EP0319813B1 - Handwerkzeugmaschine mit automatischer Arretierung der Arbeitsspindel - Google Patents

Handwerkzeugmaschine mit automatischer Arretierung der Arbeitsspindel Download PDF

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Publication number
EP0319813B1
EP0319813B1 EP19880119771 EP88119771A EP0319813B1 EP 0319813 B1 EP0319813 B1 EP 0319813B1 EP 19880119771 EP19880119771 EP 19880119771 EP 88119771 A EP88119771 A EP 88119771A EP 0319813 B1 EP0319813 B1 EP 0319813B1
Authority
EP
European Patent Office
Prior art keywords
power tool
hand power
tool according
working spindle
locking device
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.)
Expired - Lifetime
Application number
EP19880119771
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0319813A2 (de
EP0319813A3 (en
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
C&E Fein GmbH and Co
Original Assignee
C&E Fein GmbH and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by C&E Fein GmbH and Co filed Critical C&E Fein GmbH and Co
Publication of EP0319813A2 publication Critical patent/EP0319813A2/de
Publication of EP0319813A3 publication Critical patent/EP0319813A3/de
Application granted granted Critical
Publication of EP0319813B1 publication Critical patent/EP0319813B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B45/00—Means for securing grinding wheels on rotary arbors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B23/00—Portable grinding machines, e.g. hand-guided; Accessories therefor
    • B24B23/02—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor
    • B24B23/022—Spindle-locking devices, e.g. for mounting or removing the tool
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B41/00—Component parts such as frames, beds, carriages, headstocks
    • B24B41/04—Headstocks; Working-spindles; Features relating thereto
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B45/00—Means for securing grinding wheels on rotary arbors
    • B24B45/006—Quick mount and release means for disc-like wheels, e.g. on power tools
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/929—Tool or tool with support
    • Y10T83/9372—Rotatable type
    • Y10T83/9377—Mounting of tool about rod-type shaft
    • Y10T83/9379—At end of shaft

Definitions

  • the invention relates to a hand-held power tool, in particular an angle grinder, with a drive, with a work spindle having a tool clamping and with a securing device which can be operated from outside the device housing, by means of which the tool clamping can be moved between a manually releasable position and a manually non-releasable, tool-exciting position , wherein the work spindle has a hollow shaft, within which a tie rod is arranged coaxially, which is braced in the axial direction by spring force and can be displaced between the manually releasable and the manually non-releasable position by means of a displacement device.
  • Handheld power tools of this type are known, for example, from EP-A 0 152 564 and EP-A-0 253 181 (which falls under Article 54 (3) EPC).
  • the tool ie the grinding tool
  • the tool clamping when inserting a grinding wheel only has to be turned by hand and is secured by the securing device and the grinding wheel is fully tensioned.
  • the tool clamping can be released to such an extent that the tool clamping can be unscrewed by hand.
  • the work spindle can rotate freely when the tool clamping is screwed in and unscrewed before it is fixed by the securing device, so that manual tightening of the tool clamping is also difficult.
  • the clamping force during operation of the machine depends on the speed.
  • the clamping force is often not sufficient when the machine is under heavy load, where the speed is reduced due to the load.
  • a hand-held power tool which has a clamping element which is rotatable relative to the machine tool spindle and which is designed to be lockable, and the machine tool spindle is provided with a drive for unclamping and clamping the tool.
  • an auxiliary shaft is pulled out of the machine housing by means of a lever, whereby the work spindle is locked in a form-locking manner via a linkage.
  • the auxiliary shaft is now turned until the clamping nut is loosened and the tool can be changed.
  • WO-A 88 04 219 international publication date 16.06.88, has disclosed a hand-held power tool in which the drive shaft and the work spindle are penetrated by a transversely displaceable wedge which interacts with the associated wedge surfaces of the drive shaft and the work spindle and is spring-loaded in the self-locking area is held. Due to the self-locking of the wedge, a clamping effect can occur, so that the tensioning device can no longer be operated or can only be actuated by the application of great force.
  • the invention is therefore based on the object of improving a hand-held power tool of the type mentioned in such a way that, with a construction which is as simple as possible in construction and simple operation, it is not possible to rotate the work spindle when loosening or manually tightening the tool clamping.
  • a hand-held power tool of the type described at the outset by providing a locking device for locking the work spindle on the device housing, which has a coupling, which is in operative engagement when the drive is switched off in the manually releasable position for the rotationally fixed locking of the work spindle on the device housing and in the position that is not releasable manually, the tool exciting position is out of operative engagement.
  • a locking device is known from DE-U 1 623 791, but it can be actuated from outside the housing and would require an additional actuation process, in particular binding an operator's hand to actuate this locking device when changing the grinding wheel.
  • Another disadvantage of the locking device according to DE-U 1 623 791 can be seen in the fact that an additional opening is required in the gear housing, which increases the risk of it leaking.
  • the solution according to the invention achieves, on the one hand, that the work spindle can be locked as such, but, on the other hand, additionally ensures that this locking takes place automatically when the drive is switched off and, in particular, at a standstill and in the position of the securing device which can be manually released from the tool clamping.
  • This is achieved by the coupling provided according to the invention, which is coupled to the securing device.
  • the work spindle is automatically locked in a rotationally fixed manner, while it is automatically released when the tool is clamped.
  • the locking device has two coupling elements which can be brought into operative connection when actuated and which, starting from this position, can be brought out of operative connection against the force of a resilient element.
  • This has the advantage that, when the locking device is actuated, the resilient element will endeavor to bring the coupling elements into operative connection or to hold them, particularly in the case of coupling elements which can be connected by positive locking and which do not engage in every relative position are feasible.
  • the locking device has coupling elements that form a friction clutch.
  • one coupling element has at least one claw and the other has a counterpart which can be brought into engagement with the claw.
  • the coupling elements are both designed as a friction clutch and additionally have a claw and a counterpart which can be brought into engagement with it.
  • claws When using claws, there is a problem that an operator must be expected to turn on the electric drive while the claw is engaged with the counterpart. In this case, there could be a risk that the locking device or the drive device could be damaged. For this reason, it is provided that the claw and / or the counterpart have at their mutually abutting, transverse to a direction of rotation areas oriented obliquely to the direction of rotation, that when the clutch is engaged, the claw and the counterpart by acting on the spring-elastic element in Engagement durable, but can be brought out of engagement against the force of the resilient element by sliding onto the run-up surfaces.
  • One embodiment of the locking device described above provides that the claw and the counterpart can be brought into engagement with one another by an actuating movement in the axial direction of the work spindle.
  • the locking device is arranged on an end of the work spindle opposite the tool clamping device.
  • the locking device can be actuated by operating the safety device. This inevitably ensures that the locking device is actuated even when the electric drive is switched off, since actuation of the safety device is only possible even when the work spindle is at a standstill.
  • the locking device could be actuated both by the axial movement of the tensioning device and by the displacement device or the actuating member of the displacement device.
  • a solution in which the locking device can be actuated by the displacement device has proven to be structurally particularly simple and expedient.
  • Such a solution which is particularly simple in terms of construction, provides that the displacement device is a in the axial direction of the work spindle to be displaceable and rotatably held in the housing first coupling element and the working spindle have a second coupling element which can be brought into engagement with their mutually facing sides.
  • the first coupling element is held on an intermediate piece of the displacement device.
  • this variant provides that at least one of the coupling elements is connected in a spring-elastic manner to the displacement device or to the work spindle.
  • a construction in which one of the coupling elements is arranged on a resilient support is particularly simple.
  • the spring elasticity can in particular be further improved in that, in the case of a coupling element formed from such a spring-elastic material, slots are provided on opposite sides of the claw - or the counterpart to this - so that between these slots a claw or the counterpart carrying compared to the rest of the coupling element there is an additional resilient area.
  • the locking device can be actuated by the displacement device
  • the locking device can be actuated by switching off the drive and can be released by switching it on.
  • the locking device is expediently held in the released position by a centrifugal force adjusting device, so that when the working spindle rotates, the locking device cannot become effective.
  • centrifugal force control device has a centrifugal force body which is movable radially to the work spindle and with which the coupling elements can be disengaged.
  • a coupling element is a bolt which is arranged fixed to the housing and can be moved radially towards the work spindle and has a claw on the end face and that the counterpart is a recess in an outer surface of the work spindle.
  • the centrifugal force adjustment device is preferably constructed in such a way that it comprises a centrifugal force body mounted in the work spindle, which engages through the recess from the inside of the work spindle when the work spindle rotates and to prevent the claw from engaging with a front surface in the same geometric surface as the outer lateral surface of the Working spindle lies.
  • this centrifugal body is additionally biased radially inwards with a spring element.
  • the locking device can be moved into a released position, which no longer fixes the work spindle, by means of an electric adjustment device connected in parallel with the drive and working with the same energy supply as this.
  • an electric drive provides that the adjusting device is a magnet which pulls the bolt outwards in the radial direction towards the work spindle and thus disengages the recess as soon as the electric drive is switched on.
  • the actuating device is a small pneumatic cylinder.
  • gear head 10 shows a gear head, designated as a whole by 10, of a first exemplary embodiment of an angle grinding machine according to the invention.
  • this gear head 10 is a work spindle designated as a whole by 12 in two spaced apart bearings 14 and 16 rotatably mounted about an axis of rotation 18 and driven by a first bevel gear 20 which is non-rotatably seated on the work spindle 12 and a second bevel gear 22 which engages with it , the latter being seated on a drive shaft 24 of a drive 25 with a motor running perpendicular to the axis of rotation.
  • the work spindle 12 comprises a hollow shaft 26 which carries on its end projecting over a housing 28 of the gear head 10 a counter flange 30, on which a grinding wheel 32 is applied with its central clamping area.
  • This abutment of the grinding wheel 32 on the counter flange 30 is carried out by a clamping flange 34 of an intermediate sleeve 36, which can be inserted with its cylindrical shoulder 38 into the hollow shaft 26 from the side of the counter flange 30 and is preferably held in a rotationally fixed manner by means of spline teeth.
  • the intermediate sleeve 36 is acted on as a whole by a screw 40 in the direction of the counter flange, the screw 40 having its head 42 which engages over the clamping flange 34 acting directly on the latter, so that the grinding wheel 32 is clamped between the clamping flange 34 and the counter flange 30.
  • the screw 40 is part of a securing device designated as a whole by 44 and engages with its threaded piece 46 in a tie rod 48 which is displaceably mounted in the axial direction of the work spindle 12 and which, with its end face facing the counter flange 30, rests on a spring 50 supports, which in turn rests on an annular bead 52 fixedly arranged in the hollow shaft 26 and penetrated by the screw 40.
  • the spring 50 thus acts on the tie rod 48 in the direction away from the counter flange 30 and thus, as shown on the left-hand side in FIG. 1, clamps the grinding wheel 32 between the clamping flange 34 and the flange 30.
  • a displacement device designated as a whole by 56, which is arranged on a side of the work spindle 12 opposite the counter flange 30.
  • This displacement device 56 comprises an intermediate piece 58 which acts on an end face 60 facing away from the screw 40 via a roller bearing 62 and a sliding disk 64.
  • This intermediate piece 58 is arranged in the housing 28 on the side of the work spindle 12 opposite the screw 40 in a rotationally fixed and axially displaceable manner and passes through the housing 28 with a cam 66, which is rotated in the direction parallel to the axis of rotation 18 by an eccentric 68 which is rotatably mounted on the housing 28 the counter flange 30 is displaceable.
  • the eccentric 68 is preferably rotatable by an operating lever 70.
  • the tie rod 48 is arranged coaxially to the axis of rotation 18 and provided with a bore 72 which is also coaxial with the axis of rotation 18, in which protrudes a centering pin 74 of the tie rod 48 arranged on the end face 60.
  • a ball 76 rests on this centering pin 74, which is acted upon at its end opposite the centering pin 74 by a spring 78 which is supported in a bottom of the bore 72.
  • a securing ring 80 is provided in the hollow shaft 26, which is preferably arranged at a short distance from an end face 82 of the hollow shaft 26 opposite the counter flange 30.
  • a locking device On the side of the work spindle 12 opposite the screw 40, a locking device, designated as a whole by 84, is provided.
  • This comprises an annular disk 86 held on and around the intermediate piece 58, which extends in a plane perpendicular to the axis of rotation 18 in the radial direction up to an inner surface 88 formed by the housing 28 of an annular space 90 surrounding the intermediate piece 58.
  • Recesses 92 are provided in the inner surface 88 of the annular space 90, into which tabs 94 which protrude radially from the annular disk 86 engage and thereby hold the annular disk 86 in the housing 28 in a rotationally fixed manner.
  • These recesses 92 extend parallel to the axis of rotation 18, so that the washer 86 can be moved together with the intermediate piece 58 when the tie rod 48 is displaced.
  • Recesses 96 are pressed into this annular disk 86 opposite the end face 82 of the hollow shaft 26, as can be seen in particular in FIG. 2. These recesses 96 are designed such that they can be brought into engagement with claws 98 arranged on the end face 82 of the hollow shaft 26. The claws 98 arranged on the end face 82 of the hollow shaft 26 thus form a coupling element, while the other coupling element is formed by the annular disk 86 with its recesses 96.
  • the depressions 96 are preferably provided with ramp surfaces 100 which are inclined in the circumferential direction.
  • the ring disk 86 is preferably made of resilient material, for example spring steel, and each has a slot 102, which is on the inside in the radial direction with respect to the recess 96, and a slot 104 which is on the outside in the radial direction, which slot is parallel to an inner contour or an outer contour of the ring disk 86 extend, preferably on a circular path.
  • the arc length of these slots 102 and 104 thus makes it possible to determine a spring force effect of a spring region 106 which carries the recess 96 and is arranged between the slots 102 and 104.
  • the spring area 106 merges into the ring disk 86 on both sides, that is to say the spring area 106 is only from the ring disk through the inner slot 102 and the outer slot 104 86 separated.
  • the two slots 102 'and 104' on one side of the recess 96 are connected by a transverse slot 108 ', so that the spring portion 106' only on one side in the washer 86 passes over and can spring freely with an end defined by the transverse slot 108 '.
  • the actuating lever 70 is folded into the position shown in dashed lines, so that the eccentric 68 acts on the cam 66 and thus moves the intermediate piece 58 in the direction of the counter flange 30, which in turn via the roller bearing 62nd also presses the tie rod 48 against the force of the spring 50 in the direction of the counter flange 30 so that the screw 40 screwed into the tie rod 48 moves with its head 42 away from the clamping flange 34.
  • the grinding wheel 32 is no longer clamped firmly between the clamping flange 34 and the counter flange 30.
  • the head 42 can be easily rotated manually, so that the grinding wheel 32 can be changed by unscrewing the screw 40 and removing the clamping sleeve 36.
  • the washer 86 is simultaneously displaced towards the end face 82 of the hollow shaft 26 by the intermediate piece 58, so that the recesses 96 come into engagement with the claws 98.
  • the recesses 96 have the possibility of evading them in the direction away from the claws 98 by their arrangement in the spring regions 106 and 106, respectively that both the locking device 84 and the drive 25 are protected from damage.
  • FIGS. 3 and 4 A second exemplary embodiment, shown in FIGS. 3 and 4, is provided with the same reference numerals insofar as the same parts are used as in the first exemplary embodiment, so that reference is made to the above description in this regard.
  • the housing 28 has a part-cylindrical projection 110 surrounding the intermediate piece 58 with opposite flats, which is overlapped by a bush 112, which rests with its jacket 114 on the outside 116 of the projection 110 and is flattened by the two, on the Flattening of the partially cylindrical extension 110 adjacent jacket surfaces 118 is held on the extension 110 in a rotationally fixed manner.
  • the sleeve 112 can be moved as a whole parallel to the axis of rotation 18 of the work spindle 12.
  • a bottom part 120 of the bushing 112 extends from the jacket 114 to a central opening 122 which surrounds the intermediate piece 58.
  • recesses 124 are provided on opposite sides, with which the claws 98 can be brought into engagement and which correspond in function to the recesses 96 of the first exemplary embodiment.
  • the bushing 112 which forms a coupling element of the locking device 84, is not rigidly mounted on the intermediate piece 58, but can be moved relative to the latter from the end face 82 in the direction of the axis of rotation.
  • the intermediate piece 58 is provided on the side of the opening 122 facing the hollow shaft with a stop ring 126, against which the bottom part 120 of the bushing 112 is pressed by means of a plate spring 128, which is supported on a shoulder 130 of the intermediate piece 58 opposite the stop ring 126.
  • the stop ring 126 is arranged so that when the cam 66 is not acted on by the eccentric 68, the intermediate piece 58 holds the base part 120 so far above the claws 98 that they do not fit with the recesses 124 in Intervention.
  • the claws 98 In contrast, as shown in Fig. 3 on the right side, the claws 98 fully engage in the recesses 124 of the bottom part 120 when the cam 66 is acted upon by the eccentric 68 in order to hold the screw 40 in its releasable position.
  • the claws 98 are provided with inclined run-up surfaces 132 so that, as shown in FIG Are able to cooperate with the side edges of the recesses 124 and thereby to move the sleeve 112 against the force of the plate spring 128 in the direction of the axis of rotation 18 away from the claws 98, so that even in this embodiment, when the drive motor is switched on, the locking device is damaged 84 and the drive motor can be prevented.
  • FIGS. 6 and 7 just as in the first exemplary embodiment, insofar as the same parts are present, the same reference numerals are used, so that the description of the first exemplary embodiment can be referred to for the description thereof.
  • annular disk 134 is provided as a coupling element around the intermediate piece 58.
  • This ring disk 134 surrounds three lugs 136 of the housing 28, which are arranged as circular segments at the same angular distance around the intermediate piece 58, and protrudes with projections 138 into intermediate spaces lying between these lugs 136.
  • the intermediate piece 58 arranged within the lugs 136 is also provided with flats 140 which deviate from a cylindrical shape, so that the projections 138 can penetrate as far as the flats 140.
  • the flats 140 extend in the direction of the axis of rotation 18 on the one hand up to the roller bearing 62 and on the other hand up to shoulders 142, above which the intermediate piece 58 has a circular cylindrical shape.
  • a spring element 144 with brackets 146 is supported on these shoulders 142, which extends obliquely downward in the radial direction towards the annular disk 134 and acts on it in an outer region.
  • the end face 82 of the hollow shaft 26 is provided on its outside surrounding a spring ring 148 which is supported on its side facing the bearing 16 on a ring flange 150 fixed to the housing and on which the ring disk 134 rests with its outer peripheral region.
  • the washer 134 is clamped between the spring washer 148 and the spring element 144, the spring element 144 not being compressed in the unloaded state of the intermediate piece 58, shown on the left in FIG. 6, so that the spring washer 148 holds the washer 134 or holds their recesses 96 out of engagement with the claws 98.
  • Claws which are shaped similarly to the depressions 96 can also be attached to the annular disk 134 instead of the depressions 96.
  • the intermediate piece 58 presses through the shoulders 142 onto the spring element 144, which in turn is the Washer 134 is loaded and, due to the fact that its spring constant is greater than that of the spring ring 148, also compresses the spring ring 148, so that the recesses 96 are now engaged with the claws 98.
  • the depressions 96 can deflect the claws 98 in the direction away from the latter against the action of the spring element 144.
  • annular disk 86 corresponding to the first exemplary embodiment is used, for example. Insofar as they are identical to the first exemplary embodiment, the other parts are also provided with the same reference symbols.
  • the annular disk 86 is not provided with recesses 96, but rather with a friction disk 152 which lies opposite a friction disk 154 arranged on the end face 82 of the hollow shaft 26.
  • the two friction disks 152 and 154 bear against one another and fix the hollow shaft 26 relative to the housing 28.
  • resilient evasion can be dispensed with, but it is also advantageous if the friction disks in the abutting state shown in FIG. 8 on the right-hand side are held in contact with one another by spring-elastic elements. If the washer 86 is made of resilient material, an additional spring element can be dispensed with.
  • the locking device 156 comprises a bolt 160 which is mounted on the housing 28 and can be adjusted in the radial direction on the hollow shaft 26 by means of a spring 158 and which has a conical head 162 in a An outer side of the hollow shaft 26 has a conical recess 164 for fixing the hollow shaft 26 and thus the work spindle 12, as shown in FIG. 10.
  • a centrifugal force adjusting device 166 is provided. This comprises an annular clip 170 arranged in an annular groove 168 of the tie rod 48, which carries a pin 172 in the region of one end. This pin 172 protrudes into a bore 174 in the hollow shaft 26, which is arranged coaxially with the recess 164 and merges into it in the radial direction.
  • the pin 172 is dimensioned such that a front surface 176 of the same lies in the same geometric surface as the outer surface 178 when the pin is completely immersed in the bore 174 and the recess 164 and the bolt 160 due to the centrifugal force effect when the work spindle 12 rotates has displaced from the recess 164.
  • the hollow shaft 26 is provided on its inner surface with a groove 180 running from the bore 174 to its upper end, which leads the pin 172 to the bore 174 when inserted .
  • the ring-shaped clasp 170 must be made of a relatively unstable material so that the pin 172 can move readially.
  • a clip 170 ' is shown as a further variant, the pin 172 leaves its mobility in the radial direction due to its oval shape.
  • the bolt 160 engages, as in the exemplary embodiment described above, with its conical head 162 in the radial direction to the axis of rotation 18 in the otherwise conical recess 164 when the hollow shaft 26 is stationary, the bolt 160 is acted upon in this direction by the spring 158 supported on the housing 28.
  • an electromagnet 182 arranged on the side opposite the head 162 is provided for disengaging the head 162 from the recess 164, the armature 184 of which is firmly connected to the bolt 160.
  • This electromagnet 182 is connected in parallel with the drive motor, so that as soon as the drive motor is switched on, the electromagnet 182 pulls the armature 184 outward in the radial direction with respect to the axis of rotation 18 and thus disengages the head 162 from the recess 164.
  • the bolt 160 with the electromagnet 182 arranged behind it is provided in the region of a side of the transmission housing facing the drive motor, the electromagnet 182 advantageously being arranged in the motor housing and being coupled to the bolt 160 via a connecting piece 186. If the hand tool is driven by a pneumatic motor, the bolt 160 can be moved by a pneumatic lifting cylinder.
EP19880119771 1987-12-08 1988-11-28 Handwerkzeugmaschine mit automatischer Arretierung der Arbeitsspindel Expired - Lifetime EP0319813B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3741484A DE3741484C1 (de) 1987-12-08 1987-12-08 Handwerkzeugmaschine mit automatischer Arretierung der Arbeitsspindel
DE3741484 1987-12-08

Publications (3)

Publication Number Publication Date
EP0319813A2 EP0319813A2 (de) 1989-06-14
EP0319813A3 EP0319813A3 (en) 1990-02-28
EP0319813B1 true EP0319813B1 (de) 1992-05-27

Family

ID=6342074

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880119771 Expired - Lifetime EP0319813B1 (de) 1987-12-08 1988-11-28 Handwerkzeugmaschine mit automatischer Arretierung der Arbeitsspindel

Country Status (5)

Country Link
US (1) US4989374A (ko)
EP (1) EP0319813B1 (ko)
JP (1) JPH0661694B2 (ko)
KR (1) KR930007111B1 (ko)
DE (2) DE3741484C1 (ko)

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KR930007111B1 (ko) 1993-07-30
JPH01193164A (ja) 1989-08-03
JPH0661694B2 (ja) 1994-08-17
KR890009540A (ko) 1989-08-02
US4989374A (en) 1991-02-05
EP0319813A2 (de) 1989-06-14
DE3741484C1 (de) 1989-08-24
DE3871502D1 (de) 1992-07-02
EP0319813A3 (en) 1990-02-28

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