EP1765556B1 - Schlag- und/oder bohrhammer mit sicherheitskupplung - Google Patents

Schlag- und/oder bohrhammer mit sicherheitskupplung Download PDF

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Publication number
EP1765556B1
EP1765556B1 EP05758900A EP05758900A EP1765556B1 EP 1765556 B1 EP1765556 B1 EP 1765556B1 EP 05758900 A EP05758900 A EP 05758900A EP 05758900 A EP05758900 A EP 05758900A EP 1765556 B1 EP1765556 B1 EP 1765556B1
Authority
EP
European Patent Office
Prior art keywords
ring
latching
toothed wheel
hammer
driving toothed
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
EP05758900A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1765556A1 (de
Inventor
Rudolf Berger
Wolfgang Schmid
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.)
Wacker Neuson SE
Original Assignee
Wacker Construction Equipment 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 Wacker Construction Equipment AG filed Critical Wacker Construction Equipment AG
Publication of EP1765556A1 publication Critical patent/EP1765556A1/de
Application granted granted Critical
Publication of EP1765556B1 publication Critical patent/EP1765556B1/de
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
    • 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
    • B25D2250/195—Regulation means
    • B25D2250/205—Regulation means for torque
    • 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
    • B25D2250/301—Torque transmission means

Definitions

  • the invention relates to a hammer drill and / or hammer drill according to the preamble of claims 1 or 5, which is equipped with a safety coupling.
  • a hammer and / or hammer drill is from the DE-A-4215288 known.
  • the safety coupling can be arranged in various technical designs at different locations within the device in the force or torque flow, in particular in the torque flow between a drive of the hammer (eg an electric or internal combustion engine) and a tool-carrying tool holder. Fitting locations between a crankshaft belonging to the drive and a drilling shaft receiving or holding the tool holder have proven particularly suitable.
  • a drive of the hammer eg an electric or internal combustion engine
  • a tool-carrying tool holder Fitting locations between a crankshaft belonging to the drive and a drilling shaft receiving or holding the tool holder have proven particularly suitable.
  • Safety clutches can be configured in many ways. In practice, so-called detent or claw-type safety clutches, which are arranged in the area of the drilling shaft or a percussion tube belonging to a striking mechanism of the hammer, have proved to be particularly advantageous. In this case, usually mounted on the drilling shaft or percussion tube, provided with frontal notches or claws drive gear by a clutch against a likewise provided with detents, integral with the percussion tube or the drilling shaft pressed federation.
  • Such safety clutches are inexpensive to produce, robust and durable, since in the case of response, the rotational speeds are low and the installation site large diameter and enough space for a generous dimensioning is available.
  • Fig. 8 shows a section through a typical, z. B. off DE 101 45 464 A1 known hammer drill.
  • the torque of an electric motor 1 serving as a drive is transmitted via a plurality of gears and a crankshaft 2 to a main shaft 3 and finally via further gears on a drilling shaft 4, which carries a tool holder 5, in turn inserted into a not shown drilling and / or chiselling tool can be.
  • a safety coupling 6 is integrated, which has a supported by a spring 7 toothed disk 8.
  • a predetermined limit torque is exceeded 8 such large axial forces arise on the teeth of the toothed disc that the toothed disc 8 is pushed back against the action of the spring 7.
  • An interruption of the torque flow is the result, so that a threat to the operator of the hammer, z. B. in a blocking of the drilling tool during a drilling process, is avoided.
  • a hammer drill is known with a safety coupling in which the arranged on the safety clutch drive gear must be axially displaced against the action of a spring to be brought out of engagement of mated with him mating gear and so to interrupt the flow of torque.
  • the hammer is new, this is not a problem.
  • the drive gear wheel after prolonged use, has run in such a way with the counter gear due to wear that it can no longer be displaced axially. But then a desired response of the safety clutch is not guaranteed when the limit torque is exceeded.
  • Rotary hammers are also often switch between several modes of operation: Except a pure drilling operation (with hammer mechanism off) and a hammer drill operation (drilling and chiseling) is also a pure chisel operation possible, in which the tool is not driven to rotate. In known hammers, however, the bit is then freely and uncontrollably rotatable, which can be unfavorable in the management of the entire device.
  • the invention has for its object to provide a hammer and / or rotary hammer with a safety coupling, which are improved in terms of wear resistance, reliability and functionality.
  • the impact hammer and / or hammer drill according to the invention is equipped with a safety clutch, which can be driven by the drive torque with the drive gear, an axially arranged to the drive gear final ring over which the torque is feasible, and arranged between the drive gear and the locking ring locking device having.
  • the latching device ensures a torque flow between the drive gear and the end ring in a normal operating state. In an overload condition in which a torque exceeding a predetermined limit torque is introduced into the safety clutch, the detent interrupts the torque flow between the drive gear and the end ring.
  • the drive gear can always remain in its intended axial position and thus comb in case of overload with an associated mating gear.
  • the latching device has a locking ring arranged between the drive gear and the closing ring.
  • the locking ring is rotationally fixed relative to the closing ring and axially displaceable against the action of a spring device.
  • the drive gear and the locking ring have an interlocking locking toothing, via which the torque to be transmitted from the safety clutch is conducted.
  • the locking ring In the normal operating state of the locking ring is pressed by the spring means axially against the drive gear, so that the locking teeth mesh.
  • the overload condition of the locking ring is axially displaced in the direction of the end ring against the action of the spring means, so that the locking teeth of locking ring and drive gear are disengaged.
  • a second embodiment of the invention provides a kinematic reversal of the embodiment described above.
  • the latching ring disposed between the drive gear and the end ring is rotationally fixed relative to the drive gear and axially displaceable relative to the drive gear against the action of a spring means.
  • the locking teeth are - in contrast to the embodiment described above - not formed between the drive gear and the locking ring, but between the closing ring and the locking ring.
  • the closing ring has a latching toothing on an end face facing the latching ring, while the latching ring has a latching toothing which fits on the latching toothing of the closing ring on an end face facing the closing ring.
  • the locking ring is no longer supported by the spring device against the end ring, but against the drive gear.
  • the locking ring In the normal operating state, the locking ring is pressed against the closing ring in such a way that the locking teeth mesh with one another.
  • the locking ring In the overload condition, however, the locking ring is axially displaced in the direction of the drive gear, so that the locking teeth are disengaged.
  • the axial position of the drive gear and / or the end ring is fixed at least in an axial direction.
  • a movement of the drive gear or of the end ring in the opposite axial direction may be permissible under circumstances and then should only be possible against the action of a spring.
  • various embodiments of the safety clutch are possible.
  • the drive gear is rotatably mounted on the base sleeve, while the closing ring is mounted on the base sleeve or formed einstükkig with the basic sleeve.
  • this construction principle can be reversed, so that the closing ring is rotatably mounted on the base sleeve, while the drive gear is fixedly mounted on the base sleeve.
  • both the drive gear and the closing ring are rotatably mounted on the base sleeve.
  • the locking teeth each have, viewed in the circumferential direction, oblique side edges over which the torque to be transmitted from the safety clutch is transmitted. Due to the oblique side edges, a directed against the action of the spring device axial force is constantly generated on the locking ring. When in the overload state, the effective torque exceeds the predetermined limit torque value, the axial force is so large that it axially displaces the locking ring against the action of the spring means in the direction of the end ring, so that the locking teeth are disengaged.
  • a particularly advantageous embodiment of the invention is that the closing ring and the locking ring each have driving claws that constantly interlock.
  • the closing ring and the locking ring are rotationally fixed to each other in the circumferential direction.
  • the locking ring is displaceable relative to the closing ring.
  • the driving claws can be made stable, so that they reliably transmit the torque, even when the locking ring is in its farthest position from the closing ring.
  • the drive gear is axially supported or supported at least on a side remote from the locking claws side of the basic sleeve.
  • a complex separate storage of the drive gear can be avoided.
  • An axial bearing on the side of the locking claws, however, is not required because the drive gear is constantly supported on this side by the locking ring and the spring device acting behind it.
  • the basic sleeve is an integral part of the drilling or part of a percussion tube.
  • the basic sleeve does not necessarily have to be a separate, additional component. Rather, it is possible to build the drive gear, the end ring and the locking device on an already existing device in the hammer, namely in particular the drilling shaft, the percussion tube or another, arranged in the torque flux wave.
  • a separate base sleeve has the advantage of a particularly simple pre-assembly outside of the hammer.
  • the safety coupling can be completely preassembled and then can be slid rotatably with its base sleeve onto a carrier sleeve.
  • the carrier sleeve may be part of a drilling shaft and / or part of a striking mechanism or striking mechanism tube.
  • the safety coupling according to the invention can be used in any type of impact hammer and / or hammer drill, so that the support sleeve can be used at a suitable location.
  • the Support sleeve provided an axially displaceable switching ring, with which the torque flow from the safety coupling to the support sleeve can be made or interrupt.
  • the switching ring is used to preset different operating states of the hammer, as explained in more detail below.
  • the switching ring is preferably rotatably connected to the support sleeve and has on a front side switching claws, which are assigned opposite, provided on a rear side of the closing ring shift dogs.
  • the switching claws of the switching ring can thus be brought into engagement with the switching claws of the closing ring, so that the torque flow from the closing ring can be transmitted via the switching claws to the switching ring and from there to the carrier sleeve.
  • the switching ring is displaceable at least between a drilling position in which the switching claws of the switching ring are engaged with the switching claws of the closing ring, and a free rotation position in which the switching claws are not engaged.
  • a drilling position it is of course also possible for punches to be exerted on the tool by the impact mechanism provided in the hammer, so that the term "drilling position” also encompasses a “drilling bit position".
  • the free rotation position In the free rotation position, however, no drilling torque is transmitted to the tool. Rather, then the tool can rotate freely relative to the hammer when the operator z. B. pivoted accordingly. Accordingly, the free rotation position is typically used prior to chiseling to bring a chisel blade into a suitable angular rotational position with the hammer housing.
  • the switching ring is displaceable in a fixing position (bit position), in the Fixierklauen, which are attached to the switching ring on a front side opposite the rear side, in opposite, provided on a housing fixing ring Fixierklauen be engaged.
  • bit position in the Fixierklauen
  • the carrier sleeve is thus fixed relative to the housing of the hammer.
  • a rotation of the support sleeve or the drilling shaft and thus of the tool relative to the hammer is then excluded.
  • the fixation position is used by the operator in clean chisel work (without drilling).
  • Fig. 1 to 3 show a safety coupling according to the invention in a sectional or exploded view.
  • a drive gear 21 On a base sleeve 20, a drive gear 21 is arranged, which is supported with its smooth sliding surface 22 against a corresponding collar 23 of the basic sleeve 20.
  • the drive gear 21 is freely rotatable relative to the base sleeve 20 and meshes with a counter-wheel, not shown, from which the drive torque of a drive, also not shown, is initiated.
  • the drive gear 21 On one of the sliding surface 22 opposite end face 24, the drive gear 21 carries a plurality of radially offset Locking claws 25 a locking teeth 26 (see Fig. 2 ).
  • a closing ring 27 z. B. fixed by a press fit.
  • the end ring 27 also attached elsewhere on the base sleeve 20, z. B. bolted or formed integrally with this.
  • an axially displaceable locking ring 28 is arranged, which is pressed axially against the drive gear 21 by a plurality of springs 29 supported against the closing ring 27.
  • the locking ring 28 carries a plurality of axially extending driving claws 30, which engage in corresponding grooves 31 between associated driving claws 32 of the closing ring 27. Accordingly, it is possible that the locking ring 28 is displaced axially by the springs 29 and against the action of the springs 29, wherein always the driving claws 30 of the locking ring 28 with the driving claws 32 of the end ring 27 remain engaged, so that a torque can be transmitted can.
  • the locking ring 28 carries on a drive gear 21 facing end side a plurality of locking claws 33, which form a locking teeth 34.
  • the locking teeth 26 of the drive gear 21 and the locking teeth 34 of the locking ring 28 are formed such that the latching claws 25 and the latching claws 33 at least in a certain relative rotational position of the drive gear 21 and the locking ring 28 can engage with each other.
  • the individual latching claws 25 and 33 can have a different or asymmetrical width in the circumferential direction (angular extensions), so that the latching claws 25, 33 can engage in each other less frequently than would be possible in principle on account of the number of intermediate spaces between the latching claws 25, 33. This avoids rattling of the safety coupling and reduces wear in the event of overload. On the other hand, due to the increased number of locking claws 25, 33 several locking points, so that the torque can be reliably transmitted.
  • the latching claws 25, 33 each have bevelled side edges 35, over which the force or torque flow between the drive gear 21 and the locking ring 28 is guided. Due to their inclination, the side flanks 35 each also generate axial forces, which are a Ausdendrükken of the drive gear 21 and the locking ring 28 effect. Since the drive gear 21 is supported against the collar 23, however, it can not shift axially, but always remains in the desired axial position, in which it meshes with the mating gear, not shown. The locking ring 28, however, is - as shown above - axially displaceable.
  • limit torque When the torque introduced into the drive gear 21 exceeds a predetermined limit value (limit torque), the axial forces caused by the inclined side flanks 35 become so great that the latching ring 28 is pressed against the action of the spring 29 in the direction of the end ring 27. As a result, the latching teeth 26 and 34 are disengaged, so that further transmission of the torque is avoided.
  • the safety clutch is then in overload condition and performs its assigned function of protection of the driveline or the operator holding the hammer with his hands.
  • the locking ring 28 In the overload state, therefore, the locking ring 28 is pressed by the inclined side edges 35 against the end ring 27 such that the locking teeth 26 and 34 are disengaged. However, the springs 29 always push the locking ring 28 back to bring it into engagement with the locking teeth 26 of the drive gear 21. If the torque to be transmitted is still above the limit torque, the locking ring 28 experiences there again an increased axial force, which presses him back against the closing ring 27. Accordingly, the safety clutch will rattle in case of overload until the operator interrupts the operation of the hammer.
  • the springs 29 are to a considerable extent used in bores 36 formed essentially in the driving claws 32 of the closing ring 27.
  • the springs 29 are inserted into corresponding holes in the driving claws 30 of the locking ring 28. This would even allow an increase in the axial width of the locking ring 28, which would improve its axial sliding properties on the base sleeve 20.
  • the in the Fig. 1 to 3 shown safety coupling is a self-contained assembly, which are pre-assembled outside the hammer can. The assembly can then be installed as a single component in a simple and comfortable way in the hammer.
  • Fig. 4, 5 and 6 show the safety coupling in the installed state, that is pushed onto a support sleeve 40th Fig. 4 represents a section.
  • Fig. 5 is one to the cut of Fig. 4 matching side view pictured while Fig. 6 the arrangement in a perspective exploded view shows.
  • the carrier sleeve 40 may be part of a drilling shaft.
  • the carrier sleeve 40 is a percussion tube, in the interior of which a per se known, not shown in the figures Vietnamesefederschertechnik is arranged.
  • Air spring impactors are based on the principle that an axially reciprocating, z. B. on, a crankshaft driven drive piston back and forth drives a percussion piston lying in front of the drive piston via an air spring.
  • the percussion piston in turn transfers its impact energy cyclically to a tool. Since such air spring impact are known in various configurations, a more detailed explanation is unnecessary.
  • the carrier sleeve 40 is formed as a drilling shaft, they can record a full percussion, especially a percussion tube, or even - as in the 4 to 6 shown - the percussion tube or housing form.
  • an axially displaceable switching ring 41 is disposed on the support sleeve 40, which is non-rotatably connected via wedges 42 with the support sleeve 40.
  • the switching ring 41 is used for producing or interrupting the torque flow from the safety coupling to the support sleeve 40.
  • switching claws 43 are provided, which are assigned opposite, arranged on a rear side of the end ring 27 shift dogs 44.
  • the shift dogs 44 are also in the Fig. 1 to 3 good to see.
  • the switching ring 41 assumes a so-called "drilling position" in which the switching claws 43 of the switching ring 41 with the switching claws 44 of the end ring 27 are engaged, so that the introduced via the drive gear 21 torque via the end ring 27, the switching ring 41 and the spline 42 can be transferred to the carrier sleeve 40. From the support sleeve 40, the torque is transmitted in a manner not shown, but known per se to a likewise not shown tool.
  • a fixing ring 45 is provided, which is fixed to a housing, not shown, of the hammer.
  • Fixierklauen 46 are frontally formed, which are assigned to 41 on a back side 47 of the switching ring 41 Fixierklauen 48.
  • the switching ring 41 is accordingly displaceable in a fixation position, also not shown in the figures, in which the fixing claws 48 of the switching ring 41 are in engagement with the fixing claws 46 of the fixing ring 45.
  • the axial displacement of the switching ring 41 is effected by means of an externally accessible by the operator lever 49, the z. B. can also be performed as a rotary switch, in particular in Fig. 6 shown.
  • the rotational position of the shift lever 49 is transmitted via a shift eccentric 50 and a known switching spring 51 on a shift fork 52 which engages in a circumferential groove 53 in the outer region of the switching ring 41.
  • the switching spring 51 it is possible that in particular when z. B. the shift dogs 43 of the switching ring 41 are on the shift dogs 44 of the end ring 27, an axial force is applied to the shift dogs 43 so that they can finally engage 27 in a further relative rotation of the switching ring 41 relative to the end ring.
  • Fig. 7 shows another embodiment of the safety coupling according to the invention in a sectional view.
  • the drive gear 21 is fixedly mounted on the base sleeve 20.
  • the closing ring 27, however, is radially rotatable on the base sleeve 20. It is supported axially against the collar 23, wherein the action of the springs 29 secures the axial position of the end ring 27 against the collar 23.
  • the springs 29 in turn are supported via the locking ring 28 against the drive gear 21 fastened to the base sleeve 20.
  • both the drive gear 21 and the end ring 27 can be freely rotatably mounted on the base sleeve 20, wherein in each case a collar 23, as in the Fig. 1 and 7 shown, must be provided for each of the elements 21, 27.
  • the springs 29 together with the locking ring 28 ensure that both the locking ring 27 and the drive gear 21 are each pressed against its associated collar 23, so that the respective axial position is ensured.
  • the safety clutches shown in the figures each have a base sleeve 20, it is not necessary for the embodiment of the invention to provide such a basic sleeve 20. Rather, it is also possible, the drive gear 21, the closing ring 27 and the locking ring 28 and the springs 29 having locking device without additional base sleeve 20 at a suitable location, for. B. build on the drilling shaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP05758900A 2004-07-15 2005-07-13 Schlag- und/oder bohrhammer mit sicherheitskupplung Not-in-force EP1765556B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004034268A DE102004034268B3 (de) 2004-07-15 2004-07-15 Bohrhammer mit Sicherheitskupplung
PCT/EP2005/007637 WO2006008053A1 (de) 2004-07-15 2005-07-13 Schlag- und/oder bohrhammer mit sicherheitskupplung

Publications (2)

Publication Number Publication Date
EP1765556A1 EP1765556A1 (de) 2007-03-28
EP1765556B1 true EP1765556B1 (de) 2008-07-02

Family

ID=34979665

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05758900A Not-in-force EP1765556B1 (de) 2004-07-15 2005-07-13 Schlag- und/oder bohrhammer mit sicherheitskupplung

Country Status (7)

Country Link
US (1) US20080302548A1 (ja)
EP (1) EP1765556B1 (ja)
JP (1) JP2008506539A (ja)
CN (1) CN100515692C (ja)
DE (2) DE102004034268B3 (ja)
ES (1) ES2306173T3 (ja)
WO (1) WO2006008053A1 (ja)

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CN104500603B (zh) * 2014-12-23 2017-05-17 常州常智汽车部件科技有限公司 一种***咬合式换挡装置及方法
CN104500725B (zh) * 2014-12-23 2017-02-22 常州常智汽车部件科技有限公司 一种双向***咬合式换挡装置
CN105460823B (zh) * 2015-12-10 2018-01-30 中国船舶重工集团公司第七一三研究所 力封闭式反馈型扭矩限制装置
CN106112648B (zh) * 2016-08-22 2019-02-05 南陵旺科知识产权运营有限公司 一种数控机床传动的平衡装置
CN106513795A (zh) * 2016-12-06 2017-03-22 广州峥航机械设备有限公司 一种改进型钻孔机钻头紧固装置
CN106513731B (zh) * 2016-12-06 2018-08-31 上海通外科技发展有限公司 一种新型钻孔机钻头紧固装置
CN106735376B (zh) * 2016-12-06 2018-08-31 台州市黄岩裕盛聚酯模具厂 一种钻孔机钻头紧固装置
CN107489381B (zh) * 2017-09-28 2023-06-06 山西风雷钻具有限公司 防过载螺杆钻具
CN113714787B (zh) * 2020-05-25 2023-03-31 中车唐山机车车辆有限公司 链条紧固装置
CN113183098B (zh) * 2021-04-12 2022-07-29 苏州大可机械有限公司 冲击钻

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Also Published As

Publication number Publication date
ES2306173T3 (es) 2008-11-01
EP1765556A1 (de) 2007-03-28
JP2008506539A (ja) 2008-03-06
WO2006008053A1 (de) 2006-01-26
DE102004034268B3 (de) 2005-12-29
CN1997489A (zh) 2007-07-11
US20080302548A1 (en) 2008-12-11
DE502005004581D1 (de) 2008-08-14
CN100515692C (zh) 2009-07-22

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