 36 lie in this position in a sealing manner against the sealing strips 63 and 62, their End faces lie on the elliptical inner wall 60.
  • the control blades 33, 34 have in this position distance from the sealing strips 54 and 55.
  • the control lamellae 33, 34 are positively controlled by their followers 37 to 40 and the control tracks 45 to 48 in such a way that they do not seal against the corresponding sealing strips 54 after the 180 ° rotation of the housing 5 , 55 of the housing 5. As a result, no pressure builds up in the cylinder rooms in this position.
  • the pulse generated by the main lamellae 35 and 36 passes without pressure.
  • the output shaft 23 can thus be further accelerated.
  • the housing 5 continues to rotate in the direction of rotation 64, the main lamellae 35 and 36 abutting the elliptical inner wall 60 under spring force and the control lamellae 33 and 34 being positively controlled by the control tracks 45 to 48 via their followers 37 to 40.
  • the control lamellae 33, 34 are moved radially outward again in the following 180 ° rotation of the housing 5 until, after a 360 ° rotation of the housing 5, they again seal against the sealing strips 62, 63 (Fig. 5 and top illustration in Fig. 7). Only now does the output shaft 23 again receive a pulse.
  • this hydraulic impulse wrench it is possible with this hydraulic impulse wrench to accelerate the output shaft 23 over the entire rotation angle range of 360 ° of the housing 5 and to achieve the greatest possible speed for each individual impulse. Since all the slats 33 to 36 are pressed under spring force against the associated control tracks 45 to 48 and 60, a flexible adjustment of all slats is ensured, thereby ensuring a gap-free sealing and an improved pulse quality and torque accuracy is achieved. As a result of this flexible adaptation, larger manufacturing tolerances can be permitted, so that the striking mechanism 3 and thus the entire hydraulic pulse screwdriver can be manufactured inexpensively and can also be easily assembled.
  • control tracks 45 to 48 do not have to be manufactured with high precision, but larger tolerances can easily be permitted due to the resilient pressing of the control lamellae 33 and 34.
  • the outer diameter of the striking mechanism 3 can be kept small due to the four movable slats 33 to 36.
  • the various cylinder spaces 65 to 68 are not connected to one another because the control lamellae 33, 34 lie sealingly on the end faces of the control tracks 45 to 48 pointing in the axial direction.
  • the output shaft 23 seals with its end faces against the flange 7 and the striking mechanism cover 9 and, in the pulse position, separates the pressure-loaded spaces 65 and 67 from the pressure-relieved spaces 66 and 68 in a sealing manner.
  • the hydraulic pulse screwdriver can be switched off in a conventional manner after tightening the screws or nuts.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Automatic Assembly (AREA)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)
EP91109090A 1990-06-06 1991-06-04 Hydro-Impulsschrauber Expired - Lifetime EP0460592B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4018084A DE4018084C1 (enExample) 1990-06-06 1990-06-06
DE4018084 1990-06-06

Publications (2)

Publication Number Publication Date
EP0460592A1 EP0460592A1 (de) 1991-12-11
EP0460592B1 true EP0460592B1 (de) 1995-01-11

Family

ID=6407866

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91109090A Expired - Lifetime EP0460592B1 (de) 1990-06-06 1991-06-04 Hydro-Impulsschrauber

Country Status (3)

Country Link
EP (1) EP0460592B1 (enExample)
DE (2) DE4018084C1 (enExample)
ES (1) ES2066269T3 (enExample)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE9201405L (sv) * 1992-05-05 1993-06-21 Atlas Copco Tools Ab Hydraulisk momentimpulsgenerator
JP5021240B2 (ja) * 2006-06-07 2012-09-05 株式会社マキタ 油圧式トルクレンチ

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE656130A (enExample) * 1963-11-22
JPS59140173U (ja) * 1983-03-04 1984-09-19 瓜生製作株式会社 油圧式トルクレンチ

Also Published As

Publication number Publication date
DE59104201D1 (de) 1995-02-23
DE4018084C1 (enExample) 1992-01-30
EP0460592A1 (de) 1991-12-11
ES2066269T3 (es) 1995-03-01

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