EP2560794B1 - Handwerkzeugmaschinenvorrichtung - Google Patents

Handwerkzeugmaschinenvorrichtung Download PDF

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Publication number
EP2560794B1
EP2560794B1 EP11715509.3A EP11715509A EP2560794B1 EP 2560794 B1 EP2560794 B1 EP 2560794B1 EP 11715509 A EP11715509 A EP 11715509A EP 2560794 B1 EP2560794 B1 EP 2560794B1
Authority
EP
European Patent Office
Prior art keywords
damping
power tool
damping means
tool device
hammer tube
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
EP11715509.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2560794A1 (de
Inventor
Willy Braun
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 EP2560794A1 publication Critical patent/EP2560794A1/de
Application granted granted Critical
Publication of EP2560794B1 publication Critical patent/EP2560794B1/de
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
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • 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
    • B25D17/11—Arrangements of noise-damping means
    • 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
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0092—Arrangements for damping of the reaction force by use of counterweights being spring-mounted
    • 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
    • B25D2250/035—Bleeding holes, e.g. in piston guide-sleeves
    • 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
    • B25D2250/131—Idling mode of 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
    • B25D2250/371—Use of springs

Definitions

  • the invention relates to a hand-held power tool device according to the preamble of claim 1.
  • a hand-held power tool device is known from the WO 2008/096788 A1 known.
  • EP 1 992 453 A1 has already been proposed a hand machine tool device, in particular for a drill and / or chipping hammer, with a hammer tube and a B-impact damping system, which has at least one damping means which is intended to damp a kickback energy.
  • the invention relates to a hand tool device according to claim 1 with a hammer tube and a B-shock damping system, which has at least one damping means which is intended to damp a kickback energy.
  • the damping means is arranged in at least one operating state at least partially radially outside the hammer tube.
  • a "hammer tube” is to be understood in particular as meaning a means which is provided for movably supporting a racket in a main working direction.
  • a working air pressure can be built up within the hammer tube in at least one operating state, which accelerates the beater in at least one operating state.
  • racket is to be understood in particular a means that during a striking operation by the working air pressure is accelerated and delivers a shock pulse in the main working direction of an insert tool.
  • a piston generates the working air pressure.
  • main working direction is to be understood in particular a direction in which an operator moves the hammer drill in a working movement provided manner.
  • the main working direction is aligned parallel to a direction of impact of the racket.
  • "Provided” is to be understood in particular to be specially equipped and / or designed.
  • a "B-impact damping system” should be understood to mean a device which is intended to at least partially transmit a recoil energy to a handheld power tool housing.
  • a "recoil energy” is to be understood as meaning an energy that is reflected by the workpiece in the direction of the insertion tool when the insert tool strikes a workpiece.
  • the recoil energy preferably accelerates a striking means of the hand-held power tool device counter to the direction of impact.
  • the B-impact damping system is intended to dampen damped movement caused by the recoil energy of the impact means.
  • the recoil energy is transported by a compressive stress wave.
  • Damping is meant in this context, in particular, that the B-impact damping system reduces an amplitude of a kickback force by friction and / or elastic deformation of the damping means.
  • a “damping means” is to be understood in particular a means which is formed by the recoil energy by at least 10%, advantageously at least 25% of a length deformable in the loading direction.
  • the damping means could by friction convert a portion of the recoil energy into heat energy through a specially formed surface.
  • at least 25%, advantageously at least 50%, particularly advantageously at least 75%, of the recoil energy acts on the damping means during operation.
  • the damping means is at least partially formed by an elastic material, such as an elastomeric material.
  • the damping means could comprise one or more damping, spring, and / or shaping elements.
  • the damping elements could be formed, for example, as thermoplastic elastomers, elastic steel springs, gaseous, viscous and / or solid damping elements.
  • the damping means is formed separately from a counter-pressure spring.
  • the damping means is intended to to dampen the recoil without impact.
  • the term "non-impact” is to be understood in this context, in particular, that the damping means limits a value of its compression in the damping of the recoil energy by a counter by itself.
  • a "counter-pressure spring” should be understood to mean a spring which can be compressed by an operator by pressing the insertion tool against the workpiece by more than 10%, advantageously more than 25% of its length.
  • the hand tool device has a stop which prevents further compression of the counterpressure spring in at least one operating state.
  • the damping element has an at least five times as large, advantageously at least ten times as great spring stiffness as the counterpressure spring.
  • the counter-pressure spring moves in at least one operating state, an idle control means.
  • the damping means damps the return energy of a counter-pressure spring independently and / or in particular parallel to a counter-pressure spring.
  • the damping means damps the kickback energy "independent of a counterpressure spring.”
  • parallel is meant in this context, in particular, that a flyback pulse caused by the recoil energy is conducted via the damping means and then via an element in the direction of a main handle, which is parallel to the counterpressure spring.
  • the term "acting" is to be understood in this context, in particular, that a return pulse that transports the recoil energy generates a force on the damping means, which deforms the damping means.
  • the term "radially outward” is to be understood in particular as meaning that at least one region of the damping means is farther away from a center axis of the hammer tube in the radial direction than an average outer surface of the hammer tube. Due to the inventive design of the power tool device, a particularly short axial length and a particularly effective B-impact damping can be achieved. Furthermore, a low specific load of the damping means can be achieved by a structurally simple possible, large volume. As a result, inexpensive materials for damping can be used.
  • the damping means at least partially surround the hammer tube, whereby a particularly advantageous Utilization of space and an advantageous cooling are possible.
  • the term "enclose” is to be understood in particular that the damping means is disposed at least partially in an axial extension region of the hammer tube radially outside of the hammer tube.
  • the damping means surrounds the hammer tube over an angular range of at least 270 degrees, particularly advantageously 360 degrees.
  • the handheld power tool device has an idling control means which, in at least one operating state, transmits at least part of the kickback energy, whereby a particularly effective kickback damping can be achieved and components can be saved.
  • a low susceptibility to vibration of the idle control can be achieved.
  • the return energy is dissipated via as many components as possible to the power tool housing. At each interface from component to component, recoil energy is dissipated and force peaks are dissipated.
  • An "idle control means" is to be understood in particular as meaning a means intended to close at least one control opening of the hammer tube in at least one operating state.
  • the counter-pressure spring is provided to directly and / or indirectly shift the idle control means to an idle position.
  • a "part of the recoil energy" is to be understood in this context in particular the part of the recoil energy, which is transmitted in an operation of the damping means on the power tool housing.
  • the idle control means is supported in at least one operating state, a portion of the recoil energy in particular directly to the hammer tube and / or on a power tool housing, which structurally simple, an advantageous transmission of the recoil energy is possible.
  • the hammer tube and / or the power tool housing causes a counter force that counteracts a force of the recoil energy.
  • the B-impact damping system has at least two series-connected damping means, whereby structurally simple reliable damping can be achieved with an advantageous spring characteristic.
  • connected in series is meant in particular a part of the return energy acts on at least one first damping means on a second damping means.
  • the B-impact damping system has at least one support element which is arranged between the damping means, whereby unstable deformation behavior, such as, for example, overturning, can be avoided.
  • a "support element” is to be understood in particular an element which is intended to effect a force on the damping means in a direction deviating from a main working direction.
  • the B-impact damping system has at least one bridging means, which is provided to bridge at least one of the damping means.
  • a "bridging means” is to be understood in particular as meaning a region of a component which, in at least one operating state, effects a force transmission in an operative manner parallel to the damping means.
  • the bridging means acts from a certain compression of the damping means.
  • the damping means have different damping properties.
  • the term "different damping properties” is understood to mean a different spring hardness, a different energy absorption upon deformation and / or other properties that appear reasonable to the person skilled in the art. Due to the different damping properties, an advantageous spring characteristic, in particular with a progressive stiffness profile, can be achieved.
  • the hammer tube is movably mounted relative to a portable power tool housing, whereby a particularly low-vibration hand tool machine device is possible, in particular by the hammer tube performs vibration-reducing compensatory movements.
  • the invention proceeds from a handheld power tool having a handheld power tool device, all of which makes sense to the person skilled in the art appearing hand tool machines, such as chisel hammers, screwdrivers, and / or in particular rotary hammers for operation with a hand tool device would be conceivable, whereby a particularly low-vibration, lightweight, compact, cost-effective and durable hand tool can be provided with a particularly small axial length.
  • hand tool machines such as chisel hammers, screwdrivers, and / or in particular rotary hammers for operation with a hand tool device would be conceivable, whereby a particularly low-vibration, lightweight, compact, cost-effective and durable hand tool can be provided with a particularly small axial length.
  • FIG. 1 shows a hand tool 30a with a hand tool device 10a according to the invention, a hand tool housing 22a, a main handle 32a and a tool chuck 34a.
  • the hand tool 30a is designed as a drill and chisel hammer.
  • the handheld power tool device 10a is disposed within the power tool housing 22a, between the main handle 32a and the tool chuck 34a.
  • FIG. 2 shows a detail view of the handheld power tool device 10a.
  • the portable power tool apparatus 10a includes a hammer tube 12a, a B-type shock absorbing system 14a, a hammer 36a, a beater 38a, and a piston 40a.
  • Below the central axis 42a an operating state during a strike is shown.
  • the racket 38a and the piston 40a are movably supported in the hammer tube 12a.
  • the racket 38a is located in the main working direction 44a in front of the piston 40a, between the piston 40a and the striking means 36a.
  • the striking means 36a is disposed between the tool chuck 34a and the racket 38a.
  • the B-impact damping system 14a has a damping means 16a, which is designed as a damping ring.
  • the damping means 16a comprises an elastomeric material.
  • the damping means 16a dampens the recoil energy without impact. That is, the damping means 16a causes, by elastic deformation, a kickback counteracting force limiting the deformation of the damping means 16a. In particular, no stop effectively causes a force parallel to the damping means 16a.
  • the damping means 16a is elastically deformed at a damping.
  • the damping means 16a is arranged completely radially outside of the hammer tube 12a. In this case, the damping means 16a surrounds the hammer tube 12a annularly on a plane perpendicular to the central axis 42nd
  • the B-impact damping system 14a has an idle control means 20a, a guide means 50a, driving pins 52a, a spacer means 54a, a counterpressure spring 56a, a support washer 58a and a locking ring 60a.
  • the guide means 50a encloses a tapered portion 62a of the impact means 36a. It is designed as a guide bush.
  • the guide means 50a is movably mounted on the impact means 36a up to a stop surface 64a of the impact means 36a.
  • the driving bolts 52a are arranged in a form-fitting manner.
  • the driving bolts 52a pass through the hammer tube 12a.
  • On an outer side of the hammer tube 12a the driving bolts 52a engage in the spacing means 54a.
  • the spacer 54a is formed as a sleeve.
  • the spacer 54a encloses the hammer tube 12a.
  • the percussion means 36a transmits a kickback energy via the abutment surface 64a to the guide means 50a.
  • the guide means 50a transmits the kickback energy to the driving pins 52a.
  • the follower bolts 52a direct the kickback energy out of the hammer tube 12a.
  • the driving pins 52a transmit the kickback energy to the spacer means 54a.
  • the spacing means 54a transmits the kickback energy to the damping means 16a.
  • the damping means 16a deforms by the recoil energy and converts a portion of the recoil energy into thermal energy. Part of the recoil energy is transmitted by the damping means 16a to the idle control means 20a. This part has a much lower amplitude of a kickback force than the kickback energy transmitted by the percussion means 36a.
  • the idle control means 20a supports the damping means 16a during impact and thus delivers a portion of the recoil energy to the hammer tube 12a.
  • the locking ring 60a engages in a groove 66a of the hammer tube 12a.
  • the support disk 58a is disposed between the lock ring 60a and the idle control means 20a.
  • the idle control means 20a transmits a part of the kickback energy to the hammer pipe 12a.
  • the idling control means 20a is movably supported for turning on and off the striking operation relative to the hammer pipe 12a.
  • an operator applies the insert tool 46a to the workpiece at the beginning of a work operation presses, it moves the idle control means 20a.
  • the insert tool 46a displaces part of the B-impact damping system 14a against a force of the counter-pressure spring 56a, that is, the B-impact damping system 14a except for the support plate 58a and the locking ring 60a.
  • the idling control means 20a closes a control opening 68a of the hammer tube 12a.
  • FIG. 3 a further embodiment of the invention is shown.
  • the letter a in the reference numerals of the embodiment in the FIGS. 1 and 2 by the letter b in the reference numerals of the embodiment in the FIG. 3 replaced.
  • the following descriptions are essentially limited to the differences between the embodiments, with respect to the same components, features and functions on the description of the other embodiments, in particular in the FIGS. 1 and 2 , can be referenced.
  • FIG. 3 shows a further embodiment of a hand tool device 10b according to the invention.
  • the hand-held power tool device 10b is like the hand-held power tool device of the FIG. 2 in an idle mode and during a beat.
  • the handheld power tool device 10b includes a hammer tube 12b and a B-type shock absorbing system 14b.
  • the B-impact damping system 14b has two series-connected damping means 16b, 17b, a support element 24b and a spacer means 54b. At least one 25% of a recoil energy acts on the damping means 16b, 17b during operation.
  • the damping means 16b, 17b dampens the recoil energy without impact.
  • the damping means 16b, 17b are arranged radially outside of the hammer tube 12b and surround the hammer tube 12b.
  • the support member 24b is disposed between the damping means 16b, 17b.
  • the support member 24b encloses the hammer tube 12b. It is also on the Hammer tube 12b mounted axially movable.
  • the support element 24b has two concave support surfaces 70b, on each of which one of the damping means 16b, 17b rests.
  • the support element 24b has a bridging means 26b.
  • the bridging means 26b is formed as a molding. The bridging means 26b extends in the axial direction along one of the damping means 16b, 17b, more precisely along the damping means 16b, which is arranged facing the spacing means 54b.
  • the damping means 16b When the damping means 16b is compressed by the recoil energy, a distance between the bridging means 26b and an adjacent element, here the spacer means 54b, decreases. At a certain compression of the damping means 16b, the bridging means 26b bridges the damping means 16b, that is, the bridging means 26b prevents further compression of the damping means 16b.
  • the damping means 16b, 17b have different damping properties.
  • the bridgeable damping means 16b has a softer spring characteristic than the other damping means 17b.
  • the support member 24b has a further Anformung 72b, which has a shorter axial length than the bridging means 26b. This Anformung prevents overloading of the damping means 16b, which is arranged facing away from the spacer means 54b.
  • FIG. 4 shows an example of a non-inventive hand tool machine device 10c.
  • the hand-held power tool device 10c like the hand-held power tool device, is made of FIG. 2 , shown in an idle mode and during a strike.
  • the portable power tool apparatus 10c includes a hammer tube 12c, a B-type shock absorbing system 14c, a hammer 36c, a control port shutter 74c, and a support 76c.
  • the B-impact damping system 14c has three series-connected damping means 16c, 17c, 18c, a guide means 50c, a counterpressure spring 56c and two support elements 24c, 78c. On the damping means 16c, 17c, 18c act during operation at least 25% of a recoil energy.
  • the internal damping means 18c is disposed within the hammer tube 12c, effectively between the striking means 36c and the Guide means 50c.
  • the internal damping means 18c could thus also be integrated into the handheld power tool devices of the first two embodiments. Due to the internal damping means 18c, the other external damping means 16c, 17c can advantageously be made small.
  • the outer damping means 16c, 17c have a lower spring hardness than the inner damping means 18c.
  • the outer damping means 16c, 17c are deformable over a greater distance than the inner damping means 18c.
  • the outer damping means 16c, 17c are arranged radially outside the hammer tube 12c. Between the outer damping means 16c, 17c, one of the support elements 24c is arranged. The other support member 78c is disposed between the outer damping means 16c, 17c and the support means 76c. The support members 24c, 78c are fixedly connected to the hammer tube 12c by means of circlips 80c. The outer damping means 16c, 17c and the support members 24c, 78c are biased. When the operator presses a portable power tool 30c with the portable power tool apparatus 10c against a workpiece, the hammer tube 12c abuts on the portable power tool housing 22c of the portable power tool 30c via the B shock absorbing system 14c.
  • a portion of the kickback energy from the percussion means 36c acts on the outboard, axially-centered damping means 16c via the inboard dampening means 18c, a follower pin 52c and a spacer means 54c of the B-type impact damping system 14c.
  • the kickback energy compresses the middle damping means 16c until the follower pin 52c abuts the hammer tube 12c in a recess 82c.
  • the hammer tube 12c is partially formed as a bridging means 28c.
  • a portion of the impact energy acts on the main working direction 44c front outer damping means 17c.
  • the support means 76c supports the front damping means 17c on the hand tool housing 22c.
  • the hammer tube 12c is movably supported relative to a portable power tool housing 22c.
  • a control port locking means 74c is immovably fixed relative to the power tool housing 22c. If an operator When an insertion tool 46c presses against a workpiece at the beginning of a working operation, it moves the hammer tube 12c against a main working direction 44c. For this purpose, the insertion tool 46c displaces a part of the B-impact damping system 14c against a force of the counterpressure spring 56c, that is, the B-impact damping system 14c except for the support means 76c.
  • the support means 76c is fixedly connected to the power tool housing 22c.
  • the control port closing means 74c closes a control port 68c of the hammer tube 12c.
  • a control opening closure means could advantageously be formed with a plain bearing, at least partially in one piece, whereby a component can be saved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Vibration Dampers (AREA)
EP11715509.3A 2010-04-20 2011-04-18 Handwerkzeugmaschinenvorrichtung Active EP2560794B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010027941 2010-04-20
DE102011007433A DE102011007433A1 (de) 2010-04-20 2011-04-14 Handwerkzeugmaschinenvorrichtung
PCT/EP2011/056077 WO2011131597A1 (de) 2010-04-20 2011-04-18 Handwerkzeugmaschinenvorrichtung

Publications (2)

Publication Number Publication Date
EP2560794A1 EP2560794A1 (de) 2013-02-27
EP2560794B1 true EP2560794B1 (de) 2019-11-20

Family

ID=43977934

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11715509.3A Active EP2560794B1 (de) 2010-04-20 2011-04-18 Handwerkzeugmaschinenvorrichtung

Country Status (6)

Country Link
US (1) US9440345B2 (ru)
EP (1) EP2560794B1 (ru)
CN (1) CN102858500B (ru)
DE (1) DE102011007433A1 (ru)
RU (1) RU2572934C2 (ru)
WO (1) WO2011131597A1 (ru)

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EP3501750A1 (de) * 2017-12-19 2019-06-26 Hilti Aktiengesellschaft Vibrationsgedämpfte handwerkzeugmaschine
DE102019208953A1 (de) * 2019-06-19 2020-12-24 Robert Bosch Gmbh Handwerkzeugmaschine mit einem Schlagwerk
RU192262U1 (ru) * 2019-07-11 2019-09-11 Федеральное государственное бюджетное образовательное учреждение высшего образования "Сибирский государственный университет путей сообщения" (СГУПС) Ручной пневматический инструмент с виброзащитой
US20240198505A1 (en) * 2022-12-20 2024-06-20 Milwaukee Electric Tool Corporation Percussion tool

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US9440345B2 (en) 2016-09-13
EP2560794A1 (de) 2013-02-27
DE102011007433A1 (de) 2011-12-08
RU2572934C2 (ru) 2016-01-20
WO2011131597A1 (de) 2011-10-27
RU2012149007A (ru) 2014-05-27
US20130192861A1 (en) 2013-08-01
CN102858500B (zh) 2017-11-07
CN102858500A (zh) 2013-01-02

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