EP2353790A1 - Marteau-perforateur manuel - Google Patents

Marteau-perforateur manuel Download PDF

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Publication number
EP2353790A1
EP2353790A1 EP10196701A EP10196701A EP2353790A1 EP 2353790 A1 EP2353790 A1 EP 2353790A1 EP 10196701 A EP10196701 A EP 10196701A EP 10196701 A EP10196701 A EP 10196701A EP 2353790 A1 EP2353790 A1 EP 2353790A1
Authority
EP
European Patent Office
Prior art keywords
ring seal
hammer drill
cross
sectional profile
rotation
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
EP10196701A
Other languages
German (de)
English (en)
Other versions
EP2353790B1 (fr
Inventor
Armin Eisenhardt
Hans Klöpfer
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.)
Techtronic Industries GmbH
Original Assignee
AEG Electric Tools 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 AEG Electric Tools GmbH filed Critical AEG Electric Tools GmbH
Publication of EP2353790A1 publication Critical patent/EP2353790A1/fr
Application granted granted Critical
Publication of EP2353790B1 publication Critical patent/EP2353790B1/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
    • 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
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • 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
    • B25D2217/0023—Pistons
    • 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
    • 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
    • B25D2250/365—Use of seals

Definitions

  • the present invention relates to a hand-held rotary hammer.
  • a hand-held hammer drill comprises a spindle which drives a tool holder in rotation about a rotation axis during drilling operation.
  • the spindle itself is usually driven by means of an electric motor.
  • a hammer drill usually includes a pneumatic percussion hammering in impact mode against an inserted into the tool holder tool.
  • Such a percussion usually has a piston which executes strokes parallel to the axis of rotation in a stroke in a cylinder formed in the spindle.
  • the strokes of the piston to produce pressure oscillations in the cylinder, with the aid of a transmission piston is also driven to lift motions to strike against a percussion piston, so-called striker, which in turn transmits these shocks to the respective tool.
  • the piston is sealed relative to the cylinder appropriate.
  • the piston may have at least one annular groove in which a ring seal is arranged. Due to the stroke movement of the piston, the ring seal is exposed to high wear.
  • Modern rotary hammers may also be equipped with a percussion stop that allows for drilling without impact operation.
  • a percussion stop that allows for drilling without impact operation.
  • this is a drive train between the spindle driving the electric motor and the percussion interrupted, for example by means of a clutch or the like.
  • the piston in the cylinder does not perform any lifting movements.
  • the spindle rotates about the axis of rotation and thus also about the piston.
  • the impact mode is deactivated This leads to a particularly high load on the ring seal. It can become overheated and damaged. A damaged ring seal reduces the sealing effect between the piston and cylinder, which reduces the effectiveness of the pressure oscillations and thus the efficiency of the hammer drill in impact mode.
  • the present invention addresses the problem of providing for such a hammer drill an improved embodiment, which is characterized in particular by a reduced wear.
  • the invention is based on the general idea to match the annular groove and the ring seal so that the annular seal is movable in the annular groove parallel to the axis of rotation, wherein the annular groove has a varying groove depth parallel to the axis of rotation.
  • the sealing effect between piston and cylinder depends on the contact pressure of the ring seal on the cylinder. The greater this radial contact pressure, the greater the effective frictional forces. Due to the varying groove depth and the adjustability of the ring seal in the annular groove, the ring seal can assume a position in the moving piston, in which a smaller groove depth is present, whereby the sealing effect is increased.
  • the ring seal can assume a position in which there is a greater groove depth, as a result of which the friction can be significantly reduced.
  • the wear of the ring seal can be reduced for the drilling operation. This reduction in wear has a particularly significant effect if, by means of an optional impact shut-off the impact mode is deactivated and the piston is permanently stationary during the drilling operation.
  • a groove bottom has a maximum distance from the cylinder. Axially adjacent thereto are then smaller distances. If the ring seal is in the range of the maximum distance, it is less biased against the cylinder, whereby the friction between the annular groove and cylinder for the drilling operation is reduced without impact operation. If, however, the ring seal is located in an axial region of the cross-sectional profile with smaller distances, the contact pressure of the ring seal against the cylinder increases, which is accompanied by an increased effectiveness of the sealing effect and consequently an increase in the performance of the hammer drill for impact operation.
  • the strokes of the piston cause the ring seal to move out of the central area and, depending on the stroke direction, into one or the other Area moved in with a smaller distance.
  • This relative movement between ring seal and annular groove can be supported on the one hand by the inertial forces and on the other hand can be promoted by the prevailing between the ring seal and the cylinder friction.
  • the ring seal within the annular groove automatically takes the positions with the smaller distances, which increases the sealing effect and thus the effectiveness of the impact mechanism.
  • the cross-sectional profile of the annular groove can be configured with mirror symmetry relative to a plane of symmetry running perpendicular to the axis of rotation.
  • the region with the maximum distance is then arranged centrally in the cross-sectional profile of the annular groove, while the two adjacent end regions are then the same size. This results in substantially the same effects for the ring seal for both stroke directions of the piston.
  • the maximum distance in the context of manufacturing tolerances can be generated equal to or greater than a maximum diameter of the cross section of the ring seal measured parallel to the distance between the groove base and the cylinder.
  • the maximum distance is adapted to the ring seal so that the ring seal does not touch the cylinder or virtually force-free when it is in the axial region of the maximum distance. The friction is minimized.
  • Fig. 1 and 2 includes a hand-held hammer drill 1 shown here only partially in a housing 2, a spindle 3 and a pneumatic Schlagwerk 4.
  • the spindle 3 is used in drilling operation for driving a tool holder 5.
  • the tool holder 5 and the spindle 3 rotate about an axis of rotation 6.
  • the axis of rotation 6 in the sectional plane II-II.
  • the spindle 3 itself is for example with an in Fig. 1 indicated electric motor 7 is drive-coupled, which is arranged in a separate portion of the housing 2, which is omitted here for the sake of simplicity.
  • the striking mechanism 4 is used in a striking operation to hammer against a tool, not shown here, which is used for this purpose in the tool holder 5.
  • the hammer drill 1 may preferably be equipped with a percussion stop 8. This includes, for example, a manually operable switching element 9, with the impact mode can be turned on and off.
  • a percussion stop 8 This includes, for example, a manually operable switching element 9, with the impact mode can be turned on and off.
  • the percussion mechanism 4 has a piston 10 which in stroke operation in a cylinder 11 carries out lifting movements parallel to the axis of rotation 6.
  • the cylinder 11 is formed in the spindle 3.
  • the spindle 3 is designed to be hollow cylindrical.
  • the piston 10 performs oscillating strokes corresponding to a double arrow 12, which generate pressure pulsations in the cylinder 11 in a pressure-transmitting space 13. These are transmitted to a transfer piston 14.
  • This transfer piston 14 is thereby also excited to oscillating strokes parallel to the axis of rotation 6.
  • the transitional piston 14 strikes against a percussion piston 15, which is also referred to as an anvil 15.
  • the percussion piston 15 in turn finally strikes against the tool used in the tool holder 5 tool.
  • the percussion mechanism 4 may have a crank drive 16 which couples the piston 10 via a connecting rod 17 with a drive wheel 18 which rotates with activated impact operation about a perpendicular to the axis of rotation 6 axis of rotation 19 and arranged eccentrically to the axis of rotation 19
  • Carrier pin 20 for driving the connecting rod 17 carries.
  • the connecting rod 17 is rotatably coupled to the piston 10.
  • the piston 10 does not carry out a lifting movement, so that it stands still with respect to the axis of rotation 6.
  • the Fig. 3-5 is the cutting plane at 90 ° to the cutting plane of the Fig. 2 rotated, so that there the coupling between the connecting rod 17 and piston 10 via the pin 23 is better visible.
  • Fig. 3-6 has the piston 10 on an outer side facing the cylinder 11 with respect to the rotation axis 6 in the circumferential direction closed circumferential annular groove 21 into which a ring seal 22 is inserted.
  • the annular groove 21 has a cross-sectional profile 24 which is configured substantially U-shaped.
  • This cross-sectional profile 24 lies in a cross-sectional plane which contains the axis of rotation 6.
  • the cross-sectional profile 24 has two side flanks 25 and a groove bottom 26.
  • the two side edges 25 are largely planar, wherein they each lie in a plane which extends perpendicular to the axis of rotation 6.
  • the ring seal 22 has a cross-sectional profile 27.
  • this cross-sectional profile 27 is substantially circular designed.
  • the ring seal 22 is preferably an O-ring.
  • the cross-sectional profile 24 of the annular groove 21 has a groove width 28 which is greater than a likewise measured parallel to the axis of rotation 6 width 29 of the cross-sectional profile 27 of the ring seal 22.
  • the Ring seal 22 within the annular groove 21 axially, that is parallel to the axis of rotation 6 adjustable, which in Fig. 6 indicated by a double arrow 30.
  • the cross-sectional profile 24 of the annular groove 21 has an axial region 31, in which the groove base 26 from the cylinder 11 has a maximum distance 32. Furthermore, the groove bottom 26 has at least one further axial region 33, 34, in which the groove base 26 has at least a smaller distance 35 from the cylinder 11, that is to say at least a distance 35 which is smaller than the maximum distance 32.
  • Fig. 6 has the cross-sectional profile 24 of the annular groove 21 parallel to the rotation axis 6 on both sides of the maximum distance 32 having region 31 each have a region 33 and 34 with the at least one smaller distance 35. Consequently, the maximum distance 32 provided with an area 31 between the two other areas 33, 34, so that it is also referred to below as the central region 31, while the others are also referred to below as end regions 33, 34.
  • the in Fig. 6 shown symmetrical configuration of the annular groove 21 and its cross-sectional profile 24.
  • the cross-sectional profile 24 of Ring groove 21 with respect to a plane of symmetry 36 which extends perpendicular to the axis of rotation 6, designed mirror-symmetrically.
  • Fig. 6 other special features that can be realized optionally.
  • the central region 31 of the groove base 26 is concavely curved toward the ring seal 22.
  • a circular arc-shaped curvature can be realized here. It is then particularly advantageous to choose an arc radius 37 of this arcuate central region 31 that is larger than a circle radius 38 of the circular cross-sectional profile 27 of the ring seal 22.
  • the end portions 33, 34 are preferably shaped so as to be rectilinear in at least a substantial portion.
  • These rectilinear sections are in Fig. 6 denoted by 39 and 40, respectively.
  • the rectilinear sections 39, 40 of the end regions 33, 34 enclose therebetween an obtuse angle 41, which in particular is greater than 120 ° and can have, for example, 150 ° ⁇ 10 °.
  • the rectilinear sections 39, 40 of the end regions 33, 34 pass tangentially into the curved middle region 31.
  • an arcuate, in particular circular arc-shaped transition 42 to the rectilinear flanks 25 of the cross-sectional profile 24 of the annular groove 21 is provided.
  • Fig. 6 shows another special feature that can be realized as an option.
  • the ring seal 22 is arranged in the central region 31 of the annular groove 21. It is thus located in the region of the annular groove 21, which has the largest groove depth, ie the maximum distance 32.
  • This maximum distance 32 can now be chosen equal to a preferred embodiment as a diameter 43 of the cross section 27 of the ring seal 22, said diameter 43rd is measured parallel to the distance between groove base 26 and cylinder 11.
  • the diameter 48 is measured parallel to the distance 32, since the originally circular cross section of the ring seal 22 under radial stress, which is also in the state of the Fig. 6 can be present, is deformed more or less oval or elliptical.
  • the cross-sectional profile 24 of the annular groove 21 is parallel to the axis of rotation 6 at most 50% greater than the cross-sectional profile 27 of the ring seal 22nd
  • the central region 31 is designed such that it extends in a straight line and parallel to the axial direction 49 and thus parallel to the axis of rotation 6.
  • the annular groove 21 has a constant portion in the cross-sectional profile 24 in the central region 31 in the axial direction 49.
  • the two end regions 33, 34 are curved and pass tangentially into the rectilinear central region 31.
  • the end regions 33, 34 can be curved in a circular arc, wherein they then each have a radius 50 or 51.
  • the two radii 50, 51 are suitably the same size; However, they can be different in size.
  • the respective radius 50, 51 is greater than the radius 38 of the cross-sectional profile 27 of the ring seal 22, which is present at least in the relaxed state of the ring seal 22.
  • the end portions 33, 34 thereby form ramps along which the ring seal 22 is lifted radially outward as the ring seal 22 moves within the annular groove 21 from the central region 31 into one of the end regions 33, 34.
  • the hammer drill 1 can be connected with a cable, not shown here to a power grid. It is also possible to equip the hammer drill 1 with a battery, whereby the hammer drill 1 can be operated independently of a power grid.
  • a battery is in Fig. 1 but not shown. It usually closes in relation to the presentation in Fig. 1 at the bottom of the housing 2 at.
  • Fig. 3 represents an operating state in which with the help of the impact stop 8 the impact mode is deactivated.
  • the piston 10 performs relative to the cylinder 11 no strokes; the piston 10 is.
  • the ring seal 22 automatically positioned within the annular groove 21 in the central region 31, in which the maximum distance 32 prevails.
  • the ring seal 22 has a minimum outer diameter 44, which generates a minimum friction with respect to the rotating spindle 3.
  • the ring seal 22 With hammer mechanism 4 deactivated, the ring seal 22 automatically assumes this middle position, since the end regions 33, 34 act like ramps which center the ring seal 22 in the middle region 33.
  • the ring seal 22 is driven by the inner bias of the ring seal 22, which experiences this when it is widened in the end regions 33, 34 by the ramp effect.
  • This condition according to Fig. 3 can also occur when activated impact mode, and always when the piston 10 reverses the direction of movement when passing through one of its dead centers and is temporarily stationary.
  • Fig. 4 Due to inertial forces and / or due to the friction between the ring seal 22 and cylinder 11 while the ring seal 22 is axially displaced within the annular groove 21 against the stroke direction 45, causing them in the area 33 is moved, which faces the tool holder 5.
  • the hub 45 is oriented to the right, so that the ring seal 22 is adjusted in the left end portion 33. It comes to the left flank 25 of the annular groove 21 to the plant. Since in this end region 33 of the smaller distance 35 is effective, there is a radial expansion of the annular seal 22, so that this has an outer diameter 46 in the sequence, which is greater than that in Fig. 3 shown outside diameter 44, the ring seal 22 has at rest piston 10.
  • the larger diameter 46, 48 which automatically adjusts during impact operation, increase the contact pressure of the ring seal 22 on the cylinder 11 and thereby improve the sealing effect and thus the performance of the striking mechanism 4 or of the hammer drill 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP10196701.6A 2010-01-29 2010-12-23 Marteau-perforateur manuel Not-in-force EP2353790B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010006152.2A DE102010006152B4 (de) 2010-01-29 2010-01-29 Handgeführter Bohrhammer

Publications (2)

Publication Number Publication Date
EP2353790A1 true EP2353790A1 (fr) 2011-08-10
EP2353790B1 EP2353790B1 (fr) 2016-04-06

Family

ID=43942101

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10196701.6A Not-in-force EP2353790B1 (fr) 2010-01-29 2010-12-23 Marteau-perforateur manuel

Country Status (4)

Country Link
US (1) US8651197B2 (fr)
EP (1) EP2353790B1 (fr)
CN (1) CN102139481B (fr)
DE (1) DE102010006152B4 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9062770B2 (en) * 2013-04-12 2015-06-23 Chin-Chiu Chen Sealing device for a collet chuck
CN104389910B (zh) * 2014-07-10 2016-08-31 浙江奔宇工具有限公司 用于手持工具的多用轴承座
EP3670096A1 (fr) * 2018-12-21 2020-06-24 Hilti Aktiengesellschaft Machine-outil portative

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3067584A (en) * 1962-02-15 1962-12-11 Black & Decker Mfg Co Sealing ring means for reciprocating piston used in power-operated percussive tool
DE2729596A1 (de) * 1977-06-30 1979-01-11 Hilti Ag Bohrhammer mit pneumatisch angetriebenem schlagkolben
EP1027963A2 (fr) * 1999-02-09 2000-08-16 Black & Decker Inc. Perceuse a percussion
DE102008061173A1 (de) * 2008-12-09 2010-06-10 Aeg Electric Tools Gmbh Hammerwerk für einen pneumatischen Hammer

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2420104A (en) * 1943-07-22 1947-05-06 Maytag Co Seal guard ring
US3353454A (en) * 1966-04-05 1967-11-21 William F Donovan Ratchet
CH560340A5 (fr) 1973-02-09 1975-03-27 Occident Etablissements
US4418924A (en) * 1980-10-20 1983-12-06 Mack James F Bi-surface sealing mechanism with rolling/sliding O-ring
US4428276A (en) * 1981-10-19 1984-01-31 Humphrey Products Company O-Ring seal for piston of double-acting fluid pressure cylinder
US4577870A (en) * 1984-02-13 1986-03-25 American Standard Inc. O-ring seal in channel with fluid pressure equalization means
DE3405547A1 (de) * 1984-02-16 1985-08-14 Hilti Ag, Schaan Auspresskolben fuer behaelter
US5071318A (en) * 1990-01-22 1991-12-10 Westinghouse Electric Corp. Reactor coolant pump having improved dynamic secondary seal assembly
US5617879A (en) * 1995-02-17 1997-04-08 Deublin Company Sealing arrangement for a coolant union having a floating seal assembly
US5941537A (en) * 1997-09-05 1999-08-24 General Eletric Company Pressure actuated static seal
GB9902789D0 (en) * 1999-02-09 1999-03-31 Black & Decker Inc Rotary hammer
DE10311155A1 (de) 2003-03-14 2004-09-23 Gapi Technische Produkte Gmbh Dichtring und Dichtringanordnung
EP1674211A1 (fr) * 2004-12-23 2006-06-28 BLACK & DECKER INC. Carter pour un outil motorisé
DE102007000081A1 (de) * 2007-02-08 2008-08-21 Hilti Ag Handwerkzeugmaschine mit pneumatischem Schlagwerk

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3067584A (en) * 1962-02-15 1962-12-11 Black & Decker Mfg Co Sealing ring means for reciprocating piston used in power-operated percussive tool
DE2729596A1 (de) * 1977-06-30 1979-01-11 Hilti Ag Bohrhammer mit pneumatisch angetriebenem schlagkolben
US4192391A (en) * 1977-06-30 1980-03-11 Hilti Aktiengesellschaft Piston for a hammer drill having a separable part
EP1027963A2 (fr) * 1999-02-09 2000-08-16 Black & Decker Inc. Perceuse a percussion
DE102008061173A1 (de) * 2008-12-09 2010-06-10 Aeg Electric Tools Gmbh Hammerwerk für einen pneumatischen Hammer

Also Published As

Publication number Publication date
DE102010006152B4 (de) 2014-07-03
DE102010006152A1 (de) 2011-08-04
CN102139481A (zh) 2011-08-03
EP2353790B1 (fr) 2016-04-06
US8651197B2 (en) 2014-02-18
US20110186317A1 (en) 2011-08-04
CN102139481B (zh) 2015-03-11

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