EP2797721A1 - Système d'outil portatif - Google Patents

Système d'outil portatif

Info

Publication number
EP2797721A1
EP2797721A1 EP12810244.9A EP12810244A EP2797721A1 EP 2797721 A1 EP2797721 A1 EP 2797721A1 EP 12810244 A EP12810244 A EP 12810244A EP 2797721 A1 EP2797721 A1 EP 2797721A1
Authority
EP
European Patent Office
Prior art keywords
hand tool
racket
planetary gear
percussion
spindle
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
EP12810244.9A
Other languages
German (de)
English (en)
Other versions
EP2797721B1 (fr
Inventor
Tobias Herr
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
Priority to EP21162272.5A priority Critical patent/EP3881974A1/fr
Publication of EP2797721A1 publication Critical patent/EP2797721A1/fr
Application granted granted Critical
Publication of EP2797721B1 publication Critical patent/EP2797721B1/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
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/08—Means for driving the impulse member comprising a worm mechanism, i.e. a continuous guide surface with steadily rising and falling incline
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • 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
    • B25D2211/006—Parallel drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0015—Anvils
    • 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
    • B25D2250/231—Sleeve details
    • 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

  • EP 1 690 642 A1 a hand tool device with a percussion mechanism which has at least one racket and a cam guide which drives the racket at least in a percussion drilling operation.
  • the invention relates to a hand tool device with a percussion mechanism, which has at least one racket and a cam guide which drives the racket at least in a percussion drilling operation.
  • the racket has at least part of the curve guide.
  • a "percussion mechanism” is to be understood in particular as meaning a device which is intended to generate a shock impulse and in particular to dispense in the direction of an insertion tool
  • the impact mechanism advantageously guides the impact impulse, at least during a percussion drilling operation, via a tool spindle and / or in particular via a tool chuck
  • the percussion mechanism is intended to translate a rotational movement into a particularly translational striking movement.
  • “Provided” is to be understood in particular to be specially designed and / or equipped.
  • the term "bat” is to be understood as meaning a means which is accelerated, in particular translationally, at a percussion drilling operation and emits a pulse received during the acceleration as impact pulse in the direction of the insertion tool
  • the bat is preferably made in one piece - be formed.
  • a "curve guide” is to be understood as a device which translates a rotational energy into a stroke generation, at least by means of a specially shaped guide surface along which a connecting means runs, at least in a percussion drilling operation, into a linear kinetic energy of the striker
  • the specially shaped surface is a surface that limits a guide curve of the curve guide.
  • Connecting means is to be understood in particular as meaning a mechanical coupling between at least one a Schlagbohr nowadays rotating part moving the impact mechanism, in particular a
  • a "guide curve” is to be understood as a region delimited by the guide surface in which the connection means runs in at least one operating state.
  • a “percussion spring” is to be understood in particular as a spring which stores at least part of a striking energy in at least one operating state.
  • the term "support” is to be understood as meaning that a part of the percussion spring is arranged immovably relative to the racket or a part of the percussion spring relative to a hand tool housing
  • the percussion spring is designed as a spring which appears expedient to the person skilled in the art, but preferably as a spring
  • the term “drive” is to be understood to mean, in particular, that the curve guide transmits energy for producing beats to the racket.
  • the racket has at least part of the curve guide
  • the racket has a surface to which the connecting means directly transmits the energy to generate the striking motion
  • the portion of the cam guide which the racket comprises comprises an area-limited mounting recess which secures the connecting means in place relative to the racket the racket is intended to fasten a connecting means which, during operation, connects the part of the curve guide and a further part of the curve guide, in particular the guide curve
  • the connecting means and the racket are connected unsprung, that is to say that between the connection medium and the club is effectively no spring arranged.
  • the connecting means could be at least partially formed integrally with the racket.
  • the racket has to be formed as a guide curve.
  • "stationary" is to be understood as meaning that an axis of symmetry and / or a center of the connecting means relative to the racket is at least substantially stationary during a hammering operation.
  • the cam guide has a hammer-free range, whereby a large impact energy and an advantageously low wear can be achieved with a short length.
  • a "hammer-free range” should be understood to mean, in particular, a region of the guide curve of the cam guide in which the connecting means is arranged when the percussion spring accelerates the striker in the direction of impact
  • the impact-free region is so wide that the connecting means can pass through the impact-free region on different tracks
  • the impact-free region does not exert any force on the beater, at least during the impact-drilling operation.
  • the curve guide has a percussion-wound area, whereby an advantageous operation, in particular with low vibrations, can be achieved the guide curve of the cam guide are understood, which moves the racket at least during a percussion drilling operation in particular relative to the hand tool housing against the direction of impact.
  • the movement of the racket caused by the impact lift area compresses the percussion spring counter to the direction of impact.
  • the guide surface of the impact lift region has a pitch relative to the direction of impact between 5 degrees and 35 degrees, advantageously between 10 degrees and 25 degrees.
  • the cam guide has a mounting recess, whereby an advantageous installation and a particularly small configuration are possible.
  • a “mounting recess” is to be understood, in particular, as a region limited by the striking mechanism spindle and / or the racket, by means of which the connection means is introduced into the guide curve during assembly.
  • the percussion mechanism comprise a percussion spindle, which has at least a portion of the cam guide, whereby a compact design can be achieved.
  • a “percussion spindle” is to be understood in particular as meaning a shaft which transmits a rotational movement from a planetary gear of the hand tool device to the cam guide
  • the percussion spindle has a guide curve of the cam guide, whereby a simple production is possible.
  • the percussion spindle could have a fastening recess for fastening the connecting means that is stationary relative to the percussion spindle and / or at least partially formed integrally with the connecting means.
  • the racket at least substantially encloses the percussion spindle on at least one plane, whereby a configuration with low volume and weight is possible.
  • the phrase "at least substantially encloses at least one level" is intended to mean that beams emanating from an axis of the percussion spindle and arranged on the plane intersect the racket over an angular range of at least 180 degrees, advantageously at least 270 degrees.
  • the club encloses the percussion spindle by 360 degrees.
  • the percussion mechanism has a connection means which, in at least one operating state, transmits a movement in particular from the percussion spindle to the racket, whereby low wear, effective production and easy assembly can be achieved.
  • the hand tool device comprises a tool spindle which at least substantially encloses the racket on at least one plane.
  • a "tool spindle” is to be understood as meaning in particular a shaft which transmits a rotational movement from the planetary gear to the tool chuck,
  • the tool spindle is designed as a solid shaft
  • the tool spindle could be designed as a hollow shaft.
  • the tool spindle is arranged at least substantially coaxially to the percussion spindle, whereby a particularly compact design is possible.
  • the phrase "at least substantially coaxially arranged” is to be understood as meaning that an axis of rotation of the tool spindle and an axis of rotation of the percussion spindle are spaced apart from one another by at least one point less than 20 mm, advantageously less than 10 mm, and an orientation difference of less than 15 degrees, advantageously less than 5 degrees, to one another, particularly preferably, the axis of rotation of the tool spindle and the axis of rotation of the percussion spindle are arranged on the same straight line and aligned identically.
  • the hammer mechanism has a racket guide which rotatably supports the racket, whereby a structurally simple curve guidance is possible.
  • a “club guide” is to be understood in particular as meaning a device which movably supports the racket parallel to the direction of impact.
  • the term” rotatably support should be understood to mean that the racket guide in particular counteracts any rotary movement of the racket relative to a hand tool housing.
  • the hand tool device comprises a hand tool housing, wherein the impact mechanism has a percussion spring, which is supported on the racket and on the hand tool housing, whereby a particularly small axial length can be achieved.
  • a "hand tool housing” is to be understood as a housing which has an interior in which at least the percussion mechanism, the planetary gear and a drive unit of the
  • Hand tool housing are arranged.
  • the hand tool housing connects at least the striking mechanism, the planetary gear and a drive unit of the hand tool housing at least partially with each other.
  • the impact mechanism has the first cam guide and a second cam guide, whereby a low wear and a high degree of smoothness are possible.
  • the invention is based on a hand tool with a hand tool device according to the invention.
  • the hand tool is for this purpose seen driving the insert tool in a screwing mode, in a drilling mode, in a ringbohrmodus and in particular in a chisel mode.
  • FIG. 1 shows a section of a hand tool with a hand tool device according to the invention
  • FIG. 2 shows a partially cutaway section through a percussion mechanism and a planetary gear of the hand-held power tool device from FIG. 1,
  • FIG. 3 shows a first sectional area A of the percussion mechanism of the hand-held power tool device from FIG. 1,
  • FIG. 4 shows a second sectional area B of the impact mechanism of the hand tool device from FIG. 1,
  • FIG. 5 is a perspective view of a percussion spindle of the percussion mechanism of the hand tool device of Figure 1,
  • Fig. 6 is a perspective view of a racket of the striking mechanism of
  • Fig. 7 is a sectional area C of a first planetary gear stage and a first
  • FIG. 8 shows a sectional area D of a control element and a second impact shut-off device of the hand-held power tool device from FIG. 1, FIG.
  • FIG. 9 is a perspective sectional view of a part of the hand tool device of Figure 1,
  • FIG. 10 is a sectional view E of a spindle locking device of the hand tool device of FIG. 1, FIG. 1 1 shows a sectional area F by blocking means of the spindle locking device of the hand tool device from FIG. 1, FIG.
  • FIG. 13 shows a sectional area H of a third planetary gear stage of the hand tool device of FIG. 1, FIG.
  • FIG. 14 shows a sectional area I of a fourth planetary gear stage of the hand tool device from FIG. 1,
  • FIG. 15 is a schematic representation of an operating device and a protective device of the hand tool device of Figure 1,
  • FIG. 17 shows a further exemplary embodiment of a first impact shut-off device of a hand tool device according to the invention
  • Fig. 18 shows an alternative embodiment of a striking spring of a hand tool device according to the invention.
  • FIG. 1 shows a hand tool 10a.
  • the hand tool 10a is designed as a percussion drill.
  • the hand tool 10a has a hand tool device 12a according to the invention, a hand tool housing 14a and a battery interface 16a.
  • the battery interface 16a is provided to supply the hand tool device 12a from a hand tool battery not shown here with an electrical energy.
  • the hand tool housing 14a is pistol shaped.
  • the hand tool housing 14a is formed in several parts. It comprises a handle 18a, by means of which an operator holds the hand tool 10a in one operation.
  • the hand tool device 12a comprises a tool guide unit 20a, a striking mechanism 22a, a first impact shut-off device 24a, a second impact shut-off device 26a, a planetary gear 28a, a drive unit 30a, an operating device 32a and a torque limiting unit 34a.
  • the tool guide unit 20a comprises a tool chuck 36a and a tool spindle 38a.
  • the tool chuck 36a fastens during operation a not shown here insert tool, such as a drill or a screw bit.
  • the tool chuck 36a secures the insert tool frictionally.
  • the tool chuck 36a has three jaws movably mounted by an operator, which secure the insert tool in one operation.
  • the tool chuck 36a fixes the insert tool axially immovably with respect to the tool chuck 36a and in particular the tool spindle 38a in one operation.
  • a part of the tool chuck 36a and the tool spindle 38a are immovably connected with each other relative to each other.
  • the tool chuck 36a and the tool spindle 38a are screwed together.
  • the hand tool device 12a has a bearing means 40a, which supports the tool spindle 38a on a side facing the tool chuck 36a.
  • the bearing means 40a supports the tool spindle 38a axially displaceable.
  • the bearing means 40a is axially fixedly connected to the tool spindle 38a.
  • the bearing means 40a is axially movably mounted in the hand tool housing 14a.
  • the hand tool device 12a has a further bearing means 41a which supports the tool spindle 38a on a side facing the planetary gear 28a.
  • the bearing means 41 a is designed as a rolling bearing, here as a needle bearing, whereby a low-backlash storage is possible.
  • the bearing means 41 a supports the tool spindle 38a axially displaceable.
  • a percussion spindle 46a encloses the bearing means 41 a.
  • the bearing means 41 a is operatively disposed between the tool spindle 38a and the percussion spindle 46a.
  • the tool spindle 38a comprises a striking surface 42a on which a beater 44a of the percussion mechanism 22a strikes during a percussion drilling operation.
  • the racket 44a has a mass which is at most two thirds as large as a mass of the tool guide unit 20a.
  • the mass of the racket 44a is less than half the mass of the tool guide unit 20a.
  • the mass of the racket 44a is about 45% of the mass of the tool guide unit 20a.
  • the percussion mechanism 22a includes the racket 44a, the percussion spindle 46a, a percussion spring 48a, a percussion drive device 50a, and a racket guide 52a.
  • the racket 44a is mounted translationally movable in the direction of impact 54a.
  • the direction of impact 54a is aligned parallel to an axial direction of the percussion spindle 46a.
  • FIGS. 3 and 4 show a sectional area A and a sectional area B of the striking mechanism 22a.
  • the racket guide 52a rotatably supports the racket 44a relative to the hand tool housing 14a.
  • the racket guide 52a has three guide bars 56a on which the racket 44a slides.
  • the guide bars 56a are regularly arranged around the racket 44a.
  • the racket 44a has sliding surfaces 58a which enclose the guide bars 56a by 180 degrees on a plane perpendicular to the direction of impact 54a.
  • the racket 44a encloses the percussion spindle 46a on a plane perpendicular to the direction of impact 54a by 360 degrees.
  • the racket 44a encloses the tool spindle 38a on the level by 360 degrees.
  • the percussion spindle 46a on the plane encloses the tool spindle 38a by 360 degrees.
  • the percussion spindle 46a is arranged coaxially with the tool spindle 38a.
  • the percussion spring 48a accelerates the club 44a before a strike in the direction of impact 54a.
  • the hand tool housing 14a supports the percussion spring 48a on a side facing away from the racket 44a.
  • the percussion spring 48a presses directly against the racket 44a.
  • the racket 44a has a spring attachment 60a.
  • the spring attachment 60a is formed as an annular recess.
  • FIG. 5 shows the percussion spindle 46a in a perspective view.
  • Figure 6 shows the racket
  • the racket drive device 50a has a first cam track 62a and a second first cam track 64a.
  • the cam guides 62a, 64a each include a guide cam 66a, 68a and a connecting means 70a, 72a.
  • the connecting means 70a, 72a are spherical.
  • the racket 44a stores the connecting means 70a, 72a stationary relative to the racket 44a.
  • the racket 44a has hemispherical mounting recesses 74a.
  • the connecting means 70a, 72a slide in a percussion drilling operation in the guide curve 66a, 68a.
  • the percussion spindle 46a has a part of the cam guides 62a, 64a, namely the guide cam 66a, 68a.
  • the percussion spindle 46a defines a space in which the connecting means 70a, 72a move in a percussion drilling operation.
  • the percussion spindle 46a is formed as a hollow shaft.
  • the planetary gear 28a drives the hammer spindle 46a.
  • the striking mechanism spindle 46a has a toothing 76a on a side facing away from the tool chuck 36a.
  • the guide curves 66a, 68a each have a hammer-free region 78a, 80a, a Impact winding area 82a, 84a and a mounting recess 86a, 88a on.
  • the connecting means 70a, 72a are inserted through the mounting recesses 86a, 88a in the mounting recesses 74a of the racket 44a.
  • Impact spindle 46a rotates clockwise in percussion drilling operation in direction of impact 54a.
  • the impact winding areas 82a, 84a are formed spirally. They extend through 180 degrees about an axis of rotation 90a of the striking mechanism spindle 46a.
  • the impact winding areas 82a, 84a move the connecting means 70a, 72a and thus the racket 44a in the impact drilling operation against the direction of impact 54a.
  • the percussion mechanism 22a has the connecting means 70a, 72a, which in at least one operating state transmit movement from the percussion spindle 46a to the racket 44a.
  • the hammer-free areas 78a, 80a each connect two ends 92a, 94a, 96a, 98a of the impact-winding areas 82a, 84a.
  • the hammer-free areas 78a, 80a extend through 180 degrees about a rotation axis 90a of the hammer spindle 46a.
  • the hammer-free areas 78a, 80a each have a striking flank 100a, 102a which, proceeding from an end 94a, 96a of the impact-winding area 82a facing the planetary gear 28a, runs approximately parallel to the direction of impact 54a.
  • the percussion spring 48a accelerates the striker 44a and the connecting means 70a, 72a in the direction of impact 54a.
  • the connecting means 70a, 72a move through the hammer-free areas 78a, 80a, without experiencing an axial force, until the racket 44a hits the striking surface 42a.
  • the cam guides 62a, 64a are arranged offset by 180 degrees about the rotation axis 90a.
  • the cam guides 62a, 64a are arranged one behind the other in the axial direction.
  • the planetary gear 28a has the first planetary gear stage 104a, a second planetary gear stage 106a, a third planetary gear stage 108a and a fourth planetary gear stage 1 10a.
  • FIG. 7 shows a sectional area C of the first planetary gear stage 104a.
  • the gears of the planetary gear stages 104a, 106a, 108a, 110a have gears with a number of teeth that appears appropriate to the person skilled in the art.
  • the gears of the planetary gear stages 104a, 106a, 108a, 10a are engaged with each other, which is not shown here in part.
  • the first planetary gear stage 104a increases a first rotational speed of the second planetary gear stage 106a for driving the hammer mechanism 22a.
  • the second planetary gear stage 106a drives at this first rotational speed the tool spindle 38a.
  • the toothing 76a of the percussion spindle 46a forms a sun gear of the first planetary gear stage 104a.
  • the toothing 76a meshes with planet wheels 1 12a of the first planetary gear stage 104a, which are guided by a planet carrier 1 14a of the first planetary gear stage 104a.
  • a ring gear 1 16a of the first planetary gear stage 104a meshes with the planetary gears 1 12a of the first
  • the first impact shut-off device 24a fixed in a percussion drilling the ring gear 1 16a of the first planetary gear stage 104a relative to the hand tool housing 14a immovable.
  • the first impact shut-off device 24a is provided to turn on the racket driving device 50a in a first right-handed rotational direction of rotation and to automatically disengage the racket drive device 50a in a second, counterclockwise rotational direction.
  • the first Schlagabschaltvorides 24a acts on the ring gear 1 16a of the first planetary gear stage 104a.
  • the first impact shut-off device 24a blocks the ring gear 16a of the first one
  • the first impact shut-off device 24a releases the ring gear 16a of the first planetary gear stage 104a in the second, counterclockwise rotary drilling direction so that it can rotate.
  • the first impact shut-off device 24a has three clamping mechanisms 122a.
  • the clamping mechanisms 122a each include a blocking means
  • the blocking means 124a is formed as a roller.
  • the first clamping surface 126a forms an outer region of a surface of the ring gear 1 16a of the first planetary gear stage 104a.
  • the second clamping surface 128a is arranged immovable relative to the hand tool housing 14a.
  • the blocking means 124a clamp between the first clamping surfaces 126a and the second clamping surface 128a.
  • the freewheel surfaces 130a guide the blocking means 124a and prevent jamming.
  • FIG. 7 shows a connection means 1 18a which rotatably connects the tool spindle 38a and a planet carrier 120a of the second planetary gear stage 106a.
  • the connecting means 1 18a connects the tool spindle 38a and the planet carrier 120a of the second planetary gear stage 106a in this case axially displaceable.
  • FIGS. 3, 4 and 7 show three first transmission means 132a of the second impact shut-off device 26a.
  • the transmission means 132a are formed as rods.
  • FIG. 8 shows a sectional area D through a control element 134a of the hand-held power tool device 12a.
  • Figure 9 shows the second Schlagabschaltvoretti devis 26a in a perspective sectional view.
  • the control member 134a supports the tool guide unit 20a in a screwing mode shown in FIGS. 1, 8, and 9, and in a drilling mode in a direction opposite to the striking direction 54a.
  • a force applied to the tool guide unit 20a acts on support surfaces 138a of the control element 134a via the bearing means 40a, a second transmission means 136a of the second impact shut-off device 26a and the first transmission means 132a.
  • the control element 134a has three recesses 140a. In a percussion drilling mode shown in FIG. 2, the first transmission means 132a can be inserted into the recesses 140a, whereby the tool guidance unit 20a is axially movable.
  • the second impact shut-off device 26a has a strike cut-off clutch 142a.
  • the Schlagabschaltkupplung 142 a is partially formed integrally with the planetary gear 28 a.
  • the impact shut-off clutch 142a is disposed between the first planetary gear stage 104a and the second planetary gear stage 106a.
  • the Schlagabschaltkupplung 142 a has a first coupling element 144 a, which is non-rotatably connected to a planet carrier 1 14 a of the first planetary gear stage 104 a.
  • the Schlagabschaltkupplung 142 a has a second coupling element 146 a, which is rotatably connected to a planet carrier 120 a of the second planetary gear stage 106 a.
  • the impact shut-off clutch 142a is opened.
  • the tool spindle 38a transmits an axial coupling force to the impact shut-off clutch 142a when the operator presses an insertion tool against a workpiece.
  • the coupling force closes the impact shut-off clutch 142a.
  • the Schlagabschaltkupplung 142 a is shown closed.
  • a striking switch spring 148a of the hand tool device 12a opens the strike cutout clutch 142a.
  • the planet carrier 120a of the second planetary gear stage 106a is formed in two parts.
  • a first part 150a of the planet carrier 120a of the second planetary gear stage 106a is non-rotatably connected to the tool spindle 38a.
  • Planet carrier 120a is axially slidably connected to the tool spindle 38a, whereby the planet carrier 120a remains rotationally coupled even with a stroke with the tool spindle 38a.
  • the first part 150a is permanently connected to the tool spindle 38a.
  • the first part 150a of the planet carrier 120a is axially displaceably mounted against the striking switching spring 148a.
  • a second part 152a of the plate carrier 120a of the second planetary gear stage 106a is non-rotatable with the first one
  • Part 150a of the planet carrier 120a connected.
  • the first part 150a and the second part 152a of the planetary carrier 120a are connected to each other so as to be axially displaceable.
  • the first part 150a and the second part 152a of the planetary carrier 120a are permanently connected in a rotationally fixed manner.
  • FIG. 10 shows a sectional area of a spindle locking device 154a of the hand tool device 12a.
  • the spindle locking device 154a is provided for non-rotatably connecting the tool spindle 38a to the hand tool housing 14a when a tool torque is applied to the tool chuck 36a, for example when clamping an insert tool into the tool chuck 36a.
  • the spindle locking device 154a is partially formed integrally with the planet carrier 120a of the second planetary gear stage 106a.
  • Spindle blocking device 154a has blocking means 156a, first clamping surfaces 158a, a second clamping surface 160a and free-wheeling surfaces 162a.
  • the blocking means 156a are formed roller-shaped.
  • the first clamping surfaces 158 a are as areas of a
  • the first clamping surfaces 158a are flat.
  • the second clamping surface 160a is formed as an inner side of a clamping ring 164a of the spindle locking device 154a.
  • the clamping ring 164a is rotatably connected to the hand tool housing 14a.
  • the free-wheeling surfaces 162a are formed as portions of a surface of the second portion 152a of the planetary carrier 120a of the second planetary gear stage 106a.
  • the blocking means 156a clamps between the first clamping surfaces 158a and the second clamping surface 160a.
  • the free-wheeling surfaces 162a guide the blocking means 156a in a circular path and prevent jamming.
  • the first part 150a and the second part 152a of the planetary carrier 120a are meshed with each other with play.
  • FIGS 1, 2, 9 and 10 show the torque limiting unit 34a.
  • the torque limiting unit 34a is provided to limit in a screwing mode a maximum of the tool chuck 36a delivered tool torque.
  • the torque limiting unit 34a comprises an operating element 166a, an adjusting element 168a, limiting springs 170a, transmission means (not shown), first stop surfaces 172a, a second stop surface 174a and limiting means 176a.
  • the operating element 166a is annular. It adjoins the tool chuck 36a in the direction of the planetary gear 28a.
  • the operating element 166a has an adjusting thread 178a, which is coupled to an adjusting thread 180a of the adjusting element 168a.
  • the adjusting element 168a is rotatably mounted and axially displaceable.
  • a rotation of the operating element 166a displaces the adjusting element 168a in the axial direction.
  • the limiting springs 170a are supported on one side on the adjusting element 168a.
  • the limiting springs 170a are supported on another side via the transmission means to a stop means 182a of the torque limiting unit 34a.
  • a surface of the abutment means 182a has the first abutment surfaces 172a.
  • the abutment means 182a is movably supported in the screwing mode in the axial direction against the limiting springs 170a.
  • the second abutment surface 174 a is as an area of a surface of a
  • Ring gear 184a of the second planetary gear stage 106a formed.
  • the second abutment surface 174a has trough-shaped depressions 186a.
  • the limiting means 176a are spherical.
  • the limiting means 176a are slidably mounted in tubular recesses 188a in the direction of impact 54a.
  • FIG. 11 shows a sectional area F of the torque limiting unit 34a.
  • the limiting means 176a are arranged in the trough-shaped depressions 186a.
  • the limiting means 176a fix the ring gear 184a of the second planetary gear stage 106a in a rotationally fixed manner.
  • the limiting means 176a press the abutment means 182a against the limiting springs 170a. Then the limiting means jump
  • the control element 134a of the hand tool device 12a has support means 190a, which prevent axial movement of the stop means 182a at least during a drilling operation.
  • the support means 190a support the abutment means 182a in the axial direction.
  • the abutment means 182a has screw recesses 192a into which the abutment means 182a submerge in a screwing operation shown in particular in FIG. 9 when the maximum tool torque is reached.
  • Supporting means 190a are accordingly in a screwed position of the control element 134a. arranged speaking. In a percussion drilling operation, the support means 190a also prevent axial movement of the abutment means 182a, and thus a response of the torque limiting unit 34a. Alternatively, stop means could also be arranged in a percussion drilling operation so that they can dip into screw recesses. Thus, a torque limiting unit would be active in percussion drilling.
  • FIG. 12 shows a sectional area G of the second planetary gear stage 106a.
  • the ring gear 184a of the second planetary gear stage 106a is mounted at least in a drilling operation against a complete rotation secured in the hand tool housing 14a.
  • Planet gears 194a of the second planetary gear stage 106a mesh with the ring gear 184a and a sun gear 196a of the second planetary gear stage 106a.
  • FIG. 13 shows a sectional area H of the third planetary gear stage 108a.
  • the sun gear 196a of the second planetary gear stage 106a is rotatably connected to a planetary carrier 198a of the third planetary gear stage 108a.
  • Planet gears 200a of the third planetary gear stage 108a mesh with a sun gear 202a and a ring gear 204a of the third planetary gear stage 108a.
  • the ring gear 204a of the third planetary gear stage 108a has a toothing 206a, which rotatably connects the ring gear 204a of the third planetary gear stage 108a in a first gear ratio with the hand tool housing 14a.
  • FIG. 14 shows a sectional area I of the third planetary gear stage 108a.
  • the sun gear 202a of the third planetary gear stage 108a is non-rotatably connected to a planet carrier 208a of the fourth planetary gear stage 1 10a.
  • Planetary gears 210a of the fourth planetary gear stage 1 10a mesh with a sun gear 212a and a ring gear 214a of the fourth planetary gear stage 1 10a.
  • the ring gear 214a is rotatably connected to the hand tool housing 14a.
  • the sun gear 212a of the fourth planetary gear stage 1 10a is non-rotatably connected to a rotor 216a of the drive unit 30a.
  • the ring gear 204a of the third planetary gear stage 108a is slidably mounted in the axial direction as shown in FIG.
  • the ring gear 204a of the third planetary gear stage 108a is non-rotatably connected to the hand tool housing 14a.
  • the ring gear 204a of the third planetary gear is drive stage 108a rotatably connected to the planet carrier 208a of the fourth planetary gear stage 1 10a and rotatably mounted relative to the hand tool housing 14a.
  • a reduction ratio of the first gear ratio between the rotor 216a of the drive unit 30a and the planetary carrier 198a of the third planetary gear stage 108a is greater than a reduction ratio of the second
  • the operating device 32a has a first operating element 218a and a second operating element 220a.
  • the first operating element 218a is arranged on a side of the hand tool housing 14a facing away from the handle 18a. It is movably mounted parallel to the axial direction of the planetary gear 28a.
  • the first operating element 218a is connected via an adjusting means 222a of the operating device 32a in the axial direction with the ring gear 204a of the third planetary gear stage 108a.
  • the ring gear 204a of the third planetary gear stage 108a has a groove 224a in which the adjusting means 222a engages.
  • the ring gear 204a of the third planetary gear stage 108a is connected to the adjusting means 222a, axially rotatable relative to the adjusting means 222a, in the axial direction.
  • the adjusting means 222a is resilient, whereby the translation of a rotational position of the ring gear 204a of the third planetary gear stage 108a can be adjusted independently.
  • the second operating element 220a is arranged on a side of the hand tool housing 14a facing away from the handle 18a.
  • the second operating element 220a is displaceably arranged about an axis which is aligned parallel to the axial direction of the planetary gear 28a.
  • the second control element 220a is non-rotatably connected to the control element 134a of the hand tool device 12a.
  • FIG. 15 schematically shows a protective device 226a of the hand tool device 12a, which prevents operation in the first gear ratio in the impact drilling mode.
  • the protection device 226a is partially formed integrally with the operating device 32a.
  • a first blocking means 228a of the protective device 226a is formed.
  • a second blocking means 230a of the protective device 226a is formed.
  • the blocking means 228a are each formed tongue-shaped. The first blocking means 228a extends in the direction of the second operating element 220a.
  • the second blocking means 230a extends in the direction of the first operating element 218a.
  • the protector 226a prevents switching to the hammering mode when the first gear ratio is adjusted.
  • the protector 226a prevents switching to the first gear ratio when the hammering mode is set.
  • the drive unit 30a is designed as an electric motor.
  • the drive unit 30a has a maximum torque which causes a maximum tool torque in the first gear ratio of more than 15 Nm and in the second gear ratio of less than 15 m.
  • the maximum tool torque in the first gear ratio is 30 Nm.
  • the maximum tool torque in the second ratio is 10 Nm.
  • the tool torque must be determined according to the standard DIN EN 60745.
  • the striking switch spring 148a of the hand tool device 12a opens the strike cutout clutch 142a in a hammer drill operation when the operator sets the insert tool off the workpiece.
  • the striking switch spring 148a is coaxial with the
  • Planetary gear stages 104a, 106a, 108a, 1 10a of the planetary gear 28a arranged.
  • the second planetary gear stage 106a and the third planetary gear stage 108a respectively enclose the striking switching spring 148a on at least one plane aligned perpendicular to the axial direction of the planetary gear 28a.
  • the second planetary gear stage 106a and the third planetary gear stage 108a are each operatively arranged between at least two further planetary gear stages 104a, 106a, 108a, 110a of the planetary gear 28a.
  • the planet carrier 120a of the second planetary gear stage 106a supports the impact switching spring 148a on a side facing away from the tool chuck 36a.
  • FIGS. 16 to 19 show further exemplary embodiments of the invention.
  • the following descriptions and the drawings are essentially limited to the differences between the exemplary embodiments, wherein with respect to the same named components, in particular with respect to components with the same reference numerals, in principle to the drawings and / or the description of the other embodiments, in particular Figures 1 to 15, can be referenced.
  • To distinguish the embodiments of the letter a is the reference numerals of the embodiment in the figures 1 to 15 adjusted.
  • the letter a is replaced by the letters b to e.
  • FIG. 16 schematically shows a further, alternative exemplary embodiment of a first impact shut-off device 24b.
  • a planet carrier 1 14b of a first planetary gear stage 104b is formed in two parts.
  • a first part 232b of the planet carrier 1 14b leads planetary gears 1 12b of the first planetary gear stage 104b.
  • a second part 234b of the planetary carrier 1 14b is connected to a second planetary gear stage
  • a first impact shut-off device 24b of a percussion mechanism 22b has a freewheel 236b which appears expedient to the person skilled in the art and rotatably connects the first part 232b and the second part 234b of the planetary carrier 1 14b in a clockwise rotational drilling direction and separates them in a counterclockwise boring rotation direction.
  • a ring gear 1 16b of the first planetary gear stage 104b is permanently rotatably connected to a hand tool housing.
  • FIG. 17 schematically shows a next exemplary embodiment of a first impact shut-off device 24c.
  • a percussion spindle 46c of a percussion mechanism 22c is formed in two parts.
  • a first part 238c of the percussion spindle 46c is connected to a racket driving device.
  • a second part 240c of the percussion spindle 46c is connected to a second planetary gear stage 106c.
  • the first impact shut-off device 24c has a freewheel 242c which appears expedient to the person skilled in the art and rotatably connects the first part 238b and the second part 240c of the percussion spindle 46c in a clockwise rotational drilling direction and separates them in a left-handed rotary drilling direction.
  • a ring gear 1 16c of the first planetary gear stage 104c is permanently rotatably connected to a hand tool housing.
  • FIG. 18 shows a further exemplary embodiment of a striking switching spring 148d.
  • a second planetary gear stage 106d supports the shock switch spring 148d a side facing a tool chuck off.
  • a drive unit 30d supports the impact switching spring 148d on a side facing away from a tool chuck.
  • the second planetary gear stage 106d, a third planetary gear stage 108d and a fourth planetary gear stage 10d respectively enclose the striking switching spring 148d on at least one plane aligned perpendicular to an axial direction of the planetary gear stages 106d, 108d, 110d.
  • the drive unit 30d is non-rotatably connected to a part of the planetary gear stage 1 1 Od.
  • FIG. 19 shows an alternative embodiment of the operating device 32e and a protective device 226e.
  • the operating device 32e has a first operating element 218e and a second operating element 220e.
  • the operating elements 218e, 220e are pivotally mounted about axes of rotation 244e, 246e.
  • the operating elements 218e, 220e have a disk-shaped basic shape.
  • the first control element 218e is, not shown in more detail, connected to a planetary gear mechanism via a mechanism that appears appropriate to a person skilled in the art.
  • a first ratio and a second ratio are adjustable.
  • the second control element 220e is, not shown in more detail, connected to a control via a mechanism which appears appropriate to a person skilled in the art.
  • a screwing mode, a drilling mode and a percussion drilling mode are adjustable.
  • a chisel mode could be adjustable.
  • the protection device 226e has a free-wheeling area 248e limited by the first operating element 218e.
  • the protection device 226e has a freewheeling area 250e limited by the second operating element 220e.
  • the freewheeling portion 248e of the first operating member 218e allows adjustment of the screwing mode, the
  • Drilling mode and impact drilling mode when a second ratio is set The freewheeling area 250e of the second operating member 220e allows adjustment of the tightening mode and the drilling mode when a first gear ratio is adjusted. In the impact drilling mode, the protector 226e prevents adjustment of the first gear ratio. When set the first translation prevents the protection device

Landscapes

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

Abstract

L'invention concerne un système d'outil portatif comprenant un mécanisme de percussion (22a; 22b; 22c), lequel comprend au moins un marteau (44a) et une structure de guidage courbe (62a, 64a) qui entraîne ledit marteau (22a; 22b; 22c) au moins pendant une opération de perçage par percussion. Selon l'invention, au moins une partie de la structure de guidage courbe (62a, 64a) est formée sur le marteau (22a; 22b; 22c).
EP12810244.9A 2011-12-27 2012-12-19 Dispositif pour outil manuel Active EP2797721B1 (fr)

Priority Applications (1)

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EP21162272.5A EP3881974A1 (fr) 2011-12-27 2012-12-19 Dispositif outil manuel

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DE102011089910A DE102011089910A1 (de) 2011-12-27 2011-12-27 Handwerkzeugvorrichtung
PCT/EP2012/076201 WO2013098167A1 (fr) 2011-12-27 2012-12-19 Système d'outil portatif

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EP21162272.5A Division-Into EP3881974A1 (fr) 2011-12-27 2012-12-19 Dispositif outil manuel
EP21162272.5A Division EP3881974A1 (fr) 2011-12-27 2012-12-19 Dispositif outil manuel

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EP2797721A1 true EP2797721A1 (fr) 2014-11-05
EP2797721B1 EP2797721B1 (fr) 2023-03-01

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EP12810244.9A Active EP2797721B1 (fr) 2011-12-27 2012-12-19 Dispositif pour outil manuel

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US (2) US10315299B2 (fr)
EP (2) EP3881974A1 (fr)
JP (2) JP5847962B2 (fr)
CN (2) CN104023919B (fr)
DE (1) DE102011089910A1 (fr)
RU (1) RU2635030C2 (fr)
WO (1) WO2013098167A1 (fr)

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WO2018020283A1 (fr) * 2016-07-27 2018-02-01 BEREGSZASZI, David Dispositif de conversion de mouvement
CN106737039A (zh) * 2016-12-19 2017-05-31 上海浦江桥隧运营管理有限公司 旋转式气动除锈枪
TWI676534B (zh) 2017-03-29 2019-11-11 美商米沃奇電子工具公司 擊壓工具
CN110153957B (zh) * 2018-02-14 2023-08-11 苏州宝时得电动工具有限公司 手持式动力工具
WO2019158115A1 (fr) * 2018-02-14 2019-08-22 苏州宝时得电动工具有限公司 Outil à percussion
CN112207758B (zh) * 2019-07-09 2022-06-14 苏州宝时得电动工具有限公司 动力工具
JP2024029802A (ja) * 2022-08-23 2024-03-07 株式会社Subaru 工具駆動装置及び被穿孔品の製造方法

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Also Published As

Publication number Publication date
JP6053899B2 (ja) 2016-12-27
US20190255693A1 (en) 2019-08-22
DE102011089910A1 (de) 2013-06-27
CN104023919B (zh) 2017-06-13
US10315299B2 (en) 2019-06-11
US10960526B2 (en) 2021-03-30
RU2635030C2 (ru) 2017-11-08
WO2013098167A1 (fr) 2013-07-04
JP2015503454A (ja) 2015-02-02
EP2797721B1 (fr) 2023-03-01
CN104023919A (zh) 2014-09-03
CN107214664B (zh) 2021-03-19
RU2014130905A (ru) 2016-02-20
JP5847962B2 (ja) 2016-01-27
EP3881974A1 (fr) 2021-09-22
CN107214664A (zh) 2017-09-29
US20150075828A1 (en) 2015-03-19
JP2016027952A (ja) 2016-02-25

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