EP2269772B1 - Clé à grincement doté d'un renforcement du couple - Google Patents

Clé à grincement doté d'un renforcement du couple Download PDF

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Publication number
EP2269772B1
EP2269772B1 EP10165940.7A EP10165940A EP2269772B1 EP 2269772 B1 EP2269772 B1 EP 2269772B1 EP 10165940 A EP10165940 A EP 10165940A EP 2269772 B1 EP2269772 B1 EP 2269772B1
Authority
EP
European Patent Office
Prior art keywords
ratchet
ratchet wrench
housing
torque
lever
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.)
Not-in-force
Application number
EP10165940.7A
Other languages
German (de)
English (en)
Other versions
EP2269772A2 (fr
EP2269772A3 (fr
Inventor
Josef Bättig
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP2269772A2 publication Critical patent/EP2269772A2/fr
Publication of EP2269772A3 publication Critical patent/EP2269772A3/fr
Application granted granted Critical
Publication of EP2269772B1 publication Critical patent/EP2269772B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B25B13/00—Spanners; Wrenches
    • B25B13/46—Spanners; Wrenches of the ratchet type, for providing a free return stroke of the handle
    • B25B13/461—Spanners; Wrenches of the ratchet type, for providing a free return stroke of the handle with concentric driving and driven member
    • B25B13/462—Spanners; Wrenches of the ratchet type, for providing a free return stroke of the handle with concentric driving and driven member the ratchet parts engaging in a direction radial to the tool operating axis
    • B25B13/463—Spanners; Wrenches of the ratchet type, for providing a free return stroke of the handle with concentric driving and driven member the ratchet parts engaging in a direction radial to the tool operating axis a pawl engaging an externally toothed wheel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B17/00—Hand-driven gear-operated wrenches or screwdrivers
    • B25B17/02—Hand-driven gear-operated wrenches or screwdrivers providing for torque amplification

Definitions

  • the invention is in the field of manually operable tools and relates to a ratchet wrench or ratchet wrench with a torque gain according to the preamble of the first claim.
  • Such a ratchet wrench is for example from the US 2006/0090606 known.
  • a ratchet wrench for high torque with two parallel side plates and a ratchet wheel and an associated pawl is described.
  • the tool is actuated by tangentially introduced tensile and compressive forces, which act directly on a rotatably mounted in parallel side plates latch.
  • the tool has neither a torque ratio nor a reverse rotation.
  • the pawl has several teeth to divide the high tangential forces. Due to the elastic deformation of the teeth and the entire pawl, however, the load is distributed very differently to the individual teeth. With more than three teeth, these deformations can even lead to individual teeth no longer wear.
  • the ratchet wrench according to the invention should be suitable for very high torques without overloading and deformations occurring. Its construction should be simple and its manufacture inexpensive. The operating direction of the drive lever and the direction of rotation of the output gear should be identical, the ratchet wrench should have a reverse rotation.
  • the inventive torque wrench ratchet wrench includes a housing, externally accessible torque receiving means on the housing for receiving drive torque, externally accessible torque output means on the housing for output torque greater than the drive torque, and connection means housed in the housing for establishing operative engagement therebetween Torque receiving means and the torque output means and for amplifying the drive torque in the output torque.
  • the connecting means include an output lever, an output gear operatively connected to the torque output means, and a ratchet mechanism acting between the output lever and the output gear.
  • the torque receiving means, the torque output means and the connecting means are substantially surface symmetric with respect to a common plane of symmetry.
  • the housing is closed by two parallel to the plane of symmetry, preferably also symmetrical with respect to the plane of symmetry housing plates which are spaced apart by at least one housing spacer and connected to this form-fitting.
  • the output lever includes two parallel to the plane of symmetry also preferably symmetrical with respect to the plane of symmetry lever plates, which are spaced apart from each other by at least one lever spacer and positively connected thereto.
  • the housing plates, the at least one housing spacer, the lever plates and the at least one lever spacer are substantially flat plates, the form-fitting. preferably by means of cylindrical pins, are interconnected and preferably made of metal.
  • the ratchet mechanism includes at least two ratchet elements, each of which is independently pivotable about its own ratchet axis and adapted to engage in a corresponding toothing of the driven gear.
  • the ratchet wrench includes a reverse rotation locking mechanism acting between the housing and the driven wheel.
  • the anti-rotation mechanism ensures that the movement of the output gear is rectified, d. H. always in one direction, albeit gradually.
  • the anti-rotation locking mechanism preferably includes at least two pawl members, each of which is independently pivotable about its own pawl axis and adapted to engage in a corresponding toothing of the driven gear.
  • the ratchet and pawl elements can be made of flat plates and are preferably identical. They can be made by water jet cutting, precision casting, precision forging or sintering, e.g. B. high-strength tempered steel or tool steel.
  • At least two ratchet elements and / or at least two pawl elements can for mutual transmission of forces and / or torques through be set up direct mutual mechanical contact. At least one of the ratchet elements and / or at least one of the pawl elements can be pressed by a spring element against the driven gear.
  • a group consisting of at least two ratchet elements and / or at least two pawl elements is pressed against the output gear by a common spring element.
  • the common spring element presses on a first of the ratchet elements, and each of the other ratchet elements of the group is actuated, as it were by a domino effect, from the respective preceding one.
  • a leaf spring for this purpose.
  • other spring elements such as spiral compression springs or elastomeric fittings could be used.
  • the leaf spring is preferably made in one piece and two layers.
  • a housing spacer can serve as a bearing for the at least two pawl elements.
  • a lever spacer can serve as a bearing for the at least two ratchet elements.
  • the spacers are preferably in one piece, but may also be constructed of two or more thinner, stacked plates.
  • the torque receiving means and / or the torque output means each have a form element for receiving a shaft.
  • the connecting means are designed such that the driving torque and the output torque are rectified, i. H. By means of pivotal movements during the drive a rectified output rotary motion is generated. The operator would like to intuitively pull the drive in the same direction in which the fastener is to be rotated.
  • the ratchet wrench Due to the perfect symmetry of the ratchet wrench is evenly loaded. so that unwanted bending or torsional loads omitted. In addition, the ratchet wrench can be easily turned to reverse the direction of rotation.
  • the ratchet wrench is characterized by a particularly simple structure and a cost-effective production.
  • the plate-shaped elements can be produced easily and very accurately, for example by laser or water jet cutting. All power transmission between the ratchets and the lever spacer or between the pawls and the housing takes place positively via the cylindrical pins. Additionally or alternatively, the plates and the spacers could preferably be connected to one another in a material-locking manner, for example by soldering, only on one side.
  • FIG. 1 shows a view of the ratchet wrench with torque gain
  • the FIGS. 2 and 3 the corresponding side and top views.
  • Two identical housing plates 7 close a ratchet wrench housing up and down. They have bearing bores 8 and 9, in which a driven wheel or ratchet wheel 1 with two bearing pins 3 (see FIG. 6 ) and a drive lever 30 is mounted with two bearing journals 31.
  • the two housing plates 7 are by means of screws 51, which in corresponding threaded holes 16 of a spacer plate 12 and in a spacer 17 (see FIG. 4 ), fastened.
  • the screws 51 are preferably countersunk screws, which are embedded in corresponding countersinks 11.
  • a cover tape 50 which is preferably made of spring steel strip covers the lateral openings between the two housing plates 7 completely, so that the mechanism is protected from contamination and damage by foreign particles.
  • the FIG. 4 shows the ratchet wrench according to FIG. 1 without front housing plate 7.
  • the drive lever 30 has a shaped element 32, preferably a standardized inner square, in which a commercial tool can be applied.
  • the drive lever 30 acts on its small drive lever length 56 by means of a connecting rod 36 on two symmetrically arranged, acting as output lever ratchet plates 20 (see also FIG. 6 ) with a large output lever length 57.
  • the lever ratio that is, the ratio of the drive lever length 56 to the output lever length 57, should be less than one in any case, so that a corresponding torque transmission takes place. It is z. B. between 1: 1.5 and 1:20, preferably between 1: 2 and 1:10 and in the present embodiment is about 1: 5.
  • the cylinder pins 48, 49 are preferably made of hardened steel and frictionally in holes 15 and 28 of the spacers 12, 17 and 25 connected.
  • the cylindrical pins 48, 49 protrude from both sides of the spacers 12, 17 and 25 and engage in corresponding holes 10, 23 of the housing plates 7 and the ratchet plates 20 a.
  • the drive lever 30 is symmetrical and has, in addition to the two bearing pin 31, two side cheeks 35, in which a first connecting rod pin 38 is pressed force fit.
  • a second, preferably identical connecting rod bearing pin 38 is fastened non-positively in a bore 22 of the ratchet plates 20.
  • the connecting rod bearing bushes 37 are preferably commercially available bearing bushes, which are produced, for example, from wear-resistant plastic (eg PTFE, PI) and / or from sintered metal.
  • the FIG. 5 shows the ratchet mechanism in the initial position of the drive lever 30.
  • a stop surface 34 which is formed by side cheeks 35 of the drive lever 30, with a stop 18 of the spacer plate 12 in contact.
  • the FIG. 5 also shows two pawls 40 with their teeth 41 in engagement with a toothing 4 of the driven wheel 1, while two ratchets 44 are still outside the teeth 4 of the driven wheel 1.
  • Both the two pawls 40 and the two ratchets 44 are each pressed by a leaf spring 43 and 47 against the driven wheel 1.
  • the leaf springs 43 and 47 are positively anchored in club-shaped slots 14 and 27 of the spacers 12 and 25 and are made of one or more sheet metal layers.
  • the actuation force on the not acted upon by the leaf spring 43 and 47 pawl 40 or ratchet 44 is effected by direct, immediate contact between the pawls 40 and ratchets 44th
  • a single pawl 40 or ratchet 44 should cover an angle of at most 25 ° of the teeth 4 of the driven wheel 1; the angle is z. B. between 3 ° and 25 ° and preferably between 10 ° and 20 °.
  • the two pawls 40 are rotatably mounted with their bearing pins 42 in holes 13 of the spacer plate 12, the two ratchets 44 with their bearing pins 46 rotatably mounted in bores 26 of the spacer 25.
  • the bearing bores 13 and 26 are designed as cylindrical recesses with a lateral opening, wherein the overlap angle with the pawl or ratchet bearing pin 42, 46 is more than 190 °. This has the advantage that the pawls 40 or ratchets 44 are connected in a simple manner in a form-fitting but rotatable manner with the associated spacers 12 and 25, respectively.
  • the ratchet wrench is substantially surface-symmetrical with respect to a common plane of symmetry S, which lies parallel to the housing plates 7 and the ratchet plates 20.
  • the drive lever 30 is shown in its end position. This position is defined by a stop surface 19 of the spacer 17 and a support nose 39 on the connecting rod 36.
  • the two ratchets 44 with their teeth 45 in engagement with the teeth 4 of the driven wheel 1, while the two pawls 40 are still outside the teeth 4.
  • FIG. 8 shows a section along the line BB of FIG. 7 , Again, the surface symmetry of the inventive ratchet wrench with respect to the plane of symmetry S is clearly visible.
  • FIG. 9 shows a view of a second embodiment of the inventive ratchet wrench without front housing plate.
  • an extension arm 55 is positively or materially connected to the drive lever 30; otherwise it is analogous to the first embodiment of FIG. 1 ,
  • the second embodiment then has advantages if the space conditions do not allow the attachment of a commercial Stech Whyls the inner square 32.
  • FIGS. 10 to 13 show further embodiments of pawls 40, 140 and their operation by means of a spring element 143.
  • the ratchet 44 (see FIGS. 5, 7 ) can be configured in an analogous manner.
  • the spring element 143 may be made of a metal, but alternatively also of another material, for example of a plastic or an elastomer solid or hollow profile (not shown).
  • FIG. 10 is used instead of a leaf spring 43 (see FIGS. 5, 7 ) uses a conical coil spring 143, which is embedded in a recess 114 of the spacer 12.
  • FIG. 11 shows a pair of pawls 40, 140, in which a first pawl 40 two teeth 41 and a second pawl 140 three teeth 141 have.
  • FIG. 12 has three identical pawls 40, which are actuated by means of a two-layered leaf spring 143. With this embodiment, much higher forces can be transmitted. It is particularly advantageous if the two-layered leaf spring 143 is made in one piece as shown. As a result, the positive anchoring in a club-shaped recess 144 can be made particularly advantageous. Of course, the leaf spring 143 could also be made of three or more sheet metal layers (one or more parts) to achieve the desired spring properties.
  • FIG. 13 shows an embodiment with five ratchets 144, which each have only one ratchet tooth 145.
  • This embodiment requires relatively long ratchets 144 or pawls, so that the desired positive anchoring can be realized in the bearing bores 126.
  • FIG. 14-16 A much more compact design variant for one-tooth pawl and / or ratchet packs is in the Figures 14-16 illustrated by the example of the ratchet package 244.
  • FIG. 15 is a long, continuous pin 53 in a bore 52 frictionally connected, preferably by means of a press-fit connection with the ratchet 244.
  • two short pins 153 are used, one half of which are pressed into the holes 52 'of the ratchet plates 20 and the other halves slidingly project into the retaining hole 52 of the ratchet 244 and thus allow rotation of the ratchet 244 with simultaneous positive engagement.
  • FIGS. 17 and 18 show the inventive ratchet wrench in a first embodiment according to the FIG. 1 when tightening a screw 61, 161, 162, 62, 162, 262 in a flange 163, 164 and 63, 64 with a plurality of fasteners.
  • a commercially available torque wrench 60 is used with which the required drive torque is applied.
  • the ratchet wrench is supported with its support region 54 on the adjacent nut 162 (to the right of the nut 62 to be tightened), by means of which the reaction force occurring is absorbed.
  • an additional (not shown) extension arm can be attached, by means of which the ratchet wrench can be supported on a farther fixed base.
  • the ratchet wrench When changing the direction of rotation (not shown), for example for loosening the screw 62, the ratchet wrench is rotated by 180 degrees placed on the fastener 62 so that its housing plate 7, which was on top when tightening, now lies down.
  • FIG. 19 shows the ratchet wrench with the integrated extension arm 55 according FIG. 9 already on the occasion of the FIGS. 17, 18 described screwing.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)

Claims (15)

  1. Clé à cliquet à amplification du couple, comprenant un boîtier (7, 12, 50), des moyens de capter le couple (32) accessibles de l'extérieur sur le boîtier (7, 12, 50) pour capter un couple d'entraînement, des moyens de sortie du couple (2) accessibles de l'extérieur sur le boîtier (7, 12, 50) pour la sortie d'un couple de sortie plus grand que le couple d'entraînement, et des moyens de liaison (30, 36, 20, 44, 4, 1) logés dans le boîtier (7, 12, 50) pour établir une liaison active entre les moyens pour capter le couple (32) et les moyens de sortie du couple (2) et pour l'amplification du couple d'entraînement en couple de sortie, lesquels moyens de liaison (30, 36, 20, 44, 4, 1) comprennent un levier de sortie (20, 25), une roue de sortie (1) en liaison active avec les moyens de sortie du couple (2) et un mécanisme de cliquet (44, 4) agissant entre le levier de sortie (20, 25) et la roue de sortie (1), les moyens pour capter le couple (32), les moyens de sortie du couple (2) et les moyens de liaison (30, 36 ; 20, 44, 4, 1) étant pour l'essentiel symétriques en surface par rapport à un plan de symétrie commun (S), caractérisée en ce que le boîtier (7, 12, 50) est fermé par deux plaques de boîtier (7) parallèles au plan de symétrie (S) et de préférence symétriques aussi par rapport au plan de symétrie (S), qui sont écartées l'une de l'autre par un moins un élément d'écartement du boîtier (12, 17) et sont reliées en correspondance de forme avec celui-ci, le levier de sortie (20, 25) comprend deux plaques de levier (20) parallèles au plan de symétrie (S) et de préférence symétriques aussi par rapport au plan de symétrie (S), qui sont écartées l'une de l'autre par au moins un élément d'écartement du levier (26) et reliées à celui-ci en correspondance de forme, et les plaques du boîtier (7), l'au moins un élément d'écartement du boîtier (12, 17), les plaques du levier (20) et l'au moins un élément d'écartement du levier (26) sont pour l'essentiel des plaques planes qui sont reliées entre elles en correspondance de forme.
  2. Clé à cliquet selon la revendication 1, dans laquelle le mécanisme de cliquet (44, 4) comprend au moins deux éléments de cliquet (44) qui peuvent pivoter chacun indépendamment de l'autre autour de son propre axe de cliquet (46) et sont conformés pour s'encliqueter dans une denture (4) correspondante de la roue de sortie (1).
  3. Clé à cliquet selon l'une des revendications précédentes, dans laquelle la clé à cliquet comprend un mécanisme de sécurité antiretour (40, 4) agissant entre le boîtier (7, 12, 50) et la roue de sortie (1).
  4. Clé à cliquet selon la revendication 3, dans laquelle le mécanisme de sécurité antiretour (40, 4) comprend au moins deux éléments de loquet (40) qui peuvent pivoter chacun indépendamment de l'autre autour de son propre axe de loquet (42) et qui sont conformés pour s'encliqueter dans une denture (4) correspondante de la roue de sortie (1).
  5. Clé à cliquet selon l'une des revendications 2 à 4, dans laquelle au moins deux éléments de cliquet (44) et/ou au moins deux éléments de loquet (40) sont prévus pour se transmettre réciproquement des forces et/ou des couples par contact mécanique réciproque direct.
  6. Clé à cliquet selon l'une des revendications 2 à 5, dans lequel au moins un des éléments de cliquet (44) et/ou au moins un des éléments de loquet (40) sont pressés par un élément de ressort (47, 43) contre la roue de sortie (1).
  7. Clé à cliquet selon la revendication 5 ou 6, dans laquelle un groupe formé d'au moins deux éléments de cliquet (44) et/ou au moins deux éléments de loquet (40) est pressé par un élément de ressort commun (47, 43) contre la roue de sortie (1).
  8. Clé à cliquet selon la revendication 6 ou 7, dans laquelle l'élément de ressort (47, 43, 143, 147, 247) est conformé comme un ressort à une ou plusieurs lames (47, 43, 143, 147, 247) ou comme un ressort hélicoïdal (143) et se compose de préférence de métal.
  9. Clé à cliquet selon la revendication 8, dans laquelle un élément d'écartement du boîtier (12) sert de palier aux au moins deux éléments de loquet (40).
  10. Clé à cliquet selon la revendication 9 et l'une des revendications 6 à 8, dans laquelle l'élément d'écartement du boîtier (12) sert en même temps de fixation et/ou d'appui pour l'élément de ressort (43).
  11. Clé à cliquet selon la revendication 2, dans laquelle l'élément d'écartement du levier (25) sert de palier pour les au moins deux éléments de cliquet (44).
  12. Clé à cliquet selon l'une des revendications précédentes, dans laquelle les plaques de boîtier (7), l'au moins un élément d'écartement du boîtier (12, 17), les plaques du levier (20) et l'au moins un élément d'écartement du levier (25) sont reliés entre eux au moyen de goupilles cylindriques (48, 49) et se composent de métal.
  13. Clé à cliquet selon la revendication 9 et/ou la revendication 11, dans laquelle les extrémités tournées à l'opposé de la roue de sortie des au moins deux éléments de cliquet (44) et/ou des au moins deux éléments de loquet (40) sont munies de tourillons (46, 42) qui sont supportés de façon pivotante dans des alésages de palier cylindriques (26, 13) dans l'élément d'écartement (25, 12) correspondant, et dans laquelle l'angle de recouvrement de chaque alésage de palier (26, 13) avec le tourillon (46, 42) correspondant mesure plus de 190°.
  14. Clé à cliquet selon l'une des revendications 2 à 13, dans laquelle chacun des éléments de cliquet (44) et/ou des éléments de loquet (40) recouvre un secteur de la denture de la roue de sortie (1) qui mesure de 3° à 25° et de préférence de 10° à 20°.
  15. Clé à cliquet selon l'une des revendications précédentes, dans laquelle les moyens de liaison (30, 36, 20, 44, 4, 1) sont conformés de telle sorte que le couple d'entraînement et le couple de sortie aient la même direction.
EP10165940.7A 2009-07-03 2010-06-15 Clé à grincement doté d'un renforcement du couple Not-in-force EP2269772B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH01030/09A CH701403A1 (de) 2009-07-03 2009-07-03 Ratschenschlüssel mit Drehmomentverstärkung.

Publications (3)

Publication Number Publication Date
EP2269772A2 EP2269772A2 (fr) 2011-01-05
EP2269772A3 EP2269772A3 (fr) 2014-03-05
EP2269772B1 true EP2269772B1 (fr) 2015-07-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP10165940.7A Not-in-force EP2269772B1 (fr) 2009-07-03 2010-06-15 Clé à grincement doté d'un renforcement du couple

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EP (1) EP2269772B1 (fr)
CH (1) CH701403A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3080663B1 (fr) * 2018-04-26 2020-05-22 Schneider Electric Industries Sas Module de transmission d'un effort
CN115890549A (zh) * 2022-11-13 2023-04-04 安徽机械工业学校 安徽机械技师学院 一种变矩扭力扳手

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3564953A (en) 1969-02-26 1971-02-23 B K Sweeny Mfg Co Lateral extension devices for socket wrenches
GB1554272A (en) 1975-10-02 1979-10-17 Nsw Corp Rachet tools
US4027561A (en) * 1975-11-19 1977-06-07 Junkers John K Hydraulic wrench
DE2941045C2 (de) 1979-10-10 1981-11-19 Wagner, Paul-Heinz, 5203 Much Schraubenschlüssel
US4423649A (en) * 1981-01-15 1984-01-03 Unex Corporation Ratchet drive with an equal load double pawl arrangement
DE3534431A1 (de) * 1985-01-16 1986-05-22 Hans-Joachim 5253 Lindlar Müller Ratsche mit integriertem drehmomentverstaerker
WO1994014574A1 (fr) * 1992-12-21 1994-07-07 Matricbrook Pty. Ltd. Cle a cliquet a entrainement
US5953966A (en) 1997-11-06 1999-09-21 Spirer; Steven E Hand wrench with torque augmenting means
US7062992B2 (en) * 2004-10-29 2006-06-20 Norwolf Tool Works Constant rotation rotary torque multiplier

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Publication number Publication date
EP2269772A2 (fr) 2011-01-05
CH701403A1 (de) 2011-01-14
EP2269772A3 (fr) 2014-03-05

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