EP2452784B1 - Machine-outil manuelle - Google Patents

Machine-outil manuelle Download PDF

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Publication number
EP2452784B1
EP2452784B1 EP11185226.5A EP11185226A EP2452784B1 EP 2452784 B1 EP2452784 B1 EP 2452784B1 EP 11185226 A EP11185226 A EP 11185226A EP 2452784 B1 EP2452784 B1 EP 2452784B1
Authority
EP
European Patent Office
Prior art keywords
working axis
along
grooves
recesses
damping ring
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.)
Active
Application number
EP11185226.5A
Other languages
German (de)
English (en)
Other versions
EP2452784A1 (fr
Inventor
Olaf Koch
Matthias Keith
Ali Shadavakhsh
Dieter Kraus
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.)
Hilti AG
Original Assignee
Hilti AG
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 Hilti AG filed Critical Hilti AG
Publication of EP2452784A1 publication Critical patent/EP2452784A1/fr
Application granted granted Critical
Publication of EP2452784B1 publication Critical patent/EP2452784B1/fr
Active 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
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/26—Lubricating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0019—Guide-sleeves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2222/00—Materials of the tool or the workpiece
    • B25D2222/54—Plastics
    • B25D2222/57—Elastomers, e.g. rubber
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/345—Use of o-rings

Definitions

  • the present invention relates to a hand tool, in particular a hand tool for chiselling and / or drilling, according to the preamble of claim 1 and as from WO 03/024671 A2 known.
  • the hand tool of the invention has an accelerated along a working axis impact body and a guide for the impact body.
  • the impactor may for example be a pneumatically excited racket or intermediate racket of a pneumatic percussion.
  • a bumper limited movement of the impactor along the working axis and has an elastic Dämpfring on.
  • the bounce damper may be provided to stop a movement of the impactor in an impact direction and / or to stop a movement of the impactor against the direction of impact after a rebound.
  • the bumper may be provided to stop the striker when it is above a designated position, e.g. at a space, moved out.
  • the damping ring has at least one end face extending radially to the working axis grooves.
  • Lubricants which among other things, improve sliding of the racket in the guide, can crawl in pockets between the damper ring and the guide.
  • the grooves allow the lubricants to escape from the pockets when the damper ring is compressed in an impact of the impactor.
  • a hand tool has an accelerated along a working axis striker, a guide for the striker and a bounce.
  • the bumper limited movement of the impactor along the working axis and has an elastic Dämpfring which is supported with a perpendicular to the working axis bearing surface on a mating surface of the guide.
  • Between the elastic damping ring and the guide are provided radially and / or axially extending to the working axis channels.
  • the channels may be formed by depressions in the Dämpfring and / or grooves in the opposite surface of the guide.
  • the depressions may be formed, for example, as narrow, steep grooves or wider, shallow indentations.
  • the grooves divide a contact surface of the end face into a plurality of separate segments.
  • the grooves can occupy an area of between 5% and 15% of the front side.
  • the grooves lead to a weakening of the elastic Dämpfrings and thus its life. It has been recognized that with an area fraction of 5% to 15%, the benefits of the grooves outweigh their disadvantages.
  • the grooves have a depth of between 5% and 10% of the dimension of the damping ring along the working axis.
  • the damper ring made of plastic, e.g. Elastomers from the class of hydrogenated acrylonitrile butadiene rubbers is formed.
  • the plastic must not be mixed with the lubricants e.g. Soak grease or oil, otherwise the plastic will become hard and inelastic.
  • the surface area increased by the grooves increases the problem of a creep of Schnierstoffe in the elastic Dämpfring.
  • the guide has a sleeve movable along the working axis and the sleeve is along the working axis by two elastic damping rings. biased.
  • the sleeve may have an at least partially oriented in the direction of the working axis stop surface for a radially projecting bead of the impactor.
  • the sleeve serves as a catcher for the impactor and introduces the forces evenly into the elastic damping ring.
  • the movable sleeve is clamped between two elastic Dämpfringe, both having radially to the working axis extending grooves.
  • the elastic damping ring has protruding nubs in the radial direction.
  • the nubs prove to be suitable to prevent the Dämpfring turning and walking in the lead.
  • Fig. 1 schematically shows a hammer drill.
  • the hammer drill 1 has a tool holder 2 , in which a drill bit 3 can be used as a tool.
  • a primary drive of the hammer drill 1 is a motor 4, which drives a hammer mechanism 5 and optionally an output shaft 6 .
  • a user can guide the hammer drill 1 by means of a handle 7 and take means of a system switch 8 to the hammer drill 1 is in operation.
  • the hammer drill 1 rotates the drill bit 3 continuously about a working axis 9 and can thereby beat the drill bit 3 along the working axis 9 in a substrate.
  • the output shaft 6 can additionally turn the drill bit 3 about the working axis 9 during the beating.
  • the tool holder 2 has a receiving sleeve 10 into which one end of the drill bit 3 can be inserted. Locking elements 11 in the receiving sleeve 10 secure the drill bit 3 against falling out.
  • the receiving sleeve 10 has an inner, to the drill bit 3 form-fitting, non-rotationally symmetrical contour, which transmits a torque from the receiving sleeve 10 to the drill bit 3 .
  • radially inwardly projecting pins or balls 11 may be provided in the receiving sleeve 10 .
  • the striking mechanism 5 is, for example, a pneumatic impact mechanism 5 .
  • An example piston-shaped exciter 12 and an example piston-shaped racket 13 are guided in the striking mechanism 5 along the working axis 9 movable.
  • the exciter 12 may also be pot-shaped.
  • the exciter 12 is coupled via an eccentric 14 or a wobble finger to the motor 4 and forced to a periodic, linear movement.
  • An air spring formed by a pneumatic chamber 15 between exciter 12 and racket 13 (percussion piston) couples a movement of the racket 13 to the movement of the exciter 12 on.
  • the racket 13 can strike directly on a rear end of the drill bit 3 or indirectly transfer part of its momentum to the drill bit 3 via a substantially stationary intermediate racket 16 (striker).
  • the intermediate beater 16 is pressed against the drill bit 3 along the working axis 9 against a direction of impact 17 against a stop 18 on the machine side.
  • the racket 13 drives the intermediate racket 16 along with the drill bit 3 in the direction of impact 17 a piece in the direction of impact 17 forward.
  • a bumper 20 on the stop 18 reduces the peak load during kickback. Rebounds can also occur when a user lifts the hammer 1 from the ground.
  • the intermediate beater 16 bounces in the direction of impact 17 on a tool-side stop 21 and is reflected by this to the machine-side stop 18 .
  • Fig. 2 shows in more detail an exemplary guide 22 of the intermediate beater 16 .
  • the intermediate beater 16 may have a rotationally symmetrical shape to the working axis 9 .
  • a tool-side portion 23 and / or a machine-side portion 24 of the intermediate beater 16 are prismatic, for example cylindrical.
  • the intermediate beater 16 has a bead 25 which projects radially relative to the prismatic sections 23 , 24 and which is preferably arranged along the working axis 9 between them.
  • the guide 22 has one or more sleeve-shaped sections 26 , which surround the prismatic sections 23 , 24 accurately, radially and along the working axis 9 .
  • the sleeves 26 can also form the machine-side stop 18 and the tool-side stop 21 , which limit movement of the intermediate beater 16 along the working axis 9 in cooperation with the projecting bead 25 .
  • the sleeves 26 are preferably attached to a machine housing 27 of the hammer drill 1 .
  • the bumper 20 is disposed on the machine-side stop 18 .
  • the bumper 20 includes an elastic, annular damper 28 made of plastic, for example, synthetic rubber, hydrogenated acrylonitrile-butadiene rubber.
  • the damping ring 28 is preferably located at a side facing away from the intermediate beater 16 end face 29 on a mating surface 30 of the sleeve 26 at.
  • the damping ring 28 may be used in the guide 22 radially biased and / or fixed by clamping body 31 , for example snap rings, along the working axis 9 .
  • Fig. 3 shows the damper ring 28 in a plan view of the end face 29 , which rests against the sleeve 26 .
  • Fig. 4 shows a section in the plane IV-IV.
  • the damping ring 28 may have a base body with a substantially uniform cord diameter 32 so circular cross-section along the circumference.
  • the curved end face 29 may be flattened to a partially planar contact surface 33 .
  • the flat contact surface 33 can rest evenly over a large area on the sleeve 26 .
  • Radial (perpendicular to the working axis 9 ) extending grooves 34 divide the contact surface 33 in a plurality of segments 35 (as hatched area indicated).
  • the grooves 34 may be arranged at equal angular intervals about the working axis 9 . It has proved to be advantageous if the angular distances 36 between the grooves 34 are less than 30 degrees.
  • the grooves 34 form radially extending, ie perpendicular to the working axis 9 extending channels between the damping ring 28 and the sleeves 26 against which the damping ring 28 abuts out. Lubricant that has accumulated in cavities between the damping ring 28 and the guide 22 can escape through the channels in the direction of the working axis 9 when the damping ring 28 is compressed. The otherwise incompressible lubricants thus do not impair or only slightly affect the elastic compression of the damping ring 28 .
  • the surface area of the contact surface 33 is reduced by the grooves 34 by 5% to 15%, ie in relation to a damping ring 28 of the same construction except for the grooves 34 .
  • the total of 8 grooves 34 have a width 37 of about 2.5 mm and the circumference of the damping ring 28 is about 240 mm.
  • the width 37 of the grooves 34 may be in a range of 2 mm to 4 mm, thereby ensuring on the one hand a sufficiently uniform force in the damping ring 28 in a compression and a sufficiently low capillary action for the grooves 34 flowing through fluids.
  • the number of grooves 34 can be adapted to the size of the damping ring 28 to adjust the accumulated surface area of all grooves 34 at about 5% to 15% of the front side.
  • the grooves 34 preferably have a depth 38 (dimension along the working axis 9) of 0.5 mm to 2.0 mm.
  • the cord diameter 32 of the damping ring 28 is about 10 to 20 times as large. Lubricating fluid that has crept between the damper ring 28 and the guide 22 may escape through the grooves 34 upon compression of the damper ring 28 .
  • nubs 39 may be provided at the radially outer periphery of the damping ring 28 .
  • the nubs 39 have a small elevation, for example from 1% to 2% of the average outer diameter 40 of the damping ring 28.
  • the damping ring 28 can be used under a small radial bias in the, preferably cylindrical, guide 22 .
  • the damping ring 28 may also have tool-side grooves 41 on a second working axis 9 oriented perpendicular to the end face 42 , which may be formed equal to the machine-side grooves 34 .
  • the tool-side grooves 41 and the machine-side grooves 34 may be arranged at an angle to each other about the working axis 9 .
  • a second impact damper 50 may be arranged on the tool-side stop 21 , which is constructed as well as the impact damper 20 .
  • a second damping ring 43 of the second impact damper 50 can be oriented with its flat end face 51 in the direction of impact 17 on the tool-side stop 21 .
  • a further development of the impact absorber 20 provides a metallic disc 52 .
  • the metallic disc 52 bears against the damping ring 28 on its end face 53 facing the bead 25 and is movable along the working axis 9 .
  • the washer 52 may protect the damper ring 28 against wear.
  • the end face 54 of the disk 52 facing the intermediate beater 16 and the surface 55 of the bead 25 facing this end face 54 are designed as perfectly fitting counterparts.
  • Another bounce 60 of the type described above can be used as acting in the direction of impact 17 stop for the racket 13 .
  • Fig. 5 shows a detail of an inventive percussion 70 , which is designed for a purely chiseling tool.
  • a bracket 71 may surround a collar of the tool for locking.
  • a drive of the illustrated intermediate beater 16 can be carried out as in the previous embodiments.
  • a drive of the intermediate beater 16 by a pneumatic driven pneumatic percussion is also possible.
  • a motor-driven exciter 12 via valves alternately a tool-side end face and a tool facing away from the end face of the racket 13 are subjected to compressed air.
  • the beater 13 or the intermediate beater 16 is accelerated by a propellant charge or electrodynamic forces.
  • a guide 72 for the intermediate beater 16 has a first sleeve 73 , which is fixedly connected to the housing 74 , and along the working axis 9 offset a second sleeve 75, which is guided along the working axis 9 movable.
  • the first sleeve 73 surrounds flush the circumference of the front cylindrical portion 76 of the intermediate beater 16.
  • a slight clearance between the first sleeve 73 and the intermediate beater 16 allows the intermediate beater 16 a movement along the working axis 9.
  • a sealing ring 77 can in the first sleeve 73 may be used to reduce the ingress of dust along the intermediate beater 16 into the striking mechanism.
  • the first sleeve 73 and the second sleeve 75 limit the movement of the intermediate beater 16 along the working axis 9 .
  • the bead 25 of the intermediate beater 16 can move in a cavity 78 between the two sleeves 73 , 75 .
  • the first sleeve 73 forms part of a stop in the direction of the tool
  • the second sleeve 75 forms a stop on the machine side.
  • a first bumper 80 for stopping the intermediate beater 16 in the direction of impact 17 is applied to the first sleeve 73 along the working axis 9 .
  • the first bumper 80 has a first damper ring 81 inserted into the cavity 78 .
  • One end face 82 of the damping ring 81 contacts an opposite to the striking direction 17 facing stop surface of the first sleeve 73.
  • a metallic disk 83 may rest on another face of the first damping ring 81 and forms a part of the first rebound damper 80.
  • the metal disk 83 is preferably formed by the first damper ring 81 biased against a radial projection 84 on the guide 72 .
  • a to the bead 25 of the intermediate beater 16 facing stop surface 85 of the metallic disc 83 preferably has a shape of the bead 25 complementary shape.
  • a second bumper 90 for stopping a movement of the intermediate beater 16 against the direction of impact 17 is formed by the second sleeve 75 and a second damping ring 91 .
  • the second sleeve 75 is arranged movably within the housing 74 along the working axis 9 .
  • the housing 74 has a tubular portion 92 within which the second sleeve 75 slides.
  • the second sleeve 75 is arranged along the working axis 9 between a second damping ring 91 and a third damping ring 93 , which are supported on the guide 72 .
  • the guide 72 may provide for this corresponding radially projecting to the working axis 9 stops 95 .
  • the movable sleeve 75 preferably has a stop surface 96 complementary to the shape of the bead 25. After rebounding from the front first bumper 80 , the bead 25 may abut against the movable sleeve 75 .
  • the second damper ring 91 is compressed and dampens the movement of the intermediate racket 16 . Sealing rings on a radially inner surface and on a radially outer surface of the second sleeve 75 prevent creepage of dust along the insects along the insects 16 and between the second sleeve 75 and the housing 74 in the striking mechanism.
  • the Dämpfringe 81, 91, 93 are formed as O-rings, which have radially extending grooves 34 on at least one side.
  • the O-ring can be formed according to the previous examples.
  • the grooves 34 extend substantially perpendicular to the working axis 9.
  • the depth of the grooves 34 is selected such that upon compression of the Dämpfrings 91 , these grooves 34 are not closed.
  • a depth of 0.5 mm to 2.0 mm proves to be sufficient for the setback of the intermediate beater 16 setback when the damping ring 91 is only slightly weakened by the number and width of the grooves 34 .
  • a proportion of the grooves 34 on the front side of the damping ring 91 should be less than 15% for this purpose.
  • the grooves 34 may be provided on one side, on one end face or on both sides, on opposite end faces. Alternatively or additionally, radially extending grooves may be provided in the stops 95 . In this way, channels form equally between the elastic damping ring 91 and the stops 95 against which the damping ring 91 abuts, through which lubricant can escape: the elastic ring can also be formed without grooves in this embodiment.
  • the radially extending grooves in the stops 95 are preferably sized equal to the grooves 34 described above.
  • the damping ring 100 may be an O-ring having a substantially circular periphery, that is, a constant outer diameter 40, and a substantially circular cross-section, that is, be formed to a constant cord diameter 32nd
  • An end face 29 of the damping ring 100 can be slightly flattened for a planar contact surface 33 along a working axis 9 .
  • a number and width 37 of the grooves 102 may be selected equal to the criteria for the damping ring 28 . Due to the lower radial compared to the axial load, the grooves 102 can also be formed with a larger width.
  • a radial depth 103 of the grooves 102 is limited, since the weakening of the damping ring in the radial direction as shown also has a significant effect on the axial load capacity. The depth 103 is in the range between 5% and 10% of the cord diameter 32 .
  • a minimum depth 103 of 0.5 mm to 2.0 mm proves to be advantageous for allowing the viscous lubricants to flow in the grooves 102 .
  • the damping ring 110 may be formed as an O-ring with a substantially circular circumference, ie a constant outer diameter 40 , and a substantially circular cross-section, ie a constant cord diameter 32 .
  • An end face 29 of the damping ring 110 may be slightly flattened for a planar contact surface 33 along a working axis 9 .
  • indentations 111 are provided, which opposite a bulge 112 are arranged on the other end face 53 .
  • An axial depth 113 of the concave 111 may be equal to an axial height 114 of the bulge 112 .
  • the cord diameter 32 is constant along the entire circumference. The damping ring 110 undergoes no weakening in the region of the concavity 111 .
  • a width 115 of the concavities 111 and the bulges 112 may be between 20 degrees and 40 degrees along the circumference 101 .
  • the indentations 111 and bulges 112 preferably have only about 40 degrees to the end face 53 inclined facets.
  • the bulges 112 fill in a collision of the impactor cavity of the concavities 111 . In the area of steep facets, the occurring gravitational forces exceed the load capacity of the plastics used.
  • FIGS. 10, 11 and 12 show a further embodiment of a damping ring 120th
  • the Dämpfring 120 has radial indentations 121 in its circumference, which are offset by radial bulges 122 to the working axis 9 out.
  • a cord diameter 32 thus remains constant along the entire circumference.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Earth Drilling (AREA)
  • Vibration Dampers (AREA)

Claims (6)

  1. Machine-outil à main comportant un élément de percussion (13, 16) accéléré le long d'un axe de travail (9), un guide (22 ; 72) pour l'élément de percussion (13, 16), un absorbeur de choc (20, 50, 60 ; 80, 90) qui limite un mouvement de l'élément de percussion (13, 16) le long de l'axe de travail (9) et qui comporte une bague d'amortissement élastique (28, 43 ; 91, 93, 81), dans laquelle la bague d'amortissement (28, 43 ; 91, 93, 81) a, sur au moins une face avant (29), des renfoncements s'étendant radialement (34, 111) et/ou sur la circonférence (101) le long de l'axe de travail (9), caractérisée en ce que le guide (72) comporte une douille (75) mobile le long de l'axe de travail (9), dans laquelle la douille mobile (75) est précontrainte le long de l'axe de travail (9) entre deux bagues d'amortissement élastiques (91, 93) qui comportent toutes les deux des rainures (34) s'étendant radialement par rapport à l'axe de travail (9).
  2. Machine-outil à main selon la revendication 1, caractérisée en ce que les renfoncements (34) divisent une surface de contact (33) de la face avant (29) et/ou les renfoncements (102) divisent une surface de contact le long de la circonférence (101) en plusieurs segments séparés.
  3. Machine-outil à main selon la revendication 1 ou 2, caractérisée en ce que les renfoncements (34) occupent une partie de surface comprise entre 5 % et 15 % d'une surface de contact (33) de la face avant (29).
  4. Machine-outil à main selon la revendication 1, caractérisée en ce que les renfoncements sont des concavités radiales (121) dont des convexités radiales opposées (122) sont prévues et/ou les renfoncements sont des concavités (111) sur la face avant dont des convexités opposées (112) sont prévues sur la face avant opposée.
  5. Machine-outil à main selon la revendication 1, caractérisée en ce que la douille mobile (75) comporte une surface de contact orientée au moins partiellement en direction de l'axe de travail (9) pour un bossage faisant radialement saillie (25) de l'élément de percussion (13, 16).
  6. Machine-outil à main selon l'une des revendications précédentes, caractérisée en ce que la bague d'amortissement élastique (28, 43 ; 91, 93, 81) comporte des tenons (39) faisant saillie perpendiculairement à l'axe de travail (9).
EP11185226.5A 2010-11-16 2011-10-14 Machine-outil manuelle Active EP2452784B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010044011A DE102010044011A1 (de) 2010-11-16 2010-11-16 Handwerkzeugmaschine

Publications (2)

Publication Number Publication Date
EP2452784A1 EP2452784A1 (fr) 2012-05-16
EP2452784B1 true EP2452784B1 (fr) 2015-04-08

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ID=44785664

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11185226.5A Active EP2452784B1 (fr) 2010-11-16 2011-10-14 Machine-outil manuelle

Country Status (4)

Country Link
US (1) US9272408B2 (fr)
EP (1) EP2452784B1 (fr)
CN (1) CN102554877A (fr)
DE (1) DE102010044011A1 (fr)

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EP2886260A1 (fr) * 2013-12-19 2015-06-24 HILTI Aktiengesellschaft Appareil d'enfoncement
EP2918376A1 (fr) * 2014-03-12 2015-09-16 HILTI Aktiengesellschaft Machine-outil portative de burinage
EP2923797A1 (fr) * 2014-03-28 2015-09-30 HILTI Aktiengesellschaft Cloueur à poudre
EP2923800A1 (fr) * 2014-03-28 2015-09-30 HILTI Aktiengesellschaft Cloueur à poudre
KR102151110B1 (ko) * 2014-06-11 2020-09-02 현대모비스 주식회사 베어링 부시
EP3314059A4 (fr) * 2015-06-29 2019-03-27 Terminator IP Limited Raccord d'outil absorbant les chocs
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EP3822036A1 (fr) * 2019-11-12 2021-05-19 Hilti Aktiengesellschaft Agencement de mécanisme de frappe
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EP2452784A1 (fr) 2012-05-16
US20120125650A1 (en) 2012-05-24
CN102554877A (zh) 2012-07-11
US9272408B2 (en) 2016-03-01
DE102010044011A1 (de) 2012-05-16

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