EP2797721B1 - Hand tool device - Google Patents
Hand tool device Download PDFInfo
- Publication number
- EP2797721B1 EP2797721B1 EP12810244.9A EP12810244A EP2797721B1 EP 2797721 B1 EP2797721 B1 EP 2797721B1 EP 12810244 A EP12810244 A EP 12810244A EP 2797721 B1 EP2797721 B1 EP 2797721B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- impact
- tool
- hand
- spindle
- planetary gear
- 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
Links
- 230000007246 mechanism Effects 0.000 claims description 93
- 238000005553 drilling Methods 0.000 claims description 48
- 230000033001 locomotion Effects 0.000 claims description 18
- 238000009527 percussion Methods 0.000 description 56
- 230000000903 blocking effect Effects 0.000 description 16
- 230000001681 protective effect Effects 0.000 description 8
- 230000005540 biological transmission Effects 0.000 description 7
- 238000000034 method Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 238000004804 winding Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
Classifications
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- 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 that has at least one hammer and a cam guide that drives the hammer at least during percussion drilling operation has already been proposed.
- U.S. 2,794,621 A an attachment is disclosed which is intended to be arranged between a drive unit and an application tool.
- the attachment is designed to convert a rotary movement of a work spindle into a rotary and axial movement of the insert tool.
- U.S. 2,794,621 A discloses a hand tool device according to the preamble of claim 1.
- U.S. 2006/024141 A1 describes a hand-held power tool with a motor to provide a drive torque to a drive spindle, a work spindle to set a tool holder in rotation, the work spindle being connectable to the drive spindle, an angular torque generator which is designed to transmit an angular torque deliver the work spindle.
- DE 10 68 198 B discloses a percussion mechanism for rotary percussion drills, rotary hammers, demolition hammers and the like with individual percussion pistons eccentrically mounted in a percussion piston housing and working on a percussion plate and a curve recorder that controls and drives the percussion pistons.
- the U.S. 1,494,109 A describes an electrically powered hammer configured to convert rotary motion of a drive motor into reciprocating motion of a piston.
- WO 2010/069647 A1 discloses a hand tool in which a counterweight is mounted for reciprocation along a translational axis.
- the counterweight is in active engagement with a guide curve formed in particular in a surface of a rotatably mounted rotary body.
- the guide curve is designed in such a way that the counterweight can be swung back and forth when the rotating body is rotated.
- EP 1 690 642 A1 describes a reciprocating drive mechanism for a hammer in an electric screwdriver with a hammer mechanism.
- the invention is based on a hand tool device with an impact mechanism which has at least one impactor and a cam guide which drives the impactor at least during percussion drilling operation.
- the hand tool device according to the invention comprises the features of claim 1.
- the racquet has at least part of the curve guide.
- a "percussion mechanism” is to be understood in particular as a device which is intended to generate an impact impulse and in particular to emit it in the direction of an application tool.
- the hammer mechanism preferably forwards the hammer pulse to the insert tool, at least during hammer drilling operation, advantageously via a tool spindle and/or in particular via a tool chuck of the hand tool device.
- the term "beater” should be understood to mean a means that is accelerated at least in a percussion drilling operation, in particular translationally, and emits an impulse picked up during the acceleration as an impact impulse in the direction of the insert tool.
- the racquet is preferably constructed in one piece. Alternatively, the racquet could be constructed in several pieces be.
- a "curved guide” should be understood to mean a device that translates rotational energy for generating an impact into linear kinetic energy of the impactor, at least by means of a specially shaped guide surface along which a connecting means runs, at least during percussion drilling.
- the hammer mechanism preferably has a hammer mechanism spring, which stores the linear kinetic energy of the hammer to generate an impact.
- the specially shaped surface is a surface that delimits a guide curve of the curve guide.
- a “connecting means” is to be understood in particular as meaning a means that creates a mechanical coupling between at least one part of the impact mechanism that rotates during percussion drilling operation, in particular a percussion mechanism spindle, and the in particular linearly moving hammer.
- a “guide curve” should be understood to mean an area delimited by the guide surface, in which the connecting means runs in at least one operating state.
- a “impact mechanism spring” is to be understood in particular as a spring which stores at least part of an impact energy in at least one operating state.
- support should be understood to mean that a part of the striking mechanism spring is arranged immovably relative to the hammer or a part of the striking mechanism spring is arranged immovably relative to a hand tool housing.
- the hammer mechanism spring is designed as a spring that appears sensible to a person skilled in the art, but preferably as a helical spring.
- drive is to be understood in particular as meaning that the curve guide transfers energy to the racquet to generate an impact.
- the expression that “the racquet has at least part of the curve guide” should be understood in particular to mean that the racquet has a surface to which the connecting means directly transmits the energy for generating the striking movement.
- the part of the curve guide which the racquet has is formed as a surface which fixes the connecting means in place relative to the racquet.
- the part of the curved guide which the racquet has comprises a fastening recess which is delimited by the surface and which fastens the connecting means in a stationary manner relative to the racquet.
- the racquet is provided to attach a connecting means which, during operation, connects the part of the curved guide and a further part of the curved guide, in particular the guide curve.
- the connecting means and the racquet are connected in an unsprung manner. This means in particular that no spring is arranged between the connecting means and the racquet in terms of effect.
- the part of the curve guide, the racket has, be designed as a guide curve.
- “Stationary” is to be understood in particular as meaning that an axis of symmetry and/or a center point of the connecting means is at least essentially stationary relative to the racquet during a striking operation.
- the design of the hand tool device according to the invention makes it possible to provide a particularly small, light and yet powerful impact mechanism. in particular, a wobble bearing or a rocker arm can advantageously be dispensed with.
- the curve guide has an impact-free running area, as a result of which high impact energy and advantageously low wear can be achieved with a short overall length.
- a "impact freewheel area” is to be understood in particular as an area of the guide curve of the curved guide in which the connecting means is arranged when the striking mechanism spring accelerates the beater in the direction of impact.
- the non-impact area is preferably designed so wide that the connecting means can run through the non-impact area on different paths.
- the impact freewheel area does not cause any force on the hammer.
- the curve guide has an impact elevator area, as a result of which advantageous operation, in particular with low vibrations, can be achieved.
- an "impact lift area” should be understood to mean an area of the guide curve of the cam guide that moves the hammer at least during percussion drilling operation, in particular relative to the hand tool housing, counter to the direction of impact.
- the movement of the hammer caused by the hammer winding area against the direction of impact preferably compresses the hammer mechanism spring.
- the guide surface of the impact elevator area has an incline relative to the direction of impact of between 5 degrees and 35 degrees, advantageously between 10 degrees and 25 degrees.
- the curve guide has an assembly cutout, as a result of which advantageous assembly and a particularly small configuration are possible.
- An “assembly recess” should be understood to mean an area delimited by the percussion mechanism spindle, through which the connecting means is introduced into the guide curve during assembly.
- the percussion mechanism comprises a percussion mechanism spindle which has at least part of the cam guide, as a result of which a compact configuration can be achieved.
- a "percussion mechanism spindle” is to be understood in particular as a shaft which transmits a rotational movement from a planetary gear of the hand tool device to the cam guide.
- the percussion mechanism spindle is preferably designed as a hollow shaft.
- the percussion mechanism spindle has a guide curve of the curve guide, as a result of which simple production is possible.
- the hammer at least essentially encloses the hammer mechanism spindle on at least one level, as a result of which an embodiment with a small volume and weight is possible.
- the phrase “at least substantially encloses on at least one plane” should be understood to mean that rays emanating from an axis of the percussion mechanism spindle, which are arranged on the plane, intersect the beater over an angular range of at least 180 degrees, advantageously at least 270 degrees.
- the bat encloses the striking mechanism spindle by 360 degrees, which is particularly advantageous.
- the hammer mechanism has a connecting means which, in at least one operating state, transmits a movement, in particular from the hammer mechanism spindle to the hammer, so that less wear, effective manufacture and simple assembly can be achieved.
- the hand tool device comprises a tool spindle, which the hammer at least essentially encloses on at least one level.
- a "tool spindle” is to be understood in particular as a shaft which transmits a rotational movement from the planetary gear to the tool chuck.
- the tool spindle is preferably designed as a solid shaft.
- the tool spindle could be designed as a hollow shaft.
- the tool spindle is arranged at least essentially coaxially with the percussion mechanism spindle, as a result of which a particularly compact configuration is possible.
- the phrase “arranged at least essentially coaxially” is to be understood to mean that an axis of rotation of the tool spindle and an axis of rotation of the percussion mechanism spindle are arranged at a distance of less than 20 mm, advantageously less than 10 mm, from one another at at least one point and have an alignment difference of less than 15 degrees, advantageously less than 5 degrees, to each other.
- the axis of rotation of the tool spindle and the axis of rotation of the percussion mechanism spindle are particularly preferably arranged on the same straight line and aligned in the same way.
- the hammer mechanism has a hammer guide which supports the hammer in a rotationally fixed manner, as a result of which a constructively simple curve guidance is possible.
- a “racquet guide” is to be understood in particular as a device that supports the racquet so that it can move parallel to the direction of impact.
- the phrase “rotatably mounted” should be understood to mean that the hammer guide counteracts in particular any rotational movement of the hammer relative to a hand tool housing.
- the hand tool device comprises a hand tool housing, the hammer mechanism having a hammer mechanism spring which is supported on the hammer and on the hand tool housing, as a result of which a particularly small axial overall length can be achieved.
- a “hand tool housing” should be understood to mean a housing that has an interior space in which at least the percussion mechanism, the planetary gear and a drive unit of the hand tool housing are arranged.
- the hand-held tool housing preferably at least partially connects at least the percussion mechanism, the planetary gear and a drive unit of the hand-held tool housing to one another.
- the percussion mechanism has the first cam guide and a second cam guide, as a result of which less wear and very smooth running are possible.
- the invention is based on a hand tool with a hand tool device according to the invention.
- the hand tool is preferably provided for to drive the application tool in a screw mode, in a drill mode, in a screw drill mode and in particular in a chisel mode.
- 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 intended to supply the hand tool device 12a with electrical energy from a hand tool battery not shown in detail here.
- the hand tool housing 14a is designed in the shape of a pistol.
- the hand tool housing 14a is designed in several parts. It includes a handle 18a, by means of which an operator holds the hand tool 10a during a work process.
- the hand tool device 12a includes a tool guide unit 20a, an impact 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 includes a tool chuck 36a and a tool spindle 38a.
- the tool chuck 36a fastens an insert tool, not shown here, for example a drill or a screw bit.
- the tool chuck 36a fastens the application tool in a non-positive manner.
- the tool chuck 36a has three clamping jaws which are fastened so that they can be moved by an operator and which fasten the insert tool during a work process.
- the tool chuck 36a fastens the insert tool in an axially immovable manner relative to the tool chuck 36a and in particular the tool spindle 38a during a working process.
- 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 in an axially displaceable manner.
- the bearing means 40a is axially firmly connected to the tool spindle 38a.
- the bearing means 40a is mounted in the hand tool housing 14a so that it can move axially.
- the hand tool device 12a has a further bearing means 41a, which mounts the tool spindle 38a on a side facing the planetary gear 28a.
- the bearing means 41a is designed as a roller bearing, here as a needle bearing, which allows low-backlash mounting.
- the bearing means 41a supports the tool spindle 38a in an axially displaceable manner.
- a percussion mechanism spindle 46a encloses the bearing means 41a.
- the bearing means 41a is functionally arranged between the tool spindle 38a and the percussion mechanism spindle 46a.
- the tool spindle 38a includes an impact surface 42a, on which an impactor 44a of the impact mechanism 22a impacts during an impact drilling operation.
- the striker 44a has a mass that is at most two-thirds as large as a mass of the tool guide unit 20a. Here the mass of the striker 44a is less than half the mass of the tool guide unit 20a.
- the mass of the beater 44a is approximately 45% of the mass of the tool guide unit 20a.
- the striking mechanism 22a has the striking mechanism 44a, the striking mechanism spindle 46a, a striking mechanism spring 48a, a striking mechanism drive device 50a and a striking mechanism guide 52a.
- the hammer 44a is mounted so that it can move in a translatory manner in the direction of impact 54a.
- Impact direction 54a is aligned parallel to an axial direction of impact mechanism spindle 46a.
- the Figures 3 and 4 show a sectional area A and a sectional area B of the percussion mechanism 22a.
- the bat guide 52a supports the bat 44a in a rotationally fixed manner relative to the hand tool housing 14a.
- the racquet guide 52a has three guide rods 56a on which the racquet 44a slides.
- the guide rods 56a are regularly arranged around the beater 44a.
- the beater 44a has sliding surfaces 58a which enclose the guide rods 56a by 180 degrees on a plane perpendicular to the direction of impact 54a.
- the hammer 44a encloses the hammer mechanism spindle 46a by 360 degrees on a plane which is oriented perpendicular to the direction of impact 54a.
- the beater 44a encloses the tool spindle 38a on the plane by 360 degrees. Furthermore, the percussion mechanism spindle 46a encloses the tool spindle 38a by 360 degrees on the plane. Impact mechanism spindle 46a is arranged coaxially with tool spindle 38a.
- the hammer mechanism spring 48a accelerates the hammer 44a before an impact in the impact direction 54a.
- the hand tool housing 14a supports the hammer mechanism spring 48a on a side facing away from the hammer 44a.
- the hammer mechanism spring 48a presses directly against the hammer 44a.
- the racquet 44a has a spring attachment 60a.
- the spring mount 60a is formed as an annular recess.
- figure 5 shows the percussion mechanism spindle 46a in a perspective view.
- figure 6 shows the bat 44a in a perspective view.
- the racquet drive device 50a has a first cam guide 62a and a second first cam guide 64a.
- the curve guides 62a, 64a each comprise a guide curve 66a, 68a and a connecting means 70a, 72a.
- the connecting means 70a, 72a are spherical.
- the racquet 44a supports the connecting means 70a, 72a in a stationary manner relative to the racquet 44a.
- Beater 44a has hemispherical mounting recesses 74a.
- the connecting means 70a, 72a slide in the guide curve 66a, 68a during percussion drilling operation.
- Impact mechanism spindle 46a has part of cam guides 62a, 64a, namely guide curve 66a, 68a. Impact mechanism spindle 46a delimits a space in which connecting means 70a, 72a move during impact drilling operation.
- Impact mechanism spindle 46a is designed as a hollow shaft.
- the planetary gear 28a drives the percussion mechanism spindle 46a.
- the percussion mechanism spindle 46a has teeth 76a on a side facing away from the tool chuck 36a.
- the guide curves 66a, 68a each have a run-out area 78a, 80a, a Impact elevator area 82a, 84a and a mounting recess 86a, 88a.
- the connecting means 70a, 72a are introduced through the assembly recesses 86a, 88a into the fastening recesses 74a of the racquet 44a.
- the percussion mechanism spindle 46a rotates clockwise when viewed in the percussion direction 54a during the percussion drilling operation.
- the impact elevator areas 82a, 84a are formed in a spiral shape. They extend 180 degrees around an axis of rotation 90a of the percussion mechanism spindle 46a.
- the impact elevator areas 82a, 84a move the connecting means 70a, 72a and thus the hammer 44a during the hammer drilling operation against the impact direction 54a.
- the hammer mechanism 22a thus has the connecting means 70a, 72a, which in at least one operating state transmit a movement from the hammer mechanism spindle 46a to the hammer 44a.
- the impact-free regions 78a, 80a each connect two ends 92a, 94a, 96a, 98a of the impact winding regions 82a, 84a.
- Impact freewheel areas 78a, 80a extend 180 degrees around an axis of rotation 90a of impact mechanism spindle 46a.
- Impact freewheel areas 78a, 80a each have an impact flank 100a, 102a, which, starting from an end 94a, 96a of impact winding area 82a facing planetary gear 28a, runs approximately parallel to impact direction 54a.
- the connecting means 70a, 72a move through the non-impact areas 78a, 80a, without experiencing an axial force, until the hammer 44a hits the impact surface 42a.
- the cam guides 62a, 64a are offset by 180 degrees about the axis of rotation 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 110a.
- figure 7 shows a sectional area C of the first planetary gear stage 104a.
- the in the figures 7 , 12 , 13 and 15 The planetary gear stages 104a, 106a, 108a, 110a shown have gears with a number of teeth that appears reasonable to a person skilled in the art.
- the gears of the planetary gear stages 104a, 106a, 108a, 110a mesh with one another, 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 percussion mechanism 22a.
- the second planetary gear stage 106a drives at this first rotational speed the tool spindle 38a.
- the toothing 76a of the impact mechanism spindle 46a forms a sun wheel of the first planetary gear stage 104a.
- the toothing 76a meshes with planet gears 112a of the first planetary gear stage 104a, which are guided by a planet carrier 114a of the first planetary gear stage 104a.
- a ring gear 116a of the first planetary gear stage 104a meshes with the planet wheels 112a of the first planetary gear stage 104a.
- the first impact shut-off device 24a fixes the ring gear 116a of the first planetary gear stage 104a immovably relative to the hand tool housing 14a during an impact drilling operation.
- the first impact shut-off device 24a is provided to switch on the hammer drive device 50a in a first, clockwise drilling rotation direction and to automatically switch off the hammer drive device 50a in a second, counterclockwise drilling rotation direction.
- the first impact switch-off device 24a acts on the ring gear 116a of the first planetary gear stage 104a.
- the first impact shut-off device 24a blocks the ring gear 116a of the first planetary gear stage 104a in the first, clockwise direction of drilling rotation.
- the first impact shut-off device 24a releases the ring gear 116a of the first planetary gear stage 104a in the second, counterclockwise drilling rotation direction, so that it can rotate.
- the first impact shut-off device 24a has three clamping mechanisms 122a.
- the clamping mechanisms 122a each comprise a blocking means 124a, a first clamping surface 126a, a second clamping surface 128a and freewheel surfaces 130a.
- the blocking means 124a is designed as a roller.
- the first clamping surface 126a forms an outer area of a surface of the ring gear 116a of the first planetary gear stage 104a.
- the second clamping surface 128a is arranged immovably relative to the hand-held tool housing 14a.
- the blocking means 124a clamp between the first clamping surfaces 126a and the second clamping surface 128a.
- the free-running surfaces 130a guide the blocking means 124a and prevent jamming.
- the figure 7 a connecting means 118a which non-rotatably connects the tool spindle 38a and a planet carrier 120a of the second planetary gear stage 106a.
- the connecting means 118a connects the tool spindle 38a and the planet carrier 120a of the second planetary gear stage 106a in an axially displaceable manner.
- FIGs 3, 4 and 7 three first transmission means 132a of the second impact shut-off device 26a.
- the transmission means 132a are in the form of rods.
- figure 8 shows a section surface D through a control element 134a of the hand tool device 12a.
- figure 9 shows the second impact shut-off device 26a in a perspective sectional view.
- the control element 134a supports the tool guide unit 20a in one of the figures 1 , 8th and 9 , illustrated screwing mode and in a drilling mode in a direction opposite to the impact direction 54a.
- a force applied to the tool guide unit 20a acts via the bearing means 40a, a second transmission means 136a of the second impact shut-off device 26a and the first transmission means 132a on support surfaces 138a of the control element 134a.
- the control element 134a has three recesses 140a. In one in the figure 2 In the percussion drilling mode shown, the first transmission means 132a can be inserted into the recesses 140a, as a result of which the tool guide unit 20a can be moved axially.
- the second impact shutoff device 26a has an impact shutoff clutch 142a.
- Impact shut-off clutch 142a is partially integral with planetary gear 28a.
- the impact cut-off clutch 142a is arranged between the first planetary gear stage 104a and the second planetary gear stage 106a.
- Impact cut-off clutch 142a has a first clutch element 144a, which is connected in a torque-proof manner to a planet carrier 114a of first planetary gear stage 104a.
- Impact cut-off clutch 142a has a second clutch element 146a, which is connected in a torque-proof manner to a planet carrier 120a of second planetary gear stage 106a. In the illustrated screwing mode and the drilling mode, the impact shut-off clutch 142a is open.
- the tool spindle 38a transmits an axial clutch force to the hammer shut-off clutch 142a when the operator presses an application tool against a workpiece.
- the clutch force closes the impact shut-off clutch 142a.
- the impact cut-off clutch 142a is shown closed.
- an impact switching spring 148a of the hand tool device 12a opens the impact shut-off clutch 142a.
- the planet carrier 120a of the second planetary gear stage 106a is designed 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.
- the first part 150a of the planet carrier 120a is axially displaceably connected to the tool spindle 38a, whereby the planetary carrier 120a remains rotationally coupled to the tool spindle 38a even in the event of an impact.
- the first part 150a is permanently connected to the tool spindle 38a.
- the first part 150a of the planet carrier 120a is mounted in an axially displaceable manner against the percussion switching spring 148a.
- a second part 152a of the planetary carrier 120a of the second planetary gear stage 106a is non-rotatably connected to the first part 150a of the planetary carrier 120a.
- the first part 150a and the second part 152a of the planet carrier 120a are connected to one another in an axially displaceable manner.
- the first part 150a and the second part 152a of the planet carrier 120a are permanently connected in a rotationally fixed manner.
- FIG 10 shows a sectional surface of a spindle locking device 154a of the hand tool device 12a.
- the spindle blocking device 154a is provided to connect the tool spindle 38a in a torque-proof manner to the hand tool housing 14a when a tool torque is applied to the tool chuck 36a, for example when an insert tool is clamped in the tool chuck 36a.
- the spindle locking device 154a is partially integral with the planet carrier 120a of the second planetary gear stage 106a.
- the spindle blocking device 154a has blocking means 156a, first clamping surfaces 158a, a second clamping surface 160a and freewheel surfaces 162a.
- the blocking means 156a are designed in the form of rollers.
- the first clamping surfaces 158a are designed as areas of a surface of the first part 150a of the planet carrier 120a of the second planetary gear stage 106a.
- the first clamping surfaces 158a are flat.
- the second clamping surface 160a is designed as an inside of a clamping ring 164a of the spindle locking device 154a.
- the clamping ring 164a is non-rotatably connected to the hand tool housing 14a.
- the freewheeling surfaces 162a are designed as areas of a surface of the second part 152a of the planet carrier 120a of the second planetary gear stage 106a.
- the locking means 156a clamps between the first clamping surfaces 158a and the second clamping surface 160a.
- the freewheeling surfaces 162a guide the blocking means 156a on a circular path and prevent jamming.
- the first part 150a and the second part 152a of the planet carrier 120a are interlocked with play.
- the figures 1 , 2 , 9 and 10 show the torque limiting unit 34a.
- the torque limiting unit 34a is provided to limit a maximum tool torque delivered by the tool chuck 36a in a screwing mode.
- the torque limiting unit 34a includes an operating element 166a, an adjustment element 168a, limiting springs 170a, transmission means not shown in detail, first stop surfaces 172a, a second stop surface 174a and limiting means 176a.
- the operating element 166a is ring-shaped. It follows the tool chuck 36a in the direction of the planetary gear 28a.
- the operating element 166a has an adjustment thread 178a which is coupled to an adjustment thread 180a of the adjustment element 168a.
- the adjusting element 168a is mounted in a rotationally fixed and axially displaceable manner. A rotation of the operating element 166a displaces the adjustment element 168a in the axial direction.
- the limiting springs 170a are supported on one side on the adjustment element 168a.
- the limiting springs 170a are supported on another side via the transmission means on a stop means 182a of the torque limiting unit 34a.
- a surface of the stop means 182a has the first stop surfaces 172a.
- the stop means 182a is mounted so that it can move in the axial direction against the limiting springs 170a in the screwing mode.
- the second stop surface 174a is designed as a region of a surface of a ring gear 184a of the second planetary gear stage 106a.
- the second stop surface 174a has trough-shaped depressions 186a.
- the delimiting means 176a are of spherical design.
- the limiting means 176a are mounted in tubular recesses 188a so that they can be displaced 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 fasten the ring gear 184a of the second planetary gear stage 106a in a rotationally fixed manner.
- the limiting means 176a push the stop means 182a away against the limiting springs 170a.
- the delimiting means 176a each jump into a next one of the trough-shaped depressions 186a.
- the ring gear 184a of the second planetary gear stage 106a rotates, as a result of which the screwing process is interrupted.
- the control element 134a of the hand tool device 12a has support means 190a, which prevent an axial movement of the stop means 182a, at least during a drilling operation.
- the support means 190a support the stop means 182a in the axial direction.
- the stop means 182a has screw recesses 192a, in which the stop means 182a in a particular in the figure 9 shown screwdriving operation when the maximum tool torque is reached.
- the support means 190a are accordingly in a screwed position of the control element 134a arranged.
- the support means 190a also prevent an axial movement of the stop means 182a and thus a response of the torque limiting unit 34a.
- stop means could also be arranged in a percussion drilling operation in such a way that they can dip into screw recesses. A torque limiting unit would thus be active in percussion drilling operation.
- FIG 12 shows a sectional area G of the second planetary gear stage 106a.
- Ring gear 184a of second planetary gear stage 106a is mounted in hand tool housing 14a, secured against complete rotation at least during drilling operation.
- 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.
- figure 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 planet 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 teeth 206a which, in a first gear ratio, connect the ring gear 204a of the third planetary gear stage 108a to the hand tool housing 14a in a torque-proof manner.
- figure 14 shows a section I of the third planetary gear stage 108a.
- the sun gear 202a of the third planetary gear stage 108a is rotatably connected to a planet carrier 208a of the fourth planetary gear stage 110a.
- Planet gears 210a of the fourth planetary gear stage 110a mesh with a sun gear 212a and a ring gear 214a of the fourth planetary gear stage 110a.
- Ring gear 214a is connected to hand tool housing 14a in a torque-proof manner.
- the sun gear 212a of the fourth planetary gear stage 110a is rotatably connected to a rotor 216a of the drive unit 30a.
- the ring gear 204a of the third planetary gear stage 108a is as in figure 2 shown slidably mounted in the axial direction.
- ring gear 204a of third planetary gear stage 108a is connected to hand tool housing 14a in a torque-proof manner.
- the ring gear 204a of the third planetary gear stage is in the second gear ratio 108a rotatably connected to the planet carrier 208a of the fourth planetary gear stage 110a and rotatably mounted relative to the hand tool housing 14a. This results in a reduction ratio of the first translation between the rotor 216a of the drive unit 30a and the planetary carrier 198a of the third planetary gear stage 108a, which is greater than a reduction ratio of the second translation.
- 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 control element 218a is connected in the axial direction to the ring gear 204a of the third planetary gear stage 108a via an adjusting means 222a of the control device 32a.
- 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 in the axial direction to the adjusting means 222a, so that it can rotate axially relative to the adjusting means 222a.
- the adjusting means 222a is designed to be resilient, as a result of which the translation can be adjusted independently of a rotational position of the ring gear 204a of the third planetary gear stage 108a.
- 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 arranged such that it can be displaced about an axis which is aligned parallel to the axial direction of the planetary gear 28a.
- the second control element 220a is rotatably connected to the control element 134a of the hand tool device 12a.
- the screwing mode, the drilling mode and the percussion drilling mode can be set using the second operating element 220a. If the second operating element 220a is pushed to the left as viewed in the impact direction 54a, the impact drilling mode is set. When the second control element 220a is pushed to the right, viewed in the direction of impact 54a, the screwing mode is set. The drilling mode is set when the second operating element 220a is arranged in the center as viewed in the direction of impact 54a.
- FIG. 12 shows schematically a guard 226a of the hand tool device 12a that prevents operation in first gear in the hammer drilling mode.
- the protective device 226a is partially formed in one piece with the operating device 32a.
- a first blocking means 228a of the protective device 226a is formed onto the first operating element 218a.
- a second blocking means 230a of the protective device 226a is formed onto the second operating element 220a.
- the blocking means 228a are each designed in the shape of a tongue.
- 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 guard 226a prevents switching to hammer drilling mode when first gear is engaged.
- the guard 226a prevents shifting to first gear when the hammer drill mode is set.
- the drive unit 30a is designed as an electric motor.
- the drive unit 30a has a maximum torque that causes a maximum tool torque in the first gear of more than 15 Nm and in the second gear of less than 15 m.
- the maximum tool torque in the first gear is 30 Nm.
- the maximum tool torque in the second gear is 10 Nm.
- the tool torque is to be determined according to the DIN EN 60745 standard.
- the impact switching spring 148a of the hand tool device 12a opens the impact shut-off clutch 142a during percussion drilling operation when the operator removes the application tool from the workpiece.
- the impact switch spring 148a is arranged coaxially to the planetary gear stages 104a, 106a, 108a, 110a of the planetary gear 28a.
- the second planetary gear stage 106a and the third planetary gear stage 108a each enclose the percussion switching spring 148a on at least one plane which is 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 planetary carrier 120a of the second planetary gear stage 106a supports the impact switch spring 148a on a side facing away from the tool chuck 36a.
- a planet carrier 114b of a first planetary gear stage 104b is formed in two parts.
- a first part 232b of the planetary carrier 114b carries planetary gears 112b of the first planetary gear stage 104b.
- a second part 234b of the planetary carrier 114b is rotationally coupled to a second planetary gear stage 106b.
- a first impact shut-off device 24b of an impact mechanism 22b has a freewheel 236b, which appears sensible to the person skilled in the art, which non-rotatably connects the first part 232b and the second part 234b of the planetary carrier 114b in a clockwise drilling rotation direction and separates it in a counterclockwise drilling rotation direction.
- a ring gear 116b of the first planetary gear stage 104b is permanently connected to a hand tool housing in a rotationally fixed manner.
- a percussion mechanism spindle 46c of a percussion mechanism 22c is designed in two parts.
- a first part 238c of the hammer mechanism spindle 46c is connected to a hammer drive device.
- a second part 240c of the impact mechanism spindle 46c is connected to a second planetary gear stage 106c.
- the first impact shut-off device 24c has a freewheel 242c, which appears useful to those skilled in the art, which non-rotatably connects the first part 238b and the second part 240c of the impact mechanism spindle 46c in a clockwise drilling rotation direction and separates it in a counterclockwise drilling rotation direction.
- a ring gear 116c of the first planetary gear stage 104c is permanently connected in a rotationally fixed manner to a hand tool housing.
- FIG 18 a further exemplary embodiment of an impact switch spring 148d is shown.
- a second planetary gear stage 106d supports the impact switching spring 148d from a side facing a tool chuck.
- 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 110d each enclose the percussion switch spring 148d on at least one plane which is aligned perpendicular to an axial direction of the planetary gear stages 106d, 108d, 110d.
- the drive unit 30d is non-rotatably connected to part of the planetary gear stage 110d.
- FIG 19 12 shows an alternative exemplary 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 pivotably mounted about axes of rotation 244e, 246e.
- the operating elements 218e, 220e have a disc-shaped basic shape.
- the first operating element 218e not shown in detail, is connected to a planetary gear via a mechanism that appears sensible to a person skilled in the art.
- a first translation and a second translation can be set by means of the first operating element 218e.
- the second operating element 220e is connected to a control element, not shown in more detail, via a mechanism that appears sensible to a person skilled in the art.
- a screwing mode, a drilling mode and an impact drilling mode can be set using the second operating element 220e.
- a chisel mode could be adjustable.
- the protective device 226e has a freewheeling area 248e delimited by the first operating element 218e.
- the protective device 226e has a freewheeling area 250e delimited by the second operating element 220e.
- the freewheel area 248e of the first operating element 218e enables the screwing mode, the drilling mode and the hammer drilling mode to be set when a second gear ratio is set.
- the freewheel area 250e of the second operating element 220e enables the screwing mode and the drilling mode to be set when a first gear ratio is set.
- the guard 226e prevents the first gear from being adjusted. With the first ratio set, the guard 226e prevents the hammer drilling mode from being set.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Drilling And Boring (AREA)
- Percussive Tools And Related Accessories (AREA)
Description
Es ist in
In der
Aus der
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In der
Die Erfindung geht aus von einer Handwerkzeugvorrichtung mit einem Schlagwerk, das zumindest einen Schläger und eine Kurvenführung aufweist, die zumindest bei einem Schlagbohrbetrieb den Schläger antreibt. Die erfindungsgemäße Handwerkzeugvorrichtung umfasst die Merkmale des Anspruchs 1.The invention is based on a hand tool device with an impact mechanism which has at least one impactor and a cam guide which drives the impactor at least during percussion drilling operation. The hand tool device according to the invention comprises the features of
Es wird erfindungsgemäß vorgeschlagen, dass der Schläger zumindest einen Teil der Kurvenführung aufweist. Unter einem "Schlagwerk" soll insbesondere eine Vorrichtung verstanden werden, die dazu vorgesehen ist, einen Schlagimpuls zu erzeugen und insbesondere in Richtung eines Einsatzwerkzeugs abzugeben. Vorzugsweise leitet das Schlagwerk den Schlagimpuls zumindest bei einem Schlagbohrbetrieb vorteilhaft über eine Werkzeugspindel und/oder insbesondere über ein Werkzeugfutter der Handwerkzeugvorrichtung an das Einsatzwerkzeug weiter. Das Schlagwerkwerk ist erfindungsgemäß dazu vorgesehen, eine Rotationsbewegung in eine insbesondere translatorische Schlagbewegung zu übersetzen. Unter "vorgesehen" soll insbesondere speziell ausgelegt und/oder ausgestattet verstanden werden. Insbesondere soll unter dem Begriff "Schläger" ein Mittel verstanden wer-den, das zumindest bei einem Schlagbohrbetrieb insbesondere translatorisch beschleunigt wird und einen bei der Beschleunigung aufgenommenen Impuls als Schlagimpuls in Richtung des Einsatzwerkzeugs abgibt. Vorzugsweise ist der Schläger einstückig aus-gebildet. Alternativ könnte der Schläger mehrstückig ausgebildet sein. insbesondere soll unter einer "Kurvenführung" eine Vorrichtung verstanden werden, die eine Rotationsenergie zu einer Schlagerzeugung zumindest mittels einer speziell geformten Führungsfläche, an der zumindest bei einem Schlagbohrbetrieb ein Verbindungsmittel entlangläuft, in eine lineare Bewegungsenergie des Schlägers übersetzt. Vorzugsweise weist das Schlagwerk eine Schlagwerkfeder auf, die die lineare Bewegungsenergie des Schlägers zur Schlagerzeugung speichert. Vorzugsweise ist die speziell geformte Fläche eine Fläche, die eine Führungskurve der Kurvenführung begrenzt. Unter einem "Verbindungsmittel" soll insbesondere ein Mittel verstanden werden, das eine mechanische Kopplung zwischen zumindest einem, bei einem Schlagbohrbetrieb rotierend bewegten Teil des Schlagwerks, insbesondere einer Schlagwerkspindel, und dem insbesondere linear bewegten Schläger herstellt. Insbesondere soll unter einer "Führungskurve" ein von der Führungsfläche begrenzter Bereich verstanden werden, in dem das Verbindungsmittel in zumindest einem Betriebszustand läuft. Unter einer "Schlagwerkfeder" soll insbesondere eine Feder verstanden werden, die in zumindest einem Betriebszustand zumindest einen Teil einer Schlagenergie speichert. Insbesondere soll unter "abstützen" verstanden werden, dass ein Teil der Schlagwerkfeder relativ zu dem Schläger oder ein Teil der Schlagwerkfeder relativ zu einem Handwerkzeuggehäuse unbeweglich angeordnet ist. Die Schlagwerkfeder ist als eine, dem Fachmann als sinnvoll erscheinende Feder ausgebildet, vorzugsweise jedoch als eine Schraubenfeder. Unter "antreiben" soll in diesem Zusammenhang insbesondere verstanden werden, dass die Kurvenführung eine Energie zur Schlagerzeugung auf den Schläger überträgt. Unter der Wendung, dass "der Schläger zumindest einen Teil der Kurvenführung aufweist", soll insbesondere verstanden werden, dass der Schläger eine Fläche aufweist, auf den das Verbindungsmittel die Energie zu einer Erzeugung der Schlagbewegung direkt überträgt. Vorzugsweise ist der Teil der Kurvenführung, den der Schläger aufweist, als eine Fläche ausgebildet, die das Verbindungsmittel relativ zum Schläger ortsfest befestigt. Erfindungsgemäß umfasst der Teil der Kurvenführung, den der Schläger aufweist, eine von der Fläche begrenzte Befestigungsaussparung, die das Verbindungsmittel relativ zum Schläger ortsfest befestigt. Vorteilhaft ist der Schläger dazu vorgesehen, ein Verbindungsmittel zu befestigen, das bei einem Betrieb den Teil der Kurvenführung und einen weiteren Teil der Kurvenführung, insbesondere die Führungskurve, verbindet. Vorzugsweise sind das Verbindungsmittel und der Schläger ungefedert verbunden. Das heißt insbesondere, dass zwischen dem Verbindungsmittel und dem Schläger wirkungsmäßig keine Feder angeordnet ist. Des Weiteren könnte alternativ der Teil der Kurvenführung, den der Schläger aufweist, als eine Führungskurve ausgebildet sein. Unter "ortsfest" soll insbesondere verstanden werden, dass eine Symmetrieachse und/oder ein Mittelpunkt des Verbindungsmittels relativ zum Schläger bei einem Schlagbetrieb zumindest im Wesentlichen unbewegt ist. Durch die erfindungsgemäße Ausgestaltung der Handwerkzeugvorrichtung kann ein besonders kleines, leichtes und dennoch leistungsfähiges Schlagwerk bereitgestellt werden. insbesondere kann auf ein Taumellager oder einen Kipphebel vorteilhaft verzichtet werden.It is proposed according to the invention that the racquet has at least part of the curve guide. A "percussion mechanism" is to be understood in particular as a device which is intended to generate an impact impulse and in particular to emit it in the direction of an application tool. The hammer mechanism preferably forwards the hammer pulse to the insert tool, at least during hammer drilling operation, advantageously via a tool spindle and/or in particular via a tool chuck of the hand tool device. According to the invention, the percussion mechanism is intended to translate a rotational movement into a particularly translatory percussion movement. “Provided” is to be understood in particular as being specially designed and/or equipped. In particular, the term "beater" should be understood to mean a means that is accelerated at least in a percussion drilling operation, in particular translationally, and emits an impulse picked up during the acceleration as an impact impulse in the direction of the insert tool. The racquet is preferably constructed in one piece. Alternatively, the racquet could be constructed in several pieces be. In particular, a "curved guide" should be understood to mean a device that translates rotational energy for generating an impact into linear kinetic energy of the impactor, at least by means of a specially shaped guide surface along which a connecting means runs, at least during percussion drilling. The hammer mechanism preferably has a hammer mechanism spring, which stores the linear kinetic energy of the hammer to generate an impact. Preferably, the specially shaped surface is a surface that delimits a guide curve of the curve guide. A “connecting means” is to be understood in particular as meaning a means that creates a mechanical coupling between at least one part of the impact mechanism that rotates during percussion drilling operation, in particular a percussion mechanism spindle, and the in particular linearly moving hammer. In particular, a “guide curve” should be understood to mean an area delimited by the guide surface, in which the connecting means runs in at least one operating state. A "impact mechanism spring" is to be understood in particular as a spring which stores at least part of an impact energy in at least one operating state. In particular, “support” should be understood to mean that a part of the striking mechanism spring is arranged immovably relative to the hammer or a part of the striking mechanism spring is arranged immovably relative to a hand tool housing. The hammer mechanism spring is designed as a spring that appears sensible to a person skilled in the art, but preferably as a helical spring. In this context, “drive” is to be understood in particular as meaning that the curve guide transfers energy to the racquet to generate an impact. The expression that “the racquet has at least part of the curve guide” should be understood in particular to mean that the racquet has a surface to which the connecting means directly transmits the energy for generating the striking movement. Preferably, the part of the curve guide which the racquet has is formed as a surface which fixes the connecting means in place relative to the racquet. According to the invention, the part of the curved guide which the racquet has comprises a fastening recess which is delimited by the surface and which fastens the connecting means in a stationary manner relative to the racquet. Advantageously, the racquet is provided to attach a connecting means which, during operation, connects the part of the curved guide and a further part of the curved guide, in particular the guide curve. Preferably, the connecting means and the racquet are connected in an unsprung manner. This means in particular that no spring is arranged between the connecting means and the racquet in terms of effect. Furthermore, alternatively, the part of the curve guide, the racket has, be designed as a guide curve. “Stationary” is to be understood in particular as meaning that an axis of symmetry and/or a center point of the connecting means is at least essentially stationary relative to the racquet during a striking operation. The design of the hand tool device according to the invention makes it possible to provide a particularly small, light and yet powerful impact mechanism. in particular, a wobble bearing or a rocker arm can advantageously be dispensed with.
In einer weiteren bevorzugten Ausgestaltung wird vorgeschlagen, dass die Kurvenführung einen Schlagfreilaufbereich aufweist, wodurch bei einer kurzen Baulänge eine große Schlagenergie und ein vorteilhaft geringer Verschleiß erreicht werden können. Unter einem "Schlagfreilaufbereich" soll insbesondere ein Bereich der Führungskurve der Kurvenführung verstanden werden, in dem das Verbindungsmittel angeordnet ist, wenn die Schlagwerkfeder den Schläger in Schlagrichtung beschleunigt. Vorzugsweise ist der Schlagfreilaufbereich so breit ausgebildet, dass das Verbindungsmittel den Schlagfreilaufbereich auf unterschiedlichen Bahnen durchlaufen kann. Vorzugsweise bewirkt der Schlagfreilaufbereich zumindest bei dem Schlagbohrbetrieb keine Kraft auf den Schläger.In a further preferred embodiment, it is proposed that the curve guide has an impact-free running area, as a result of which high impact energy and advantageously low wear can be achieved with a short overall length. A "impact freewheel area" is to be understood in particular as an area of the guide curve of the curved guide in which the connecting means is arranged when the striking mechanism spring accelerates the beater in the direction of impact. The non-impact area is preferably designed so wide that the connecting means can run through the non-impact area on different paths. Preferably, at least in the hammer drilling operation, the impact freewheel area does not cause any force on the hammer.
Des Weiteren wird vorzugsweise vorgeschlagen, dass die Kurvenführung einen Schlagaufzugsbereich aufweist, wodurch ein vorteilhafter Betrieb, insbesondere mit geringen Vibrationen, erreicht werden kann. insbesondere soll unter einem "Schlagaufzugsbereich" ein Bereich der Führungskurve der Kurvenführung verstanden werden, der den Schläger zumindest bei einem Schlagbohrbetrieb insbesondere relativ zu dem Handwerkzeuggehäuse entgegen der Schlagrichtung bewegt. Vorzugsweise komprimiert die durch den Schlagaufzugsbereich verursachte Bewegung des Schlägers entgegen der Schlagrichtung die Schlagwerkfeder. Vorzugsweise weist die Führungsfläche des Schlagaufzugsbereichs eine Steigung relativ zu der Schlagrichtung zwischen 5 Grad und 35 Grad, vorteilhaft zwischen 10 Grad und 25 Grad, auf.Furthermore, it is preferably proposed that the curve guide has an impact elevator area, as a result of which advantageous operation, in particular with low vibrations, can be achieved. In particular, an "impact lift area" should be understood to mean an area of the guide curve of the cam guide that moves the hammer at least during percussion drilling operation, in particular relative to the hand tool housing, counter to the direction of impact. The movement of the hammer caused by the hammer winding area against the direction of impact preferably compresses the hammer mechanism spring. Preferably, the guide surface of the impact elevator area has an incline relative to the direction of impact of between 5 degrees and 35 degrees, advantageously between 10 degrees and 25 degrees.
Erfindungsgemäß wird vorgeschlagen, dass die Kurvenführung eine Montageaussparung aufweist, wodurch eine vorteilhafte Montage und eine besonders kleine Ausgestaltung möglich sind. Unter einer "Montageaussparung" soll ein von der Schlagwerkspindel begrenzter Bereich verstanden werden, durch den das Verbindungsmittel bei der Montage in die Führungskurve eingebracht wird.According to the invention, it is proposed that the curve guide has an assembly cutout, as a result of which advantageous assembly and a particularly small configuration are possible. An “assembly recess” should be understood to mean an area delimited by the percussion mechanism spindle, through which the connecting means is introduced into the guide curve during assembly.
Erfindungsgemäß wird vorgeschlagen, dass das Schlagwerk eine Schlagwerkspindel umfasst, die zumindest einen Teil der Kurvenführung aufweist, wodurch eine kompakte Ausgestaltung erreicht werden kann. Unter einer "Schlagwerkspindel" soll insbesondere eine Welle verstanden werden, die eine Rotationsbewegung von einem Planetengetriebe der Handwerkzeugvorrichtung zu der Kurvenführung überträgt. Vorzugsweise ist die Schlagwerkspindel als eine Hohlwelle ausgebildet.According to the invention, it is proposed that the percussion mechanism comprises a percussion mechanism spindle which has at least part of the cam guide, as a result of which a compact configuration can be achieved. A "percussion mechanism spindle" is to be understood in particular as a shaft which transmits a rotational movement from a planetary gear of the hand tool device to the cam guide. The percussion mechanism spindle is preferably designed as a hollow shaft.
Weiterhin wird vorzugsweise vorgeschlagen, dass die Schlagwerkspindel eine Führungskurve der Kurvenführung aufweist, wodurch eine einfache Fertigung möglich ist.Furthermore, it is preferably proposed that the percussion mechanism spindle has a guide curve of the curve guide, as a result of which simple production is possible.
In einer vorteilhaften Ausbildung der Erfindung wird vorgeschlagen, dass der Schläger die Schlagwerkspindel auf wenigstens einer Ebene zumindest im Wesentlichen umschließt, wodurch eine Ausgestaltung mit geringem Volumen und Gewicht möglich ist. insbesondere soll unter der Wendung "auf wenigstens einer Ebene zumindest im Wesentlichen umschließen" verstanden werden, dass von einer Achse der Schlagwerkspindel ausgehende Strahlen, die auf der Ebene angeordnet sind, den Schläger über einem Winkelbereich von wenigstens 180 Grad, vorteilhaft wenigstens 270 Grad schneiden. Besonders vorteilhaft umschließt der Schläger die Schlagwerkspindel um 360 Grad.In an advantageous embodiment of the invention, it is proposed that the hammer at least essentially encloses the hammer mechanism spindle on at least one level, as a result of which an embodiment with a small volume and weight is possible. In particular, the phrase “at least substantially encloses on at least one plane” should be understood to mean that rays emanating from an axis of the percussion mechanism spindle, which are arranged on the plane, intersect the beater over an angular range of at least 180 degrees, advantageously at least 270 degrees. The bat encloses the striking mechanism spindle by 360 degrees, which is particularly advantageous.
Erfindungsgemäß wird vorgeschlagen, dass das Schlagwerk ein Verbindungsmittel aufweist, das in zumindest einem Betriebszustand eine Bewegung insbesondere von der Schlagwerkspindel auf den Schläger überträgt, wodurch ein geringer Verschleiß, eine effektive Fertigung und eine einfache Montage erreicht werden können.According to the invention, it is proposed that the hammer mechanism has a connecting means which, in at least one operating state, transmits a movement, in particular from the hammer mechanism spindle to the hammer, so that less wear, effective manufacture and simple assembly can be achieved.
Des Weiteren wird vorzugsweise vorgeschlagen, dass die Handwerkzeugvorrichtung eine Werkzeugspindel umfasst, die der Schläger auf zumindest einer Ebene zumindest im Wesentlichen umschließt. Unter einer "Werkzeugspindel" soll insbesondere eine Welle verstanden werden, die eine Rotationsbewegung von dem Planetengetriebe zu dem Werkzeugfutter überträgt. Vorzugsweise ist die Werkzeugspindel als eine Vollwelle ausgebildet. Alternativ könnte die Werkzeugspindel als eine Hohlwelle ausgebildet sein.Furthermore, it is preferably proposed that the hand tool device comprises a tool spindle, which the hammer at least essentially encloses on at least one level. A "tool spindle" is to be understood in particular as a shaft which transmits a rotational movement from the planetary gear to the tool chuck. The tool spindle is preferably designed as a solid shaft. Alternatively, the tool spindle could be designed as a hollow shaft.
Ferner wird vorzugsweise vorgeschlagen, dass die Werkzeugspindel zumindest im Wesentlichen koaxial zur Schlagwerkspindel angeordnet ist, wodurch eine besonders kompakte Ausgestaltung möglich ist. Insbesondere soll unter der Wendung "zumindest im Wesentlichen koaxial angeordnet" verstanden werden, dass eine Drehachse der Werkzeugspindel und eine Drehachse der Schlagwerkspindel an zumindest einem Punkt weniger als 20 mm, vorteilhaft weniger als 10 mm, voneinander beabstandet angeordnet sind und einen Ausrichtungsunterschied von weniger als 15 Grad, vorteilhaft weniger als 5 Grad, zueinander aufweisen. Besonders bevorzugt sind die Drehachse der Werkzeugspindel und der Drehachse der Schlagwerkspindel auf einer gleichen Geraden angeordnet und gleich ausgerichtet.Furthermore, it is preferably proposed that the tool spindle is arranged at least essentially coaxially with the percussion mechanism spindle, as a result of which a particularly compact configuration is possible. In particular, the phrase “arranged at least essentially coaxially” is to be understood to mean that an axis of rotation of the tool spindle and an axis of rotation of the percussion mechanism spindle are arranged at a distance of less than 20 mm, advantageously less than 10 mm, from one another at at least one point and have an alignment difference of less than 15 degrees, advantageously less than 5 degrees, to each other. The axis of rotation of the tool spindle and the axis of rotation of the percussion mechanism spindle are particularly preferably arranged on the same straight line and aligned in the same way.
Zudem wird vorzugsweise vorgeschlagen, dass das Schlagwerk eine Schlägerführung aufweist, die den Schläger drehfest lagert, wodurch eine konstruktiv einfache Kurvenführung möglich ist. Unter einer "Schlägerführung" soll insbesondere eine Vorrichtung verstanden werden, die den Schläger parallel zu der Schlagrichtung bewegbar lagert. Insbesondere soll unter der Wendung "drehfest lagern" verstanden werden, dass die Schlägerführung insbesondere jeder Drehbewegung des Schlägers relativ zu einem Handwerkzeuggehäuse entgegenwirkt.In addition, it is preferably proposed that the hammer mechanism has a hammer guide which supports the hammer in a rotationally fixed manner, as a result of which a constructively simple curve guidance is possible. A “racquet guide” is to be understood in particular as a device that supports the racquet so that it can move parallel to the direction of impact. In particular, the phrase “rotatably mounted” should be understood to mean that the hammer guide counteracts in particular any rotational movement of the hammer relative to a hand tool housing.
Weiterhin wird vorzugsweise vorgeschlagen, dass die Handwerkzeugvorrichtung ein Handwerkzeuggehäuse umfasst, wobei das Schlagwerk eine Schlagwerkfeder aufweist, die an dem Schläger und an dem Handwerkzeuggehäuse abgestützt ist, wodurch eine besonders geringe axiale Baulänge erreicht werden kann. Insbesondere soll unter einem "Handwerkzeuggehäuse" ein Gehäuse verstanden werden, das einen Innenraum aufweist, in dem zumindest das Schlagwerk, das Planetengetriebe und eine Antriebseinheit des Handwerkzeuggehäuses angeordnet sind. Vorzugsweise verbindet das Handwerkzeuggehäuse zumindest das Schlagwerk, das Planetengetriebe und eine Antriebseinheit des Handwerkzeuggehäuses zumindest teilweise miteinander.Furthermore, it is preferably proposed that the hand tool device comprises a hand tool housing, the hammer mechanism having a hammer mechanism spring which is supported on the hammer and on the hand tool housing, as a result of which a particularly small axial overall length can be achieved. In particular, a “hand tool housing” should be understood to mean a housing that has an interior space in which at least the percussion mechanism, the planetary gear and a drive unit of the hand tool housing are arranged. The hand-held tool housing preferably at least partially connects at least the percussion mechanism, the planetary gear and a drive unit of the hand-held tool housing to one another.
In einer vorteilhaften Ausbildung der Erfindung wird vorgeschlagen, dass das Schlagwerk die erste Kurvenführung und eine zweite Kurvenführung aufweist, wodurch ein geringer Verschleiß und eine hohe Laufruhe möglich sind.In an advantageous embodiment of the invention, it is proposed that the percussion mechanism has the first cam guide and a second cam guide, as a result of which less wear and very smooth running are possible.
Des Weiteren geht die Erfindung aus von einem Handwerkzeug mit einer erfindungsgemäßen Handwerkzeugvorrichtung. Vorzugsweise ist das Handwerkzeug dazu vorgesehen, das Einsatzwerkzeug in einem Schraubmodus, in einem Bohrmodus, in einem Schraubbohrmodus und insbesondere in einem Meißelmodus anzutreiben.Furthermore, the invention is based on a hand tool with a hand tool device according to the invention. The hand tool is preferably provided for to drive the application tool in a screw mode, in a drill mode, in a screw drill mode and in particular in a chisel mode.
Weitere Vorteile ergeben sich aus der folgenden Zeichnungsbeschreibung. In der Zeichnung sind fünf Ausführungsbeispiele der Erfindung dargestellt. Die Zeichnung, die Beschreibung und die Ansprüche enthalten zahlreiche Merkmale in Kombination.Further advantages result from the following description of the drawings. Five exemplary embodiments of the invention are shown in the drawing. The drawing, the description and the claims contain numerous features in combination.
Es zeigen:
- Fig. 1
- einen Schnitt eines Handwerkzeugs mit einer erfindungsgemäßen Handwerkzeugvorrichtung,
- Fig. 2
- einen teilweise freigestellten Schnitt durch ein Schlagwerk und ein Planetengetriebe der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 3
- eine erste Schnittfläche A des Schlagwerks der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 4
- eine zweite Schnittfläche B des Schlagwerks der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 5
- eine perspektivische Darstellung einer Schlagwerkspindel des Schlagwerks der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 6
- eine perspektivische Darstellung eines Schlägers des Schlagwerks der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 7
- eine Schnittfläche C einer ersten Planetengetriebestufe und einer ersten Schlagabschaltvorrichtung der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 8
- eine Schnittfläche D eines Steuerelements und einer zweiten Schlagabschaltvorrichtung der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 9
- eine perspektivische Schnittdarstellung eines Teils der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 10
- eine Schnittfläche E einer Spindelblockiervorrichtung der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 11
- eine Schnittfläche F durch Blockiermittel der Spindelblockiervorrichtung der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 12
- eine Schnittfläche G einer zweiten Planetengetriebestufe der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 13
- eine Schnittfläche H einer dritten Planetengetriebestufe der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 14
- eine Schnittfläche I einer vierten Planetengetriebestufe der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 15
- eine schematische Darstellung einer Bedienvorrichtung und einer Schutzvorrichtung der Handwerkzeugvorrichtung aus
Figur 1 , - Fig. 16
- ein alternatives Ausführungsbeispiel einer ersten Schlagabschaltvorrichtung einer erfindungsgemäßen Handwerkzeugvorrichtung,
- Fig. 17
- ein weiteres Ausführungsbeispiel einer ersten Schlagabschaltvorrichtung einer erfindungsgemäßen Handwerkzeugvorrichtung,
- Fig. 18
- ein alternatives Ausführungsbeispiel einer Schlagschaltfeder einer erfindungsgemäßen Handwerkzeugvorrichtung und
- Fig. 19
- ein alternatives Ausführungsbeispiel einer Bedienvorrichtung und einer Schutzvorrichtung einer erfindungsgemäßen Handwerkzeugvorrichtung.
- 1
- a section of a hand tool with a hand tool device according to the invention,
- 2
- a partially cropped section through a percussion mechanism and a planetary gear of the hand tool device
figure 1 , - 3
- a first cut surface A of the hammer mechanism of the hand tool device
figure 1 , - 4
- a second cut surface B of the hammer mechanism of the hand tool device
figure 1 , - figure 5
- a perspective view of an impact mechanism spindle of the impact mechanism of the hand tool device
figure 1 , - 6
- a perspective view of a bat of the impact mechanism of the hand tool device
figure 1 , - 7
- an interface C of a first planetary gear stage and a first impact shut-off device of the hand tool device
figure 1 , - 8
- an interface D of a control element and a second impact shut-off device of the hand tool device
figure 1 , - 9
- a perspective sectional view of a part of the hand tool device
figure 1 , - 10
- a cut surface E of a spindle locking device of the hand tool device
figure 1 , - 11
- a cut surface F through blocking means of the spindle blocking device of the hand tool device
figure 1 , - 12
- a sectional area G of a second planetary gear stage of the hand tool device
figure 1 , - 13
- a sectional area H of a third planetary gear stage of the hand tool device
figure 1 , - 14
- a sectional area I of a fourth planetary gear stage of the hand tool device
figure 1 , - 15
- a schematic representation of an operating device and a protective device of the hand tool device
figure 1 , - 16
- an alternative embodiment of a first impact shut-off device of a hand tool device according to the invention,
- 17
- a further exemplary embodiment of a first impact shut-off device of a hand tool device according to the invention,
- 18
- an alternative embodiment of an impact switch spring of a hand tool device according to the invention and
- 19
- an alternative embodiment of an operating device and a protective device of a hand tool device according to the invention.
Die Werkzeugführungseinheit 20a umfasst ein Werkzeugfutter 36a und eine Werkzeugspindel 38a. Das Werkzeugfutter 36a befestigt bei einem Arbeitsvorgang ein hier nicht dargestelltes Einsatzwerkzeug, beispielsweise einen Bohrer bzw. ein Schraubbit. Das Werkzeugfutter 36a befestigt das Einsatzwerkzeug kraftschlüssig. Das Werkzeugfutter 36a weist drei von einem Bediener bewegbar befestigte Spannbacken auf, die bei einem Arbeitsvorgang das Einsatzwerkzeug befestigen. Zudem befestigt das Werkzeugfutter 36a das Einsatzwerkzeug bei einem Arbeitsvorgang axial unbeweglich gegenüber dem Werkzeugfutter 36a und insbesondere der Werkzeugspindel 38a. Ein Teil des Werkzeugfutters 36a und die Werkzeugspindel 38a sind relativ zueinander unbeweglich miteinander verbunden. Hier sind das Werkzeugfutter 36a und die Werkzeugspindel 38a miteinander verschraubt. Die Handwerkzeugvorrichtung 12a weist ein Lagermittel 40a auf, das die Werkzeugspindel 38a auf einer dem Werkzeugfutter 36a zugewandten Seite lagert. Das Lagermittel 40a lagert die Werkzeugspindel 38a axial verschiebbar. Das Lagermittel 40a ist axial fest mit der Werkzeugspindel 38a verbunden. Das Lagermittel 40a ist axial bewegbar in dem Handwerkzeuggehäuse 14a gelagert. Die Handwerkzeugvorrichtung 12a weist ein weiteres Lagermittel 41a auf, das die Werkzeugspindel 38a auf einer dem Planetengetriebe 28a zugewandten Seite lagert. Das Lagermittel 41a ist als ein Wälzlager, hier als ein Nadellager, ausgebildet, wodurch eine spielarme Lagerung möglich ist. Das Lagermittel 41a lagert die Werkzeugspindel 38a axial verschiebbar. Einer Schlagwerkspindel 46a umschließt das Lagermittel 41a. Das Lagermittel 41a ist wirkungsmäßig zwischen der Werkzeugspindel 38a und der Schlagwerkspindel 46a angeordnet.The
Die Werkzeugspindel 38a umfasst eine Schlagfläche 42a, auf die bei einem Schlagbohrbetrieb ein Schläger 44a des Schlagwerks 22a schlägt. Der Schläger 44a weist eine Masse auf, die maximal zwei Drittel so groß ist wie eine Masse der Werkzeugführungseinheit 20a. Hier ist die Masse des Schlägers 44a weniger als halb so groß wie die Masse der Werkzeugführungseinheit 20a. Die Masse des Schlägers 44a beträgt etwa 45 % der Masse der Werkzeugführungseinheit 20a.The
In der
Die
Die Schlagwerkfeder 48a beschleunigt den Schläger 44a vor einem Schlag in Schlagrichtung 54a. Dazu stützt das Handwerkzeuggehäuse 14a die Schlagwerkfeder 48a auf einer dem Schläger 44a abgewandten Seite ab. Die Schlagwerkfeder 48a drückt direkt gegen den Schläger 44a. Der Schläger 44a weist eine Federbefestigung 60a auf. Die Federbefestigung 60a ist als eine ringförmige Vertiefung ausgebildet.
Die Schlagwerkspindel 46a ist als eine Hohlwelle ausgebildet. Das Planetengetriebe 28a treibt die Schlagwerkspindel 46a an. Dazu weist die Schlagwerkspindel 46a auf einer dem Werkzeugfutter 36a abgewandten Seite eine Verzahnung 76a auf. Die Führungskurven 66a, 68a weisen jeweils einen Schlagfreilaufbereich 78a, 80a, einen Schlagaufzugsbereich 82a, 84a und eine Montageaussparung 86a, 88a auf. Bei einer Montage werden die Verbindungsmittel 70a, 72a durch die Montageaussparungen 86a, 88a in die Befestigungsaussparungen 74a des Schlägers 44a eingebracht. Die Schlagwerkspindel 46a rotiert bei dem Schlagbohrbetrieb in Schlagrichtung 54a gesehen im Uhrzeigersinn. Die Schlagaufzugsbereiche 82a, 84a sind spiralförmig ausgebildet. Sie erstrecken sich um 180 Grad um eine Rotationsachse 90a der Schlagwerkspindel 46a. Die Schlagaufzugsbereiche 82a, 84a bewegen die Verbindungsmittel 70a, 72a und damit den Schläger 44a bei dem Schlagbohrbetrieb entgegen der Schlagrichtung 54a. Somit weist das Schlagwerk 22a die Verbindungsmittel 70a, 72a auf, welche in zumindest einem Betriebszustand eine Bewegung von der Schlagwerkspindel 46a auf den Schläger 44a übertragen.
Die Schlagfreilaufbereiche 78a, 80a verbinden je zwei Enden 92a, 94a, 96a, 98a der Schlagaufzugsbereiche 82a, 84a. Die Schlagfreilaufbereiche 78a, 80a erstrecken sich um 180 Grad um eine Rotationsachse 90a der Schlagwerkspindel 46a. Die Schlagfreilaufbereiche 78a, 80a weisen je eine Schlagflanke 100a, 102a auf, die, von einem dem Planetengetriebe 28a zugewandten Ende 94a, 96a des Schlagaufzugsbereichs 82a ausgehend, in etwa parallel zu der Schlagrichtung 54a verläuft. Nachdem die Verbindungsmittel 70a, 72a in die Schlagfreilaufbereiche 78a, 80a eindringen, beschleunigt die Schlagwerkfeder 48a den Schläger 44a und die Verbindungsmittel 70a, 72a in Schlagrichtung 54a. Dabei bewegen sich die Verbindungsmittel 70a, 72a durch die Schlagfreilaufbereiche 78a, 80a, ohne eine axiale Kraft zu erfahren, bis der Schläger 44a auf die Schlagfläche 42a trifft. Die Kurvenführungen 62a, 64a sind um 180 Grad um die Rotationsachse 90a versetzt angeordnet. Die Kurvenführungen 62a, 64a sind in axialer Richtung hintereinander angeordnet.The impact-
Das Planetengetriebe 28a weist die erste Planetengetriebestufe 104a, eine zweite Planetengetriebestufe 106a, eine dritte Planetengetriebestufe 108a und eine vierte Planetengetriebestufe 110a auf.
Die erste Schlagabschaltvorrichtung 24a fixiert bei einem Schlagbohrbetrieb das Hohlrad 116a der ersten Planetengetriebestufe 104a relativ zu dem Handwerkzeuggehäuse 14a unbeweglich. Die erste Schlagabschaltvorrichtung 24a ist dazu vorgesehen, die Schlägerantriebsvorrichtung 50a bei einer ersten, rechtslaufenden Bohrrotationsrichtung einzuschalten und die Schlägerantriebsvorrichtung 50a bei einer zweiten, linkslaufenden Bohrrotationsrichtung selbstständig abzuschalten. Die erste Schlagabschaltvorrichtung 24a wirkt auf das Hohlrad 116a der ersten Planetengetriebestufe 104a. Die erste Schlagabschaltvorrichtung 24a blockiert das Hohlrad 116a der ersten Planetengetriebestufe 104a bei der ersten, rechtslaufenden Bohrrotationsrichtung. Die erste Schlagabschaltvorrichtung 24a gibt das Hohlrad 116a der ersten Planetengetriebestufe 104a bei der zweiten, linkslaufenden Bohrrotationsrichtung frei, so dass es sich drehen kann. Dazu weist die erste Schlagabschaltvorrichtung 24a drei Klemmmechanismen 122a auf. Die Klemmmechanismen 122a umfassen jeweils ein Blockiermittel 124a, eine erste Klemmfläche 126a, eine zweite Klemmfläche 128a und Freilaufflächen 130a. Das Blockiermittel 124a ist als eine Walze ausgebildet. Die erste Klemmfläche 126a bildet einen außenliegenden Bereich einer Oberfläche des Hohlrads 116a der ersten Planetengetriebestufe 104a. Die zweite Klemmfläche 128a ist relativ zu dem Handwerkzeuggehäuse 14a unbeweglich angeordnet. Bei einem Betrieb in der ersten, rechtslaufenden Bohrrotationsrichtung klemmen die Blockiermittel 124a zwischen den ersten Klemmflächen 126a und der zweiten Klemmfläche 128a. Bei einem Betrieb in der zweiten, linkslaufenden Bohrrotationsrichtung führen die Freilaufflächen 130a die Blockiermittel 124a und verhindern ein Verklemmen.The first impact shut-off
Des Weiteren zeigt die
Ferner zeigen die
Die zweite Schlagabschaltvorrichtung 26a weist eine Schlagabschaltkupplung 142a auf. Die Schlagabschaltkupplung 142a ist teilweise einstückig mit dem Planetengetriebe 28a ausgebildet. Die Schlagabschaltkupplung 142a ist zwischen der ersten Planetengetriebestufe 104a und der zweiten Planetengetriebestufe 106a angeordnet. Die Schlagabschaltkupplung 142a weist ein erstes Kupplungselement 144a auf, das drehfest mit einem Planetenträger 114a der ersten Planetengetriebestufe 104a verbunden ist. Die Schlagabschaltkupplung 142a weist ein zweites Kupplungselement 146a auf, das drehfest mit einem Planetenträger 120a der zweiten Planetengetriebestufe 106a verbunden ist. In dem dargestellten Schraubmodus und dem Bohrmodus ist die Schlagabschaltkupplung 142a geöffnet. Bei einem Schlagbohrvorgang überträgt die Werkzeugspindel 38a eine axiale Kupplungskraft auf die Schlagabschaltkupplung 142a, wenn der Bediener ein Einsatzwerkzeug gegen ein Werkstück drückt. Die Kupplungskraft schließt die Schlagabschaltkupplung 142a. In der
Der Planetenträger 120a der zweiten Planetengetriebestufe 106a ist zweiteilig ausgebildet. Ein erstes Teil 150a des Planetenträgers 120a der zweiten Planetengetriebestufe 106a ist drehfest mit der Werkzeugspindel 38a verbunden. Das erste Teil 150a des Planetenträgers 120a ist axial verschiebbar mit der Werkzeugspindel 38a verbunden, wodurch der Planetenträgers 120a auch bei einem Schlag mit der Werkzeugspindel 38a drehgekoppelt bleibt. Somit ist das erste Teil 150a permanent mit der Werkzeugspindel 38a verbunden. Das erste Teil 150a des Planetenträgers 120a ist gegen die Schlagschaltfeder 148a axial verschiebbar gelagert. Ein zweites Teil 152a des Planetenträgers 120a der zweiten Planetengetriebestufe 106a ist drehfest mit dem ersten Teil 150a des Planetenträgers 120a verbunden. Das erste Teil 150a und das zweite Teil 152a des Planetenträgers 120a sind zueinander axial verschiebbar verbunden. Das erste Teil 150a und das zweite Teil 152a des Planetenträgers 120a sind permanent drehfest verbunden.The
Die
Die Drehmomentbegrenzungseinheit 34a umfasst ein Bedienelement 166a, ein Verstellelement 168a, Begrenzungsfedern 170a, nicht näher dargestellte Übertragungsmittel, erste Anschlagsflächen 172a, eine zweite Anschlagsfläche 174a und Begrenzungsmittel 176a. Das Bedienelement 166a ist ringförmig ausgebildet. Es schließt sich in Richtung des Planetengetriebes 28a an das Werkzeugfutter 36a an. Das Bedienelement 166a weist ein Einstellgewinde 178a auf, das mit einem Einstellgewinde 180a der Verstellelement 168a gekoppelt ist. Das Verstellelement 168a ist drehfest und axial verschiebbar gelagert. Eine Drehung des Bedienelements 166a verschiebt das Verstellelement 168a in axialer Richtung. Die Begrenzungsfedern 170a sind auf einer Seite an dem Verstellelement 168a abgestützt. Die Begrenzungsfedern 170a sind auf einer anderen Seite über die Übertragungsmittel an einem Anschlagsmittel 182a der Drehmomentbegrenzungseinheit 34a abgestützt. Eine Oberfläche des Anschlagsmittels 182a weist die erste Anschlagsflächen 172a auf. Das Anschlagsmittel 182a ist in dem Schraubmodus in axialer Richtung gegen die Begrenzungsfedern 170a bewegbar gelagert. Die zweite Anschlagsfläche 174a ist als ein Bereich einer Oberfläche eines Hohlrads 184a der zweite Planetengetriebestufe 106a ausgebildet. Die zweite Anschlagsfläche 174a weist muldenförmige Vertiefungen 186a auf. Die Begrenzungsmittel 176a sind kugelförmig ausgebildet. Die Begrenzungsmittel 176a sind in röhrenförmigen Aussparungen 188a in Schlagrichtung 54a verschiebbar gelagert.
Das Steuerelement 134a der Handwerkzeugvorrichtung 12a weist Abstützmittel 190a auf, die zumindest bei einem Bohrbetrieb eine axiale Bewegung des Anschlagsmittel 182a verhindern. Dazu stützen die Abstützmittel 190a das Anschlagsmittel 182a in axialer Richtung ab. Das Anschlagsmittel 182a weist Schraubaussparungen 192a auf, in die die Anschlagsmittel 182a bei einem insbesondere in der
Das Hohlrad 204a der dritten Planetengetriebestufe 108a ist wie in
Die Bedienvorrichtung 32a weist ein erstes Bedienelement 218a und ein zweites Bedienelement 220a auf. Das erste Bedienelement 218a ist auf einer dem Handgriff 18a abgewandten Seite des Handwerkzeuggehäuses 14a angeordnet. Es ist parallel zur axialen Richtung des Planetengetriebes 28a bewegbar gelagert. Das erstes Bedienelement 218a ist über ein Verstellmittel 222a der Bedienvorrichtung 32a in axialer Richtung mit dem Hohlrad 204a der dritten Planetengetriebestufe 108a verbunden. Das Hohlrad 204a der dritten Planetengetriebestufe 108a weist eine Nut 224a auf, in die das Verstellmittel 222a eingreift. Somit ist das Hohlrad 204a der dritten Planetengetriebestufe 108a mit dem Verstellmittel 222a, relativ zu dem Verstellmittel 222a axial drehbar, in axialer Richtung verbunden. Das Verstellmittel 222a ist federnd ausgebildet, wodurch die Übersetzung von einer Drehstellung des Hohlrad 204a der dritten Planetengetriebestufe 108a unabhängig verstellt werden kann. Wenn das erste Bedienelement 218a in Richtung des Werkzeugfutters 36a geschoben ist, ist die erste Übersetzung eingestellt. Wenn das zweite Bedienelement 220a von dem Werkzeugfutter 36a weggeschoben ist, ist die zweite Übersetzung eingestellt.The operating
Das zweite Bedienelement 220a ist auf einer dem Handgriff 18a abgewandten Seite des Handwerkzeuggehäuses 14a angeordnet. Das zweite Bedienelement 220a ist um eine Achse verschiebbar angeordnet, die parallel zu der axialen Richtung des Planetengetriebes 28a ausgerichtet ist. Das zweite Bedienelement 220a ist drehfest mit dem Steuerelement 134a der Handwerkzeugvorrichtung 12a verbunden. Mittels des zweiten Bedienelements 220a sind der Schraubmodus, der Bohrmodus und der Schlagbohrmodus einstellbar. Wenn das zweite Bedienelement 220a in Schlagrichtung 54a gesehen nach links geschoben ist, ist der Schlagbohrmodus eingestellt. Wenn das zweite Bedienelement 220a in Schlagrichtung 54a gesehen nach rechts geschoben ist, ist der Schraubmodus eingestellt. Wenn das zweite Bedienelement 220a in Schlagrichtung 54a gesehen mittig angeordnet ist, ist der Bohrmodus eingestellt.The
Die Antriebseinheit 30a ist als ein Elektromotor ausgebildet. Die Antriebseinheit 30a weist ein maximales Drehmoment auf, das ein maximales Werkzeugdrehmoment in der ersten Übersetzung von mehr als 15 Nm und in der zweiten Übersetzung von weniger als 15 m verursacht. Das maximale Werkzeugdrehmoment in der ersten Übersetzung beträgt 30 Nm. Das maximale Werkzeugdrehmoment in der zweiten Übersetzung beträgt 10 Nm. Das Werkzeugdrehmoment ist dabei nach der Norm DIN EN 60745 zu bestimmen.The
Die Schlagschaltfeder 148a der Handwerkzeugvorrichtung 12a öffnet bei einem Schlagbohrbetrieb die Schlagabschaltkupplung 142a, wenn der Bediener das Einsatzwerkzeug von dem Werkstück absetzt. Die Schlagschaltfeder 148a ist koaxial zu den Planetengetriebestufen 104a, 106a, 108a, 110a des Planetengetriebes 28a angeordnet. Die zweite Planetengetriebestufe 106a und die dritte Planetengetriebestufe 108a umschließen die Schlagschaltfeder 148a jeweils auf zumindest einer Ebene, die senkrecht zu der axialen Richtung des Planetengetriebes 28a ausgerichtet ist. Die zweite Planetengetriebestufe 106a und die dritte Planetengetriebestufe 108a sind jeweils wirkungsmäßig zwischen zumindest zwei weiteren Planetengetriebestufen 104a, 106a, 108a, 110a des Planetengetriebes 28a angeordnet. Der Planetenträger 120a der zweiten Planetengetriebestufe 106a stützt die Schlagschaltfeder 148a auf einer dem Werkzeugfutter 36a abgewandten Seite ab.The
In den
In der
In der
In der
Die Schutzvorrichtung 226e weist einen von dem ersten Bedienelement 218e begrenzten Freilaufbereich 248e auf. Die Schutzvorrichtung 226e weist einen von dem zweiten Bedienelement 220e begrenzten Freilaufbereich 250e auf. Der Freilaufbereich 248e des ersten Bedienelements 218e ermöglicht ein Einstellen des Schraubmodus, des Bohrmodus und des Schlagbohrmodus, wenn eine zweite Übersetzung eingestellt ist. Der Freilaufbereich 250e des zweiten Bedienelement 220e ermöglicht ein Einstellen des Schraubmodus und des Bohrmodus, wenn eine erste Übersetzung eingestellt ist. In dem Schlagbohrmodus verhindert die Schutzvorrichtung 226e ein Einstellen der ersten Übersetzung. Bei eingestellter erster Übersetzung verhindert die Schutzvorrichtung 226e ein Einstellen des Schlagbohrmodus.The
Claims (12)
- Hand-tool device having an impact mechanism (22a; 22b; 22c) which is intended for converting a rotational movement into an in particular translational striking movement and which has at least one striker (44a) and one cam guide (62a, 64a) which drives the striker (44a) at least during impact drilling operation, wherein the striker (44a) has at least a part of the cam guide (62a, 64a) and the impact mechanism (22a; 22b; 22c) comprises an impact-mechanism spindle (46a, 46c) which has at least a part of the cam guide (62a, 64a) and which has a connecting means (70a, 72a) which, in at least one operating state, transmits a movement to the striker (44a), wherein the cam guide (62a, 64a) comprises a fastening cutout (74a) which fastens the connecting means (70a, 72a) in a positionally fixed manner relative to the striker (44a),
characterized in that the cam guide (62a, 64a) comprises a fitting cutout (86a, 88a) in the impact-mechanism spindle (46a, 46c), by way of which the connecting means (70a, 72a) is introduced into the cam guide (62a, 64a) during the fitting. - Hand-tool device according to Claim 1, characterized in that the cam guide (62a, 64a) has an impact free-movement region (78a, 80a).
- Hand-tool device according to Claim 1 or 2, characterized in that the cam guide (62a, 64a) has an impact winding-up region (82a, 84a).
- Hand-tool device according to one of the preceding claims, characterized in that the impact-mechanism spindle (46a; 46c) has a guide curve (66a, 68a) of the cam guide (62a, 64a).
- Hand-tool device according to one of the preceding claims, characterized in that the striker (44a) at least substantially encloses the impact-mechanism spindle (46a; 46c) in at least one plane.
- Hand-tool device according to one of the preceding claims, characterized by a tool spindle (38a) which the striker (44a) at least substantially encloses in at least one plane.
- Hand-tool device according to one of the preceding claims, characterized in that the tool spindle (38a) is arranged at least substantially coaxially with respect to the impact-mechanism spindle (46a; 46c).
- Hand-tool device according to one of the preceding claims, characterized in that the impact mechanism (22a; 22b; 22c) has a striker guide (52a) which serves for rotationally fixed mounting of the striker (44a).
- Hand-tool device according to one of the preceding claims, characterized by a hand-tool housing (14a), wherein the impact mechanism (22a; 22b; 22c) has an impact-mechanism spring (48a) which is supported against the striker (44a) and against the hand-tool housing (14a).
- Hand-tool device according to one of the preceding claims, characterized in that the impact mechanism (22a; 22b; 22c) has the first cam guide (62a) and a second cam guide (64a).
- Hand-tool device according to one of the preceding claims, characterized in that the connecting means (70a, 72a) is of spherical form.
- Hand tool having a hand-tool device (12a) according to one of the preceding claims.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP21162272.5A EP3881974A1 (en) | 2011-12-27 | 2012-12-19 | Handheld tool device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011089910A DE102011089910A1 (en) | 2011-12-27 | 2011-12-27 | Hand tool device |
PCT/EP2012/076201 WO2013098167A1 (en) | 2011-12-27 | 2012-12-19 | Portable tool device |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP21162272.5A Division EP3881974A1 (en) | 2011-12-27 | 2012-12-19 | Handheld tool device |
EP21162272.5A Division-Into EP3881974A1 (en) | 2011-12-27 | 2012-12-19 | Handheld tool device |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2797721A1 EP2797721A1 (en) | 2014-11-05 |
EP2797721B1 true EP2797721B1 (en) | 2023-03-01 |
Family
ID=47504949
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12810244.9A Active EP2797721B1 (en) | 2011-12-27 | 2012-12-19 | Hand tool device |
EP21162272.5A Pending EP3881974A1 (en) | 2011-12-27 | 2012-12-19 | Handheld tool device |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP21162272.5A Pending EP3881974A1 (en) | 2011-12-27 | 2012-12-19 | Handheld tool device |
Country Status (7)
Country | Link |
---|---|
US (2) | US10315299B2 (en) |
EP (2) | EP2797721B1 (en) |
JP (2) | JP5847962B2 (en) |
CN (2) | CN107214664B (en) |
DE (1) | DE102011089910A1 (en) |
RU (1) | RU2635030C2 (en) |
WO (1) | WO2013098167A1 (en) |
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DE102013212753A1 (en) * | 2013-06-28 | 2014-12-31 | Robert Bosch Gmbh | Percussion device |
US11185015B2 (en) * | 2015-11-18 | 2021-11-30 | Techtronic Cordless Gp | Hedge trimmer with a dual gear setting |
CN107544426B (en) | 2016-06-27 | 2021-09-07 | 苏州宝时得电动工具有限公司 | Control method and device of electric tool and electric tool |
WO2018020283A1 (en) * | 2016-07-27 | 2018-02-01 | BEREGSZASZI, David | Motion conversion device |
CN106737039A (en) * | 2016-12-19 | 2017-05-31 | 上海浦江桥隧运营管理有限公司 | Rotary pneumatic pistol for rust removal |
TWI676534B (en) * | 2017-03-29 | 2019-11-11 | 美商米沃奇電子工具公司 | Punchdown tool |
CN210790852U (en) * | 2018-02-14 | 2020-06-19 | 苏州宝时得电动工具有限公司 | Hand tool and chuck accessory |
CN110153960A (en) * | 2018-02-14 | 2019-08-23 | 苏州宝时得电动工具有限公司 | Percussion tool |
CN112207758B (en) * | 2019-07-09 | 2022-06-14 | 苏州宝时得电动工具有限公司 | Power tool |
JP2024029802A (en) * | 2022-08-23 | 2024-03-07 | 株式会社Subaru | Tool drive device and manufacturing method of drilled item |
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- 2012-12-19 JP JP2014549428A patent/JP5847962B2/en active Active
- 2012-12-19 EP EP12810244.9A patent/EP2797721B1/en active Active
- 2012-12-19 CN CN201280064464.8A patent/CN104023919B/en active Active
- 2012-12-19 RU RU2014130905A patent/RU2635030C2/en active
- 2012-12-19 WO PCT/EP2012/076201 patent/WO2013098167A1/en active Application Filing
- 2012-12-19 US US14/368,469 patent/US10315299B2/en active Active
- 2012-12-19 EP EP21162272.5A patent/EP3881974A1/en active Pending
-
2015
- 2015-11-25 JP JP2015229860A patent/JP6053899B2/en active Active
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2019
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EP1690642A1 (en) * | 2005-02-10 | 2006-08-16 | BLACK & DECKER INC. | Hand-held hammer machine |
Also Published As
Publication number | Publication date |
---|---|
DE102011089910A1 (en) | 2013-06-27 |
US10960526B2 (en) | 2021-03-30 |
WO2013098167A1 (en) | 2013-07-04 |
JP6053899B2 (en) | 2016-12-27 |
CN104023919A (en) | 2014-09-03 |
EP2797721A1 (en) | 2014-11-05 |
US20150075828A1 (en) | 2015-03-19 |
JP5847962B2 (en) | 2016-01-27 |
JP2015503454A (en) | 2015-02-02 |
US20190255693A1 (en) | 2019-08-22 |
CN104023919B (en) | 2017-06-13 |
EP3881974A1 (en) | 2021-09-22 |
RU2635030C2 (en) | 2017-11-08 |
CN107214664A (en) | 2017-09-29 |
CN107214664B (en) | 2021-03-19 |
JP2016027952A (en) | 2016-02-25 |
US10315299B2 (en) | 2019-06-11 |
RU2014130905A (en) | 2016-02-20 |
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