EP1320446A1 - Machine outil comprenant une chambre a lubrifiant et un dispositif de compensation de pression destine a cette chambre - Google Patents

Machine outil comprenant une chambre a lubrifiant et un dispositif de compensation de pression destine a cette chambre

Info

Publication number
EP1320446A1
EP1320446A1 EP01969266A EP01969266A EP1320446A1 EP 1320446 A1 EP1320446 A1 EP 1320446A1 EP 01969266 A EP01969266 A EP 01969266A EP 01969266 A EP01969266 A EP 01969266A EP 1320446 A1 EP1320446 A1 EP 1320446A1
Authority
EP
European Patent Office
Prior art keywords
bearing
machine tool
tool according
pressure compensation
chamber
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
EP01969266A
Other languages
German (de)
English (en)
Other versions
EP1320446B1 (fr
Inventor
Helmut Lebisch
Otto Baumann
Rolf Mueller
Dietmar Saur
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1320446A1 publication Critical patent/EP1320446A1/fr
Application granted granted Critical
Publication of EP1320446B1 publication Critical patent/EP1320446B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/185—Pressure equalising means between sealed chambers

Definitions

  • Machine tool with a room with lubricant and a pressure compensation device of the room
  • the invention relates to a machine tool with a space with lubricant and a pressure compensation device for the space according to the preamble of claim 1.
  • the rotary hammer has a drive motor which is arranged in a motor space of a housing and has a motor shaft which extends through a housing part into a gear space and there engages with a gear for driving a tool holder via a molded pinion.
  • the gearbox is provided with a pressure compensation device which reduces pressure generated in the gearbox during operation to the atmosphere or to the engine compartment.
  • the pressure compensation device has a bore leading from the transmission space to the outside or to the engine compartment and a permanent one rotating driven rotary element in the form of a cover cap, in which a passage is introduced.
  • the invention relates to a machine tool, in particular a hand-held rotary hammer, with a space with lubricant and a pressure compensation device for the space in the area of a bearing of a component that can be driven in rotation.
  • the bearing form at least part of a lubricant seal of the pressure compensation device, via which a pressure in the room can be compensated. Additional components, installation space, weight, installation effort and costs can be saved. This can be achieved in a particularly simple and cost-effective manner with a lubricant seal designed as a gap seal, which is arranged between the bearing and a bearing seat, wherein the gap seal can be arranged between an outer ring and / or between an inner ring of the bearing and a bearing seat.
  • the lubricant seal which can also be used for pressure equalization, is formed by a channel through the bearing, for example from a channel through a cage of a rolling bearing and / or through bearing sealing washers correspondingly attached to the bearing.
  • the bearing seat is advantageously made of aluminum or an aluminum alloy and the bearing is made of steel. If an outer bearing seat is formed from a material with a greater coefficient of thermal expansion than the bearing, as is advantageous with an aluminum bearing seat and a steel bearing, the bearing seat expands more when heated and a gap is formed between the bearing and the bearing seat, which can advantageously be used as a gap seal.
  • an aluminum-steel combination other combinations of materials that appear sensible to a person skilled in the art are also conceivable.
  • the pressure equalization channel can, for example, only have the shape of an axis. m a shaft, m an inner ring of a roller bearing, an outer ring of a roller bearing and / or m a component forming an outer bearing seat, etc.
  • the pressure equalization channel is at least partially formed by a tapered depression, an advantageous labyrinth effect or labyrinth seal can be achieved and, in addition, a recovery effect can be achieved, namely by appropriately coordinating the thread direction and the direction of rotation.
  • the shaped depression can in turn be introduced in the bearing and / or in the bearing seat. If the pressure compensation channel merges into at least one annular groove, it can be produced particularly simply and inexpensively, for example in a turning process, starting from a first annular groove and mouthing in a second annular groove.
  • a filter element is advantageously connected in series to the lubricant seal at least partially formed by the bearing.
  • the sealing effect can be improved while ensuring the pressure equalization function.
  • a felt seal is particularly suitable as a filter element, which is particularly inexpensive to manufacture and has advantageous, preserved properties.
  • the felt can be various fibrous materials which appear to be useful to the person skilled in the art, such as in particular animal hair, vegetable fibers and / or synthetic fibers, etc.
  • the filter element is advantageously fixed in its position by a component fixing a bearing.
  • an advantageously large filter volume can be achieved by branching off at least two radial pressure compensation channels from the bearing, in particular by surrounding the bearing with an annular filter element, and the pressure compensation channels opening radially outward from the bearing on the filter element.
  • the solution according to the invention can be used in all machine tools which appear to be useful to the person skilled in the art, in particular in hand-held machine tools, such as, for example, in grinding machines, saws, milling machines, planes, drilling machines, chisel hammers, etc.
  • FIG. 1 shows a schematically illustrated rotary hammer from the side
  • Fig. 2 shows a section marked with II 3 shows a variant of FIG. 2 with pressure equalization channels running radially outward
  • FIG. 4 shows a variant of FIG. 2 with a curved pressure equalization channel.
  • FIG. 1 shows a schematically illustrated rotary hammer with a housing 104, in which a drive motor 58 is mounted in an engine compartment 56.
  • a tool holder 60 and a drill 62 fastened in the tool holder 60 can be driven in a rotating and impacting manner via a gear arranged in a transmission space 10, not shown in detail.
  • the hammer drill can be guided with two handles 64, 66 which extend essentially perpendicular to an actuation direction, a handle 64 being formed on the housing 104 on a side facing away from the drill 62, and a handle 66 on one of the drill 62 facing side is attached to the housing 104.
  • the drive motor 58 has a drive shaft 68 on which an air wheel 80 is arranged in a rotationally fixed manner in the engine compartment 56 (FIG. 2).
  • the drive shaft 68 protrudes from the engine compartment 56 through an intermediate wall 70 made of aluminum m, the transmission compartment 10 and is rotatably mounted in the intermediate wall 70 in a ball bearing 48.
  • the ball bearing 48 is with its outer ring 72 via a press fit with the intermediate wall 70 and is connected to its inner ring 74 via a press fit with the drive shaft 68.
  • the ball bearing 48 is designed as a fixed bearing, specifically that it is supported axially in the direction of the gear chamber 10 on a shoulder 78 in the intermediate wall 70 and axially in the direction of the engine chamber 56 on a retaining ring 32 fastened in the intermediate wall 70.
  • the gearbox 10 filled with lubricant is sealed in an airtight and lubricant-tight manner on the ball bearing 48 via a sealing washer 76 in the direction of the engine compartment 56.
  • a pinion 82 is formed on an end of the drive shaft 68 protruding into the transmission space 10, by means of which the drive shaft 68 meshes with a gearwheel, not shown, which is arranged in a rotationally fixed manner on an intermediate shaft 20 of the transmission.
  • the intermediate shaft 20 is rotatably mounted in the intermediate wall 70 via a ball bearing 16.
  • the ball bearing 16 is designed as a fixed bearing, namely it is supported axially in the direction of the engine compartment 56 on a shoulder 88 in the intermediate wall 70 and axially in the direction of the transmission space 10 via a holding element (not shown in more detail) fastened in the intermediate wall 70.
  • the ball bearing 16 forms part of a lubricant seal 24 of a pressure compensation device 12, by means of which the pressure in the gear chamber 10 can be compensated or a build-up of pressure in the gear chamber 10 can be reliably avoided by heating during operation of the rotary hammer.
  • the ball bearing 16 is rotatably fixed with its inner ring 84 via a press fit connected to the intermediate shaft 20. Furthermore, the ball bearing 16 with its outer ring 86 made of steel is introduced via a sliding seat m into a bearing seat 28 formed by the intermediate wall 70.
  • the ball bearing 16 and the intermediate wall 70 heat up. Due to their different coefficients of thermal expansion, the intermediate wall 70 made of aluminum expands more than the ball bearing 16 made of steel.
  • a bearing gap between the inner ring 84 and the outer ring 86 of the ball bearing 16 is sealed airtight and lubricant-tight via a sealing ring 90.
  • the latter is connected to the intermediate wall 70 in a rotationally fixed manner by means of a positive connection via the holding element m circumferentially fixing the ball bearing 16 m in the direction of the gear space 10.
  • a filter element 46 m formed by a felt is connected to the gap seal between the outer ring 86 and the intermediate wall 70.
  • the filter element 46 is introduced into a recess 94 of the intermediate wall 70 which surrounds the ball bearing 48 in an annular manner and is held in place by the retaining ring 32 m.
  • a bore 92 is made in the intermediate wall 70 coaxially to the intermediate shaft 20 and covers it in the direction of the engine compartment 56 from the filter element 46 and via which a pressure difference between the gear chamber 10 and the engine compartment 56 can be compensated.
  • FIG. 3 shows a variant of FIG. 2 with a pressure compensation device 14.
  • Components that are essentially the same are basically numbered with the same reference numerals in the exemplary embodiments shown.
  • a drive shaft 22 of a drive motor 58 is mounted in an intermediate wall 106 via a ball bearing 18.
  • the ball bearing 18 forms part of a lubricant seal 26 of the pressure compensation device 14, via which the pressure in a gear chamber 10 can be compensated.
  • the ball bearing 18 is connected with its inner ring 96 in a rotationally fixed manner to the drive shaft 22 via a press fit.
  • the ball bearing 18 with its outer ring 98 made of steel is introduced into a bearing seat 30 formed by the intermediate wall 106 via a sliding seat.
  • a bearing gap between the inner ring 96 and the outer ring 98 of the ball bearing 18 is sealed air and lubricant-tight via a sealing ring 90.
  • a filter element 46 formed by a felt ring is connected in series with the gap seal that is established between the outer ring 98 and the intermediate wall 106.
  • the filter element 46 is introduced into a recess 94 of the intermediate wall 106 which surrounds the ball bearing 18 in an annular manner and is held in position by the retaining ring 32.
  • Extending from the outer ring 98 of the ball bearing 18 are four radial pressure equalization channels 50, 52, which are evenly distributed over the circumference and introduced into the intermediate wall 106 and open radially outward on the filter element 46.
  • An intermediate shaft 20 of a gearbox not shown in detail in the gear box 10 is mounted in the 'partition wall 106 via a ball bearing 100th
  • the intermediate wall 106 is sealed in the area of the ball bearing 100 from the gear space 10 in the direction of the engine space 56.
  • an intermediate shaft 54 is rotatably mounted in a partition wall 70 via a ball bearing 36.
  • the ball bearing 36 forms part of a lubricant seal 38 of a pressure compensation device. device 34, via which the pressure in a gear chamber 10 can be compensated.
  • the ball bearing 36 is arranged with its inner ring 84 in a rotationally fixed manner via a press fit on a bearing seat 40 of the intermediate shaft 54.
  • the ball bearing 36 with its outer ring 86 made of steel is introduced into a bearing seat 102 formed by the intermediate wall 70 via a press fit.
  • a pressure compensation channel 42 formed by a thread-like depression, is introduced into a bearing surface of the bearing seat 40 and opens into an annular groove 44 against a venting direction of the gear chamber 10.
  • the pressure compensation channel 42 forms a labyrinth seal and also has a return flow effect of the lubricant during operation.
  • a bearing gap between the inner ring 84 and the outer ring 86 of the ball bearing 36 is sealed air and lubricant-tight via a sealing ring 90.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Rolling Contact Bearings (AREA)
  • Drilling And Boring (AREA)

Abstract

La présente invention concerne une machine outil, notamment un marteau perforateur manuel, comprenant une chambre (10) à lubrifiant et un dispositif de compensation de pression (12, 14, 34), qui est destiné à la chambre (10) et se trouve dans la zone d'un support (16, 18, 36) pour un composant pouvant être entraîné en rotation (20, 22, 54). Selon cette invention, le support (16, 18, 36) constitue au moins une partie d'un joint à lubrifiant (24, 26, 38) du dispositif de compensation de pression (12, 14, 34), qui permet de compenser une pression dans la chambre (10).
EP01969266A 2000-09-15 2001-08-31 Machine outil comprenant une chambre a lubrifiant et un dispositif de compensation de pression destine a cette chambre Expired - Lifetime EP1320446B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10045618 2000-09-15
DE10045618A DE10045618A1 (de) 2000-09-15 2000-09-15 Werkzeugmaschine mit einem Raum mit Schmiermittel und einer Druckausgleichseinrichtung des Raums
PCT/DE2001/003358 WO2002022315A1 (fr) 2000-09-15 2001-08-31 Machine outil comprenant une chambre a lubrifiant et un dispositif de compensation de pression destine a cette chambre

Publications (2)

Publication Number Publication Date
EP1320446A1 true EP1320446A1 (fr) 2003-06-25
EP1320446B1 EP1320446B1 (fr) 2009-02-11

Family

ID=7656283

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01969266A Expired - Lifetime EP1320446B1 (fr) 2000-09-15 2001-08-31 Machine outil comprenant une chambre a lubrifiant et un dispositif de compensation de pression destine a cette chambre

Country Status (5)

Country Link
US (1) US6722449B2 (fr)
EP (1) EP1320446B1 (fr)
JP (1) JP2004508948A (fr)
DE (2) DE10045618A1 (fr)
WO (1) WO2002022315A1 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7032683B2 (en) 2001-09-17 2006-04-25 Milwaukee Electric Tool Corporation Rotary hammer
US6880223B2 (en) * 2002-04-25 2005-04-19 Milwaukee Electric Tool Corporation Grease slinger
RU2311282C2 (ru) * 2004-11-05 2007-11-27 Хитачи Коки Ко., Лтд. Приводной инструмент с устройством для предотвращения утечки смазочного материала (варианты)
DE602006005101D1 (de) * 2005-06-02 2009-03-26 Makita Corp Kraftwerkzeug
JP4461062B2 (ja) * 2005-06-02 2010-05-12 株式会社マキタ 作業工具
EP1872912B1 (fr) * 2006-07-01 2014-03-19 Black & Decker Inc. Marteau perforateur avec une structure de support d'enclume
DE102006054288A1 (de) * 2006-11-17 2008-05-21 A & M Electric Tools Gmbh Bohrhammer
DE102007050549A1 (de) * 2007-10-23 2009-04-30 Robert Bosch Gmbh Handwerkzeugmaschine
WO2009137808A1 (fr) * 2008-05-09 2009-11-12 Milwaukee Electric Tool Corporation Poignée auxiliaire pour outil à moteur
US9776296B2 (en) 2008-05-09 2017-10-03 Milwaukee Electric Tool Corporation Power tool dust collector
DE102008054978A1 (de) * 2008-12-19 2010-06-24 Robert Bosch Gmbh Elektrohandwerkzeug, insbesondere Bohr- und/oder Schlaghammer
DE102009001657A1 (de) * 2009-03-19 2010-09-23 Robert Bosch Gmbh Handwerkzeugmaschine
CN102476222B (zh) * 2010-11-24 2014-12-10 南京德朔实业有限公司 用于振荡工具上的开孔器
US9486908B2 (en) 2013-06-18 2016-11-08 Ingersoll-Rand Company Rotary impact tool
US11084006B2 (en) 2017-03-23 2021-08-10 Milwaukee Electric Tool Corporation Mud mixer
US11865688B2 (en) * 2021-02-15 2024-01-09 Makita Corporation Impact tool

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US3162268A (en) * 1964-12-22 Lubricator for a motion-translating mechanism
US1956644A (en) * 1930-10-01 1934-05-01 Independent Pneumatic Tool Co Oil regulator for pneumatic tools
US3946490A (en) * 1974-03-27 1976-03-30 Star Dental Manufacturing Co., Inc. Lubrication system for dental handpiece
JPS6043278B2 (ja) * 1977-02-04 1985-09-27 芝浦メカトロニクス株式会社 ハンマドリル
US4403679A (en) * 1981-04-01 1983-09-13 Cooper Industries, Inc. Angle drive lubricator
DE3262635D1 (en) 1981-06-17 1985-04-25 Black & Decker Inc Hand-held power tools including bearing supports for components undergoing linear movement
DE3405922A1 (de) 1984-02-18 1985-08-22 Robert Bosch Gmbh, 7000 Stuttgart Handwerkzeugmaschine, insbesondere bohr- oder schlaghammer
DE8624918U1 (de) * 1986-09-18 1988-01-28 Robert Bosch Gmbh, 7000 Stuttgart Filz-Gleitringdichtung für Handwerkzeugmaschinen
DE4026946A1 (de) * 1990-08-25 1992-02-27 Bosch Gmbh Robert Bohr- und/oder schlaghammer
DE4038623A1 (de) 1990-12-04 1992-06-11 Bosch Gmbh Robert Handwerkzeugmaschine
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Also Published As

Publication number Publication date
JP2004508948A (ja) 2004-03-25
EP1320446B1 (fr) 2009-02-11
DE50114703D1 (de) 2009-03-26
US6722449B2 (en) 2004-04-20
DE10045618A1 (de) 2002-04-04
WO2002022315A1 (fr) 2002-03-21
US20030121683A1 (en) 2003-07-03

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