EP2934816B1 - Spindel einer werkzeugschleifmaschine - Google Patents

Spindel einer werkzeugschleifmaschine Download PDF

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Publication number
EP2934816B1
EP2934816B1 EP14786498.7A EP14786498A EP2934816B1 EP 2934816 B1 EP2934816 B1 EP 2934816B1 EP 14786498 A EP14786498 A EP 14786498A EP 2934816 B1 EP2934816 B1 EP 2934816B1
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EP
European Patent Office
Prior art keywords
bearing
spindle
spindle head
workpiece
head
Prior art date
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EP14786498.7A
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German (de)
English (en)
French (fr)
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EP2934816A1 (de
Inventor
Günther Strasser
Adolf FEUCHTHUBER
Reinhard ENDRES
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Isog Technology GmbH
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Isog Technology & Co KG GmbH
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Priority to PL14786498T priority Critical patent/PL2934816T4/pl
Publication of EP2934816A1 publication Critical patent/EP2934816A1/de
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    • 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
    • B24B41/06—Work supports, e.g. adjustable steadies
    • B24B41/066—Work supports, e.g. adjustable steadies adapted for supporting work in the form of tools, e.g. drills
    • 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
    • B24B3/00—Sharpening cutting edges, e.g. of tools; Accessories therefor, e.g. for holding the tools
    • 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
    • B24B41/042—Balancing mechanisms

Definitions

  • the invention relates to a tool grinding machine, in particular a spindle for a collet chuck of a tool grinding machine.
  • Tool grinding machines usually have a collet for clamping an at least substantially cylindrical workpiece, the later tool.
  • Typical examples of such tools made by grinding are drills and cutters.
  • the workpiece To machine the workpiece from all sides, it is rotated around the cylinder axis during machining.
  • the axis of rotation and the longitudinal axis of the workpiece are identical mathematically.
  • bearing tolerances of the spindle and machining forces acting on the workpiece reduce the precision of the finished tools.
  • the precision requirements for drills or milling cutters are in the range of a few micrometers. Therefore, the workpiece is usually supported on one or more lunettes to prevent deflection of the workpiece during processing.
  • the workpiece headstock for a tool grinding machine described.
  • the workpiece headstock has a spindle with a collet to receive the workpiece.
  • the so-called eccentricity of the workpiece is measured and corrected after each clamping operation.
  • To correct the spindle has a releasable alignment interface, which allows a motor alignment of the collet and thus the workpiece perpendicular to the spindle axis.
  • a spindle of a machine tool has a drive shaft and a work spindle.
  • the drive shaft and the work spindle are coupled together via a flexible membrane disc as a rotary joint. Machining forces occurring in the axial direction are intercepted by angular contact ball bearings.
  • the workpiece-side angular contact ball bearing is designed as a fixed bearing and the drive shaft side angular contact ball bearings allows a wobble compensation.
  • a split tool spindle for a combined milling lathe with a stationary and a rotating tool is described.
  • the tool spindle has a clamping head with a spindle shaft, which is connected via a coupling with the shaft of a drive motor.
  • the tool spindle is fixed hydrostatically in the chuck.
  • US 6,375,542 B1 discloses an adjustable precision spindle with an adjustable axis to the drive chuck axis to any misalignment of the Compensate for workpiece.
  • the spindle as usual, a housing in which the drive shaft is rotatably supported via radial bearings.
  • the drive shaft has an axial recess in which a second shaft is arranged.
  • the two shafts are connected to each other via an elastic rotary coupling 4.
  • the inner shaft is centered by hydrostatic radial bearings in the drive shaft.
  • the radial bearings have pockets divided into quadrants, which can be charged separately with a fluid.
  • the longitudinal axis of the inner shaft 3 can be adjusted relative to the longitudinal axis of the drive shaft.
  • the bearings do not allow tilting or radial displacement of the inner shaft but they are static bearings, which serve only to adjust the inner shaft relative to the drive shaft.
  • a thrust bearing between the inner shaft and the drive shaft prevents tilting of the inner shaft, relative to the drive shaft.
  • WO 2004/052592 A1 relates to an apparatus and method for centered clamping of rotationally driven parts, eg milling tools.
  • the spindle has a collet that can be aligned in a clamping cone relative to the axis of rotation of a drive shaft via a so-called tensioning and adjusting device.
  • the adjustment units distributed over the circumference of the collet grip.
  • a possible wobble or radial offset of the part is determined by two sensors.
  • a controller evaluates the signals obtained and adjusted by means of the adjusting units, the orientation of the longitudinal axis of the rotating part relative to the axis of rotation of the spindle head until the rotating part is aligned within the measurement accuracy with the axis of rotation of the spindle head.
  • a workpiece is clamped in a rotatable workpiece chuck and radially by two axially spaced-apart prisms supported to intercept machining forces as possible without deformation of the workpiece.
  • the so-called chuck body ie the part of the spindle which accommodates the chuck, is mounted so as to be radially displaceable on the spindle.
  • a clutch disc is arranged, which has a radially extending web on both sides. The webs engage in complementary grooves of the chuck and the rear spindle portion to transmit a rotational movement of the rear spindle portion on the collet receiving.
  • DE 101 18 664 A1 proposes to adjust a collet a spindle in the spindle to adjust the workpiece longitudinal axis in alignment with the axis of rotation of the spindle.
  • the collet sits in a so-called sliding body with a flat end face, with which it bears against a support surface of a base body.
  • About wedges of the sliding body can be clamped to the body and thus fixed. With dissolved wedges of the main body is displaced. After the best possible position of the collet has been set, the sliding body and thus the collet are fixed by means of the wedges.
  • DE 33 22 007 A1 discloses a drive shaft with a collet for a tool.
  • the shaft is stored in a bearing bush.
  • the bearing bush in turn sits with one end in a spherical floating bearing and another end in an annular, closed hollow body made of an elastic material.
  • the hollow body can be acted upon by a gaseous medium, thereby defining the center position of the bearing bush.
  • the invention has for its object to provide a machine tool that allows over the prior art increased precision machining and easier handling.
  • the invention is based on the finding that precise guidance of the workpiece is best achieved by one or preferably two steady rests.
  • the Wiederhohlgenautechnik when clamping the workpieces in the collet but is worse than the leadership of the workpiece by steady rests, so that there is a risk that spindle and / or workpieces while rotating the same brace about their longitudinal axes which is detrimental to the precision.
  • the hydrostatic spindle bearing proposed in the state of the art does not convince because either the bearings are set soft to compensate for the tumbling motion or stiff to accommodate the radial machining forces. This conflict of objectives when setting the bearing pressure can not be solved.
  • the core of the invention is a spindle with a bearing which provides wobble compensation and optionally compensation for radial misalignment between a rear spindle portion, i. allows the drive shaft and the longitudinal axis of a set in a collet chuck the workpiece.
  • the spindle has a front portion, which is referred to as a spindle head and which can accommodate as usual a collet for a workpiece, ie, for example, has a recess for a collet receiving.
  • the corresponding collet holder can be used for example in an axial recess of the spindle head.
  • the collet receiver may be an integral part of the spindle head.
  • the longitudinal axis of the spindle head corresponds at least approximately to the longitudinal axis of the collet and is also referred to as the first longitudinal axis.
  • the spindle has a rear spindle portion which is arranged in the extension of the first longitudinal axis.
  • the rear spindle section is the drive shaft of the spindle head and has a second longitudinal axis.
  • the rear spindle section can be received and driven by a bearing block or headstock of a machine tool and is designed accordingly.
  • the rear spindle portion may be at least one seat for at least one bearing for rotatably supporting the rear spindle portion on a bearing block.
  • at least one bearing surface of a pivot bearing may be formed on the rear spindle section.
  • At the rear spindle section can connect more spindle sections. Between the spindle head and the rear spindle portion, ie the drive shaft is at least one bearing that allows tilting of the first axis relative to the second axis.
  • the bearing also allows a radial displacement of the first axis relative to the second.
  • tilting or tilting here is meant a pivoting of the two axes in two linearly independent directions, so that a tumbling motion between the spindle head and the rear spindle portion is possible.
  • the bearing transmits compressive and / or tensile forces in the axial direction of the first and the second axis between the spindle head and the rear spindle portion.
  • the bearing is either torsionally rigid or is bridged by a torsionally rigid coupling.
  • the first and the second axis are extremely close together in practice and are only slightly tilted against each other.
  • the typical radial offset is on the order of a few hundredths of a millimeter (corresponding to less than 100 to 10 ⁇ m).
  • the tilt is typically on the order of a few hundredths of a degree.
  • the bearing should preferably allow a radial offset by a few millimeters and a tilt by a few degrees, inter alia because then the movement of the bearing can be checked by hand.
  • a machine tool with the previously described spindle allows the workpiece to be supported and / or fixed in two places by fixable support elements such as steady rest, for example by one or more clamping fingers (whereby rotation about the longitudinal axis should remain possible).
  • the position and position of the rod-shaped workpiece is consequently determined exclusively by the supporting and the machining forces, at least in the radial direction receiving static support elements.
  • the machining forces acting radially on the rod-shaped workpiece can be reliably intercepted without a significant position or change in position of the workpiece taking place. Any inaccuracies caused by the clamping of the workpiece in the collet, are compensated by the bearing between the spindle head and the rear spindle portion, whereby the precision is increased.
  • Axial working forces acting on the workpiece as well as torques on the bearing from the spindle head to the rear spindle portion can be transmitted and introduced, for example via a headstock in the structure of the machine tool.
  • the storage of the drive shaft on the machine tool comparatively simple can be done because an expensive precision storage is no longer necessary.
  • the lunettes must be adjusted accordingly for the first calibration or adjustment of the position of a workpiece or a calibration mandrel. Often it is therefore easier to reduce the precision of the storage of the drive shaft relative to the bearing block. This allows the workpiece or a calibration mandrel to be positioned (ie 'gauge-in') and then the steady rests to be applied to the workpiece or the calibration mandrel.
  • the spindle has a centering device around the spindle head and the rear spindle section to center each other.
  • centering is meant that the spindle head and the rear spindle portion are aligned with each other so that the first axis and the second axis are preferably at least approximately aligned or at least in a defined position to each other.
  • the centering device allows the spindle head in the defined position to lock the rear spindle section and cancel the blocking again.
  • the spindle head and the shaft each have opposite centering surfaces, between which at least one centering slide between at least a first position and a second position is adjustable.
  • the centering surfaces are clamped by the slide against each other whereby the bearing bridged by the centering slide and whereby the spindle head and the rear portion are centered to each other.
  • the blocking is canceled.
  • the centering slide may for example have a tapered portion and a thickened portion, wherein for centering the thickened portion is pushed into a gap between the centering surfaces in order to clamp the centering surfaces against each other.
  • the centering slide may for example be an axially displaceable between an axial centering of the spindle head and a centering of the rear spindle portion ring or a ring segment.
  • the centering can also be arranged on the spindle head and the centering pin on the rear spindle portion.
  • the centering allows you to use the workpiece precisely in the spindle head with a workpiece change and in particular to use an automatic loading device, such as a robot gripper as he, for example, from DE 10 2011 052 976 is known without a position detection must be provided for the spindle head.
  • an automatic loading device such as a robot gripper as he, for example, from DE 10 2011 052 976 is known without a position detection must be provided for the spindle head.
  • the spindle head is centered by means of the centering device to the rear spindle section.
  • the position and position of the workpiece are now very well known and it can be removed, for example, with a robotic gripper from the collet without sensors for position detection of the workpiece would be necessary.
  • a new workpiece can be very precisely inserted into the collet.
  • the centering device is opened and canceled the centering accordingly, ie the bearing is now released again and allows a Taumelaus Dermat and / or a radial offset.
  • the bearing compensates for differences in the position or orientations of the workpiece longitudinal axis, which is rigidly connected to the spindle head via the collet, and the rear spindle section. As a result, the workpiece is precisely rotated around its and not about the second axis during rotation of the rear spindle section.
  • the bearing has a first and / or a second air bearing.
  • the first air bearing may have spherical surface segment-shaped bearing surfaces, and the second air bearing planar bearing surfaces whose surface normals are parallel to the first or second axis.
  • An embodiment of the bearing as an air bearing or as a combination of two air bearings allows a balance of wobbling and a radial offset of the first to the second axis, without a static friction would have to be overcome. The precision is thus further increased.
  • the design as an air bearing allows a compact design and a very high rigidity in the axial direction.
  • Air bearings are simplified formulated plain bearings, in which the two sliding surfaces are separated by an air cushion. The air thus acts as a lubricant. Instead of air as the lubricant of the bearing, other fluids can be used as well.
  • air bearing is therefore pars pro toto for a hydrostatic bearing.
  • the coolant used in grinding can be used as a lubricant for the bearing. This eliminates the need for separate (non-gaseous) fluids separate discharge or separation of the lubricant.
  • the bearing may have an annular or at least one ring segment-shaped intermediate piece.
  • the intermediate piece preferably has at least one first spherical surface segment-shaped bearing surface and on its side remote from the spherical segment-shaped bearing surface at least one second planar bearing surface. In this sense, you can call the intermediate piece as an intermediate block. Due to the flat bearing surfaces, a radial offset of the first to the second axis is possible. By the spherical segment-shaped Bearing surfaces is a tilting of the first to the second axis possible. Therefore, the ball center of the ball segment is preferably on the first or the second axis.
  • the ball center so the point by which the spindle head against the rear portion is pivotable on the corresponding axis in front of the collet.
  • the ball center point is preferably located above the center of gravity of the spindle head (preferably with the workpiece clamped in. In the case of a vertical spindle axis, the collet opening then always points upward.
  • the two bearing surfaces of the intermediate block can be segments of cylinder jacket surfaces.
  • the respective complementary bearing surfaces of the spindle head and the rear spindle section are segments of cylinder jacket surfaces.
  • the bearing has a first and / or a second preferably as an air bearing (general hydrostatic bearing) executed part store, wherein the first part bearing has two mutually complementary first bearing blocks with first cylinder jacket surface segment-shaped bearing surfaces and the second part bearing two mutually complementary second bearing blocks with second cylinder jacket surface segment-shaped bearing surfaces having.
  • Each of the two partial bearings permits a tilting movement of the corresponding bearing blocks in the plane which orthogonally intersects the central axis of the longitudinal axis of the respective cylinder jacket surface segments and a translation in the plane orthogonal thereto.
  • the cylinder longitudinal axes of the two cylinder jacket surface segments should not be parallel to one another, but preferably form a preferably right angle along at least one axial projection along the first and / or second axis.
  • the two cylinder longitudinal axes lie in one plane, This results in the possibility of pivoting the spindle head about a point in two linearly independent directions as with a ball joint.
  • the cylinder longitudinal axes can be superimposed on a corresponding adjustment of the radii of the cylinder segment surfaces and / or by the orientation of the cylinder segment surfaces.
  • the bearing surfaces are V-shaped.
  • the bearing surfaces are typically surfaces of corresponding complementary bearing blocks between which an air gap limited by the bearing surfaces (general fluid gap).
  • the opposing, ie complementary bearing surfaces or the corresponding bearing blocks of at least one air bearing are preferably magnetically biased against each other.
  • biasing is meant the exertion of a force compressing the bearing surfaces, which defines the gap thickness for a given air flow through the bearing. This allows a particularly compact and rigid air bearing.
  • the biasing force preferably exceeds the machining forces acting in the axial direction, so that they do not cause any appreciable bearing play.
  • the biasing force F v is at least 1.2 times the intercepted in the axial direction, machining forces F Bax (F y ⁇ 1.2 ⁇ F Bax, particularly preferably Fy ⁇ 2 ⁇ F Bax, more preferably F y ⁇ 10 ⁇ F Bax).
  • F Bax F y ⁇ 1.2 ⁇ F Bax, particularly preferably Fy ⁇ 2 ⁇ F Bax, more preferably F y ⁇ 10 ⁇ F Bax.
  • Magnetic biasing may preferably be done by permanent magnets embedded in mutually complementary bearing blocks.
  • magnets are arranged on both sides of the gap such that the magnetic flux bridges the gap, that is from the north pole of a first magnet in a first bearing block passing through the gap to a south pole of at least one second magnet in the opposite second bearing block.
  • it can also be a single, magnet sufficient if its two poles are connected to each other via at least one magnetic conductor, wherein the magnetic flux passes through the gap.
  • the magnetic flux between the north and south pole of at least one magnet or at least two different magnets bridging the air gap between the bearing surfaces out.
  • the north and south pole of the magnets in the complementary bearing blocks can be aligned with each other so that the magnets tighten and thus exert a force compressing the bearing surfaces on the bearing blocks.
  • return plates or the like can be used to guide the magnetic fields. Only for the sake of simplicity in the context of the application, only from the north or south of Tru, because the out of these off or entering this field lines can by magnetic conductors with a better magnetic conductivity than the surrounding material, as they usually for magnetic return plates can be used to almost any places 'misplaced'.
  • the magnetic flux may be passed from the north pole of a magnet through the air gap and with a magnetic conductor through the opposite bearing block so that it flows through the air gap again traversed to the south pole of another or the same magnet. North and South Pole can therefore be arranged in almost any position and position, provided the magnetic flux is passed through the air gap, for example via a magnetic conductor.
  • the bearing blocks each have at least one recess, in each of which at least one permanent magnet is arranged.
  • the permanent magnet may be arranged in a recess of the corresponding bearing surface.
  • the recess can be made e.g. be closed with a polymer, preferably so that the closure continues the storage area. This means that the gap between the bearing surfaces is as uniform as possible.
  • the (at least one) magnet can be inserted from the rear side facing away from the bearing surface or a narrow side connecting the bearing surface with the rear side into an eg blind hole-like recess, wherein the distance of the magnet from the bearing surface should be as small as possible.
  • the north and / or south pole of the magnet should preferably point in the direction of the opposite bearing surface.
  • an entire bearing block or a segment of a bearing block can be made of a permanent magnetic material.
  • a torque transmission between the rear spindle portion and the spindle head can be effected by a clutch bridging the bearing.
  • the coupling may have a freely displaceable with respect to the first and / or second axis and preferably tiltable coupling element.
  • the coupling element preferably surrounds the bearing, or a part thereof annularly.
  • the rear spindle section is connected to the coupling element via at least one, but preferably two, at least approximately parallel ( ⁇ 15 °) first struts.
  • the first struts are preferably arranged on opposite sides of the first and / or the second longitudinal axis laterally on the drive shaft and the coupling element and preferably extend at least approximately ( ⁇ 15 °) in a first and / or second axis orthogonal intersecting plane.
  • the coupling element In the plan view of the plane fastened to the coupling element ends preferably in at least approximately ( ⁇ 15 °) diametrically opposite directions.
  • the coupling element is connected in a similar manner to the spindle head, namely via at least one, preferably two mutually at least approximately ( ⁇ 15 °) parallel second struts.
  • the two second struts are preferably arranged on two opposite sides of the first and / or the second axis and at least approximately ( ⁇ 15 °) parallel to each other.
  • the longitudinal axes of the second struts are in the same plane as that of the first strut or in a plane at least approximately ( ⁇ 15 °) parallel thereto, but are twisted against the first struts, i. the longitudinal axes of the struts form a parallelogram at least in the projection on one of the two planes.
  • the ends attached to the coupling element preferably have in at least approximately ( ⁇ 15 °) diametrically opposite directions.
  • Torques can be transmitted reliably from the shaft serving as the drive shaft for the spindle head rear spindle portion of the spindle head over the struts.
  • a radial offset of the spindle head with respect to the rear Usually in a bearing block of the machine tool recorded rear spindle portion, ie the first relative to the second axis is not hindered even with a rotation of the spindle of the clutch, the struts are only slightly deformed elastically. However, these radial compensatory movements are comparatively small, typically in the range of a few hundredths of a millimeter (about 10 to 100 ⁇ m). For example, with a strut length of 10 cm, the restoring forces acting on the bearing are negligible.
  • the struts are easily twisted and also curved along its longitudinal axis.
  • the restoring force generated thereby is very small and does not affect the concentricity of a workpiece guided on lunettes measurable because of the only slight tilting of tool spindles of typically only a few hundredths of the first axis to the second axis.
  • the coupling offers the advantage of a high torsional stiffness while balancing a radial offset and a tumbling movement of the first and second axes to each other at a low cost and with a very small footprint. The latter applies in particular if the struts are made of a band-like elastic material, for example spring steel strips.
  • Such strip-like struts may for example be arranged in a transverse plane around the intermediate block, ie the longitudinal axes of the struts lie in the plane.
  • the transverse plane is preferably penetrated orthogonally from the longitudinal axis of the intermediate block.
  • the longitudinal axis of the intermediate block preferably coincides with the first and / or the second axis.
  • the spindle head has a continuous recess in one side of a collet sits.
  • the collet can be connected to a displaceable in the recess and biased against the spindle head tension element, such as a rod. This allows the collet to be opened and closed by moving the rod.
  • the rod is biased in one direction, eg train. To open the collet then it is sufficient with a example in the rear spindle section or a downstream spindle section arranged piston to move the rod against the bias in the direction of the chuck.
  • the machine tool has the spindle described above with a clamping device for clamping the workpiece as precisely as possible, for example a collet for the workpiece.
  • a clamping device for clamping the workpiece as precisely as possible, for example a collet for the workpiece.
  • collet is used as a synonym for any clamping device.
  • the rear spindle section is mounted in at least one bearing block.
  • the machine tool preferably has at least one, preferably two steady rests, of which at least one is designed as a guide prism.
  • Such guide prisms are prismatic blocks with a mostly V-shaped groove to which a workpiece can be applied.
  • a clamping finger can load the workpiece against the guide prism.
  • the machine tool has a grinding and / or milling head, a machine control, usually also a car and / or a loading and unloading device.
  • the spindle 1 in FIG. 1 has a spindle head 10 with a collet holder 41 in which a collet 42 is seated.
  • the spindle head 1 has a bearing block 11 whose rear part can be protected by a cover 50 (cover s. Fig. 6 and Fig. 7 ).
  • the collet receptacle 42 is a component connected to the bearing block 11;
  • the bearing block 11 may also have a recess formed as a collet receiving.
  • the spindle 1 To the rear, ie on the side facing away from the collet 42, the spindle 1 has a drive shaft 20, which is also referred to as a rear spindle section 20. To the drive shaft 20, an air supply and control unit 60 connects. Via the drive shaft 20, the spindle 1 can be connected to a machine tool, i. The drive shaft can be connected to a drive and received by a bearing block of the machine tool. The bearing block allows, as usual, only one rotation of the drive shaft about its longitudinal axis, i. around the second axis.
  • the spindle 1 has a bearing that allows a radial offset of the drive shaft 20 and spindle head 10 as well as a tilting of the drive shaft 20 and spindle head 10 to each other.
  • the warehouse consists of two part bearings, which form a front part bearing and a rear part bearing.
  • the rear part bearing has two mutually opposite and mutually displaceable bearing surfaces 24, 34.
  • the drive shaft 20 may have a planar annular rear bearing surface 24 which is preferably orthogonal to the longitudinal axis of the drive shaft 20, ie the rear spindle portion 20 is cut. In this sense, the rear spindle portion 20 is or has a bearing block.
  • Between the two bearing surfaces 24, 34 is preferably a thin air gap, which can be fed, for example via an air duct 46 with compressed air.
  • Alternative fluids can also be used as lubricants.
  • the rear spindle portion 20 and the intermediate block 30 therefore form a linear bearing with two degrees of freedom; in other words, the intermediate block is radially displaceable to the rear spindle portion 20.
  • the intermediate piece 30 would also be rotatable relative to the drive shaft 20 without the coupling described below, therefore the rear part bearing has strictly three degrees of freedom.
  • the front part bearing is also formed by first and second bearing surfaces 33, 13, which are preferably complementary spherical surface segments.
  • first and second bearing surfaces 33, 13, which are preferably complementary spherical surface segments.
  • on the annular bearing surface 34 opposite side of the intermediate block 30 may be a first spherical surface segment-shaped bearing surface 33.
  • This bearing surface 33 is located opposite a bearing surface 13 of the spindle head 10. Again, the gap between the bearing surfaces 33, 13 can be fed with compressed air or another fluid.
  • the front part bearing thus allows a tilting of the spindle head 10 relative to the rear spindle portion 20 about the common center of the spherical surface segments (2 degrees of freedom).
  • the spindle head 10 would also be rotatable relative to the intermediate piece 30 without the coupling described below, and therefore the front part bearing has, strictly speaking, three degrees of freedom.
  • the center of the spherical surface segments in the region of the workpiece not shown.
  • This has the advantage that the radial offset during wobble compensation remains very low and that the center of gravity of the spindle head is below the pivot point at a tilt, so the spindle head does not tilt around but is self-centering with vertically mounted spindle to the vertical.
  • the first part store and also the second part store are biased by permanent magnets against each other. However, these are outside the two offset by 90 ° to each other cutting planes and are therefore not visible.
  • the magnets are arranged in a ring around the longitudinal axes of the corresponding components in recesses of the bearing blocks.
  • the front part bearing could be a linear bearing and the rear part bearing could be a ball joint. It is important for the invention only that the partial bearings together preferably both a tilt with two degrees of freedom and a radial displacement (also with 2 degrees of freedom) of the longitudinal axes of the spindle head 10 and the rear spindle portion 20 allow, and are as torsionally rigid as possible, to which a coupling may be provided can.
  • the rear spindle section 20 is connected to a coupling element 53 via two parallel first struts 51 ( Fig. 1 to Fig. 4 and Fig. 5 With Fig. 6 ).
  • the coupling element is composed of two ring halves and surrounds the intermediate block 30 like a ring, but is not at least in its rest position on the intermediate block. The coupling element is held in position via first struts 51 and second struts 52.
  • first struts 51 of the rear spindle portion 20 has on two with respect to the longitudinal axis of the drive shaft diametrically opposite sides fastening elements 55, for example, the angle pieces 55 shown at each of which one end of a first strut 51 is attached.
  • the other end of the first struts 52 is non-positively connected to the coupling element 53.
  • the longitudinal axes of the first struts 51 are preferably at least approximately parallel ( ⁇ 15 °, more preferably ⁇ 5 °, more preferably ⁇ 1 °) orthogonal to each other in a longitudinal axis of the intermediate piece cutting level.
  • two further (second) struts 52 may be arranged in the same plane.
  • the further struts 52 are connected in the same way on two diametrically opposite sides with the coupling element 53, but offset from the first struts 51 by 90 °.
  • the other end of the second struts 52 is non-positively connected via second fastening elements 56 (eg, angle pieces 56) to the spindle head 10.
  • the struts 51, 52 thus form together with the coupling element 53 a rotary coupling (see. Fig. 5 ).
  • a radial offset of the spindle head 10 to the rear spindle section 20 is influenced only by low restoring forces of the struts 51, 52. The same applies to a tumbling movement of the spindle head 10 to the rear spindle portion 20th
  • the spindle has a centering device with the spindle head 10, for example, when inserting and / or removal of a workpiece in or out of the collet 42 with the rear spindle portion 20 can be centered, ie the bearing is locked.
  • the rear spindle portion 20 has at least one first annular or ring-segment-shaped centering surface 44, which tapers conically in the direction of the spindle head 10 in the example shown.
  • At the first centering surface 44 is located as Zentrierschieber 43 an annular or alternatively ring segment-shaped piston with a tapered in the direction of the spindle head 10 lateral surface portion 45 at.
  • the centering slide 43 is axially displaceable on a preferably cylindrical bearing surface 141 of an axial pin 14 of the spindle head 10, which forms the second centering surface.
  • elastic elements 47 (only in Fig. 7 visible)
  • the centering slide 43 is biased in the direction of the spindle head 10, so that the centering slide 43 is clamped with its lateral surface portion 45 against the first centering surface whereby the spindle head 10 is centered relative to the rear spindle portion.
  • the piston can be acted upon spindle head side with a fluid, for example compressed air, thereby against the elastic elements to move, so that the lateral surface portion is no longer applied to the first centering.
  • the collet is connected to a tension element 48, here a rod (see. Fig. 6 and Fig. 7 ).
  • the rod 48 is seated in a continuous recess 16 of the spindle head 10 and is biased to train by a on the spindle head 10 supporting clamping element 49 (shown is a disc spring pact) in the direction of the rear spindle portion 10.
  • clamping element 49 shown is a disc spring pact
  • the clamping element is in a chamber 40 of the spindle head 10.
  • the rod 48 is axially displaced in the direction of the collet.
  • the rod 48 has an axial recess 46 which serves as an air passage 46 for supplying compressed air (or other fluid) for the bearing and at the same time for opening the centering device.
  • the air duct 46 is connected via corresponding bores 461, or recesses 462 with the gaps between the bearing surfaces 13, 33 and 24, 34 as well as with the sealed annular gap 431 in which the Zentrierschieber sits. If the air duct 46 is pressurized with compressed air, the centering slide is consequently first displaced and the bearing released. As soon as the pressure is high enough to compensate for the magnetic preload, the bearing is free to move.
  • a piston rod 61 of the air supply and operating unit 60 which is connected to (at least one) piston 62.
  • the piston 62 is seated in a serving as a cylinder for the piston 62 recess 63 of the housing 64 of Lucaszu Operations- and actuating unit 60 and against the force of a restoring element 65 can be acted upon with pressure, whereby the piston 62 and thus the piston rod 61 in the direction of the collet is moved and thus the tension element, ie the rod 48 relieved.
  • the piston rod 61 and the piston 62 have an axial channel 66 which communicates with the air duct 46 communicating.
  • the rod 48 has at its distal end a radial projection, which can be inserted into a complementary recess of the piston rod and then locked by a rotation through 90 ° in the recess.
  • the spindle is shown together with some elements of a tool grinder.
  • the spindle block, the optional cab, the grinding head together with the drive and traversing unit are not shown for the sake of clarity.
  • the spindle is arranged standing as shown, that is, its longitudinal axis corresponds to at least approximately ( ⁇ 15 °) of the vertical.
  • a support unit 80 which is non-positively connected to the machine frame shown only partially, a prism 70 with a clamping finger 71 and a bezel 75 are arranged.
  • the guide prism 70 has a groove 711 in which a workpiece with the clamping fingers can be fixed.
  • the position and position of the guide prism 70 relative to the support unit 80 and thus also to the spindle can be varied by means of an adjustment unit 73 until a desired position is reached. In the desired position, that of the guide prism 70 together with the clamping fingers 71 can be determined. In the same way, the bezel 75 can be brought into a desired position via a further setting unit 76 in position and position and can be fixed there.
  • a workpiece or preferably a calibration mandrel is first inserted into the collet.
  • the bearing between the spindle head 10 and the rear spindle portion is preferably locked by means of the centering device.
  • the guide prism and the steady rest can be applied to the calibration mandrel or the workpiece and fixed in the appropriate position.
  • the clamping finger 71 is preferably loaded in the direction of the guide prism 70, whereby the latter is applied cleanly to the workpiece becomes.
  • the workpiece is now in the corresponding grooves 711, 751, the guide prism or the steady rest.
  • the calibration mandrel can be exchanged for a workpiece.
  • the centering device is opened, ie the bearing is released and the machining of the workpiece can begin.
  • the machining forces insofar as they act on the workpiece in the radial direction, are exclusively intercepted by the guide prism 70 or the steady rest 75. Even with a rotation of the workpiece in the V-grooves 711, 751 (at least in the radial direction), the position of the workpiece is determined only by the guide prism 70 and the bezel 75. Even with a rotation of the workpiece due to the bearing between the spindle head 10 and the rear spindle portion 20, no radial forces are transmitted to the workpiece from the rear spindle portion to the workpiece, whereby the accuracy of the positioning of the workpiece during processing is improved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
  • Turning (AREA)
  • Machine Tool Units (AREA)
EP14786498.7A 2013-10-21 2014-10-17 Spindel einer werkzeugschleifmaschine Active EP2934816B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL14786498T PL2934816T4 (pl) 2013-10-21 2014-10-17 Wrzeciono szlifierko-ostrzarki

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013111599.3A DE102013111599A1 (de) 2013-10-21 2013-10-21 Spindel einer Werkzeugschleifmaschine
PCT/EP2014/072304 WO2015059046A1 (de) 2013-10-21 2014-10-17 Spindel einer werkzeugschleifmaschine

Publications (2)

Publication Number Publication Date
EP2934816A1 EP2934816A1 (de) 2015-10-28
EP2934816B1 true EP2934816B1 (de) 2017-03-29

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP14786498.7A Active EP2934816B1 (de) 2013-10-21 2014-10-17 Spindel einer werkzeugschleifmaschine

Country Status (8)

Country Link
US (1) US10065287B2 (enrdf_load_stackoverflow)
EP (1) EP2934816B1 (enrdf_load_stackoverflow)
JP (1) JP6205054B2 (enrdf_load_stackoverflow)
KR (1) KR101777147B1 (enrdf_load_stackoverflow)
CN (2) CN204277753U (enrdf_load_stackoverflow)
DE (1) DE102013111599A1 (enrdf_load_stackoverflow)
PL (1) PL2934816T4 (enrdf_load_stackoverflow)
WO (1) WO2015059046A1 (enrdf_load_stackoverflow)

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* Cited by examiner, † Cited by third party
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DE102016006092A1 (de) * 2016-05-20 2017-11-23 Klingelnberg Ag WERKZEUGSPlNDEL MlT WUCHTSYSTEM, GESAMTSYSTEM, DAS ElNE WERKZEUGSPlNDEL MlT WUCHTSYSTEM UMFASST UND VERFAHREN ZUM BETREIBEN EINER WERKZEUGSPINDEL MIT WUCHTSYSTEM
CN108673341B (zh) * 2018-08-01 2024-03-15 台州小助手智能科技有限公司 快速定心夹紧机构
JP6775276B2 (ja) * 2019-03-15 2020-10-28 株式会社ソディック 静圧流体軸受装置
CN110369735B (zh) * 2019-08-19 2024-03-08 珠海格力智能装备有限公司 机床
TWI785717B (zh) * 2021-08-04 2022-12-01 全鑫精密工業股份有限公司 直結式高速液靜壓磨床主軸結構

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Also Published As

Publication number Publication date
JP2016535683A (ja) 2016-11-17
EP2934816A1 (de) 2015-10-28
US10065287B2 (en) 2018-09-04
PL2934816T3 (pl) 2018-03-30
PL2934816T4 (pl) 2018-03-30
WO2015059046A1 (de) 2015-04-30
CN105764647A (zh) 2016-07-13
CN204277753U (zh) 2015-04-22
US20160229027A1 (en) 2016-08-11
KR101777147B1 (ko) 2017-09-11
DE102013111599A1 (de) 2015-08-06
KR20160085275A (ko) 2016-07-15
JP6205054B2 (ja) 2017-09-27
CN105764647B (zh) 2018-05-08

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