EP2560794A1 - Dispositif pour machine-outil portative - Google Patents

Dispositif pour machine-outil portative

Info

Publication number
EP2560794A1
EP2560794A1 EP11715509A EP11715509A EP2560794A1 EP 2560794 A1 EP2560794 A1 EP 2560794A1 EP 11715509 A EP11715509 A EP 11715509A EP 11715509 A EP11715509 A EP 11715509A EP 2560794 A1 EP2560794 A1 EP 2560794A1
Authority
EP
European Patent Office
Prior art keywords
damping
damping means
hammer tube
tool device
impact
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
EP11715509A
Other languages
German (de)
English (en)
Other versions
EP2560794B1 (fr
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/fr
Application granted granted Critical
Publication of EP2560794B1 publication Critical patent/EP2560794B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • B25D17/24—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 is based on a handheld power tool device according to the preamble of claim 1.
  • a hand-held power tool device in particular for a rotary 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 recoil energy.
  • the invention is based on a hand-held power tool device with a hammer tube and a B-impact damping system which has at least one damping means which is intended to damp a recoil energy.
  • the damping means is arranged at least partially radially outside the hammer tube in at least one operating state.
  • a "hammer tube” is to be understood as meaning in particular a means which is intended to movably support 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 racket in at least one operating state.
  • racket is to be understood in particular as meaning a means which, during an impact operation, is controlled by the weapon. beits Kunststoffbuch is accelerated and emits 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 as meaning a direction in which an operator moves the rotary hammer in a movement intended for a working movement
  • the main working direction is aligned parallel to a direction of impact of the racket. or understood to be understood.
  • a "B-impact damping system” is to be understood as a device which is intended to at least partially transmit a recoil energy to a handheld power tool housing is reflected from the workpiece in the direction of the insert tool.
  • the recoil energy accelerates a percussion means of the craft machine device against the direction of impact.
  • B-shock damping system intended to dampen the movement caused by the recoil energy of the impact means attenuated.
  • the recoil energy is transported by a compressive stress wave.
  • "damping" is to be understood in particular as meaning that the B-impact damping system has an amplitude of a kickback force
  • a “damping means” is to be understood in particular as meaning a means which is formed by the recoil energy deformable by at least 10%, advantageously at least 25% of a length in the direction of loading Alternatively or additionally, the damping means could by friction form a part through a specially designed surface In particular, at least 25%, advantageously at least 50%, more preferably at least 75% of the recoil energy acts on the damping means during operation and / or additionally, the damping means could comprise one or more damping, spring, and / or shaping elements
  • the damping elements could be, for example, thermoplastic elastomers, elastic steel springs, gaseous, viscous and / or solid damping be formed.
  • 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 to mean that the damping means limits a value of its compression in the damping of the recoil energy by a counter-self.
  • a "counter-pressure spring” should be understood to mean a spring that is pressed by an operator of the insert tool to the workpiece by more than 10%, advantageously more than 25% of its length is compressible.
  • 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 to be understood in particular as meaning that a kickback pulse caused by the kickback energy is transmitted via the damping means and then via an element in the direction a main handle is located, which is parallel to the counter-pressure spring.
  • the term "acting" is to be understood in particular as meaning that a return pulse which transports the recoil energy generates a force on the damping means which deforms the damping means Area of the damping means in the radial direction is further away from a central axis of the hammer tube, as an average outer surface of the hammer tube.
  • the damping means at least partially surround the hammer tube, whereby a particularly Advantageous utilization of space and an advantageous cooling are possible.
  • the damping means is arranged at least partially radially outwardly of the hammer tube in an axial extension region 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 transmits at least part of the kickback energy in at least one operating state, whereby a particularly effective return shock 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 counterpressure spring is provided to directly and / or indirectly shift the idle control means to an idling position one
  • part of the recoil energy is to be understood as meaning, in particular, the part of the recoil energy which is transmitted from the damping means to the handheld power tool housing during operation
  • Operating state supports part of the recoil energy, in particular directly on the hammer tube and / or on a power tool housing, whereby structurally simple an advantageous transmission of the recoil energy is possible.
  • 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 as meaning, in particular, a region of a component which, in at least one operating state, brings about a force transmission in parallel to the damping means
  • the bridging means acts from a certain compression of the damping means
  • damping means have different damping properties.
  • damping properties should be understood as meaning a different spring hardness, a different energy absorption upon deformation and / or other properties deemed appropriate by the person skilled in the art.
  • the hammer tube is movably mounted relative to a machine tool housing, whereby a particularly low-vibration hand tool machine device is possible, in particular by the hammer tube executing vibration-reducing compensatory movements.
  • the invention proceeds from a hand-held power tool with a hand-held power tool device, wherein all, to those skilled in mind fully-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 with a particularly small axial length can be provided.
  • hand tool machines such as chisel hammers, screwdrivers, and / or in particular rotary hammers for operation with a hand tool device
  • FIG. 1 shows a hand tool with a hand tool device according to the invention
  • FIG. 2 shows a first exemplary embodiment of the handheld power tool device from FIG. 1 with a damping means
  • Fig. 3 shows a second embodiment of the hand tool device of Figure 1 with a plurality of damping means
  • FIG. 4 shows a third exemplary embodiment of the hand-held power tool device from FIG. 1 with a movably mounted hammer tube.
  • FIG. 1 shows a handheld power tool 30a with a handheld power tool device 10a according to the invention, a handheld power 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 detailed view of the handheld power tool device 10a.
  • the hand-held power tool device 10a has a hammer tube 12a, a B-impact damping system 14a, a hammer 36a, a beater 38a and a piston 40a.
  • Above a central axis 42a of the hammer tube 12a an idling operating state is shown in FIG.
  • 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 region 62a of the impact agent 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.
  • 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 to the guide means 50a via the abutment surface 64a.
  • 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 spacer means 54a transmits the flyback 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.
  • FIGS. 3 and 4 show two further exemplary embodiments of the invention.
  • the letter a in the reference numerals of the embodiment in Figures 1 and 2 is replaced by the letters b and c in the reference numerals of the embodiments in Figures 3 and 4.
  • the following descriptions are essentially limited to the differences between the exemplary embodiments, reference being made to the description of the other exemplary embodiments, in particular FIGS. 1 and 2, with regard to components, features and functions remaining the same.
  • FIG. 3 shows a further exemplary embodiment of a handheld power tool device 10b according to the invention.
  • the handheld power tool device 10b like the handheld power tool device of FIG. 2, is shown in an idle mode and during a strike.
  • 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.
  • a distance between the bridging means 26b and an adjacent element, here the spacer means 54b decreases.
  • 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 a further exemplary embodiment of a handheld power tool device 10c according to the invention.
  • the handheld power tool device 10c like the handheld power tool device of FIG. 2, is shown in an idle mode and during a strike.
  • the handheld power tool device 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.
  • the other external damping means 16c, 17c can advantageously be dimensioned 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.
  • one of the support elements 24c is arranged between the outer damping means 16c, 17c.
  • 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.
  • a portion of the kickback energy from the percussion means 36c via the internal damping means 18c, a driving pin 52c and a spacing means 54c of the B-impact damping system 14c acts on the outboard axial center damping means 16c.
  • 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.
  • Supporting 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 closing means 74c is relative to
  • Hand tool housing 22c fixed immovably. If an operator When an insert tool 46c presses against a workpiece at the beginning of a work operation, it moves the hammer tube 12c against a main working direction 44c. For this purpose, the insert tool 46c shifts a part of the B-impact damping system 14c against a force of the counter-pressure spring 56c, that is, the B-impact damping system 14c except for the support means 76c.
  • Supporting 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.
  • the counter-pressure spring 56c shifts the hammer tube 12c in the main working direction 44c.
  • the control port closing means 74c releases the control port 68c.
  • 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.

Landscapes

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

Abstract

L'invention concerne un dispositif pour machine-outil portative, comprenant un tube de marteau (12a; 12b; 12c) et un système d'amortissement des coups en mode perçage (14a; 14b; 4c) qui présente au moins un moyen d'amortissement (16a; 16b; 16c) destiné à amortir l'énergie de contrecoup. L'invention est caractérisée en ce que le moyen d'amortissement (16a; 16b; 16c) est disposé, dans au moins un état de fonctionnement, au moins partiellement radialement à l'extérieur du tube de marteau (12a; 12b; 12c).
EP11715509.3A 2010-04-20 2011-04-18 Dispositif pour machine-outil portative Active EP2560794B1 (fr)

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 (fr) 2010-04-20 2011-04-18 Dispositif pour machine-outil portative

Publications (2)

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

Family

ID=43977934

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11715509.3A Active EP2560794B1 (fr) 2010-04-20 2011-04-18 Dispositif pour machine-outil portative

Country Status (6)

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

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DE102023210544A1 (de) * 2023-10-25 2025-04-30 Robert Bosch Gesellschaft mit beschränkter Haftung Handwerkzeugmaschine mit einer Schlagwerkeinheit
DE102024202092A1 (de) 2024-03-06 2025-09-11 Robert Bosch Gesellschaft mit beschränkter Haftung Handwerkzeugmaschine mit einer Schlagwerkeinheit und einem Dämpfungselement

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Also Published As

Publication number Publication date
WO2011131597A1 (fr) 2011-10-27
US9440345B2 (en) 2016-09-13
US20130192861A1 (en) 2013-08-01
DE102011007433A1 (de) 2011-12-08
RU2572934C2 (ru) 2016-01-20
CN102858500B (zh) 2017-11-07
EP2560794B1 (fr) 2019-11-20
RU2012149007A (ru) 2014-05-27
CN102858500A (zh) 2013-01-02

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