EP2934816B1 - Spindle of a grinding machine tool - Google Patents
Spindle of a grinding machine tool Download PDFInfo
- 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
- Authority
- EP
- European Patent Office
- Prior art keywords
- bearing
- spindle
- spindle head
- workpiece
- head
- 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.)
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- 238000000227 grinding Methods 0.000 title claims description 13
- 230000008878 coupling Effects 0.000 claims description 32
- 238000010168 coupling process Methods 0.000 claims description 32
- 238000005859 coupling reaction Methods 0.000 claims description 32
- 230000000295 complement effect Effects 0.000 claims description 16
- 230000002706 hydrostatic effect Effects 0.000 claims description 11
- 239000012530 fluid Substances 0.000 claims description 10
- 230000004907 flux Effects 0.000 claims description 7
- 238000006073 displacement reaction Methods 0.000 claims description 4
- 230000005540 biological transmission Effects 0.000 claims description 2
- 238000003754 machining Methods 0.000 description 15
- 230000033001 locomotion Effects 0.000 description 14
- 239000004020 conductor Substances 0.000 description 5
- 239000000314 lubricant Substances 0.000 description 5
- 238000003801 milling Methods 0.000 description 5
- 230000003068 static effect Effects 0.000 description 4
- 230000000903 blocking effect Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
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- 229920000642 polymer Polymers 0.000 description 2
- 230000036316 preload Effects 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
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- 235000008733 Citrus aurantifolia Nutrition 0.000 description 1
- 244000290594 Ficus sycomorus Species 0.000 description 1
- 229910000639 Spring steel Inorganic materials 0.000 description 1
- 235000011941 Tilia x europaea Nutrition 0.000 description 1
- 230000001447 compensatory effect Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000001627 detrimental effect Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 239000004571 lime Substances 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
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Images
Classifications
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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
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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
- B24B41/04—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.
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Description
Die Erfindung betrifft eine Werkzeugschleifmaschine, insbesondere eine Spindel für eine Spannzange einer Werkzeugschleifmaschine.The invention relates to a tool grinding machine, in particular a spindle for a collet chuck of a tool grinding machine.
Werkzeugschleifmaschinen haben in der Regel eine Spannzange zum Einspannen eines zumindest im Wesentlichen zylindrischen Werkstücks, des späteren Werkzeugs. Typische Beispiele für solche durch Schleifen hergestellte Werkzeuge sind Bohrer und Fräser.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.
Um das Werkstück von allen Seiten zu bearbeiten, wird es während der Bearbeitung um die Zylinderachse gedreht. Idealerweise sind dabei die Rotationsachse und die Längsachse des Werkstücks im mathematischen Sinne identisch. In der Praxis gibt es jedoch Toleranzen, die vielerlei Gründe haben. Beispielsweise ist die Wiederholgenauigkeit beim Einspannen des Werkstücks endlich. Auch Lagertoleranzen der Spindel und auf das Werkstück wirkende Bearbeitungskräfte reduzieren die Präzision der fertigen Werkzeuge. Die Präzisionsanforderungen an Bohrer oder Fräser sind jedoch im Bereich weniger Mikrometer. Daher wird das Werkstück meist an einer oder mehreren Lünetten abgestützt, um ein Ausweichen des Werkstücks während der Bearbeitung zu verhindern.To machine the workpiece from all sides, it is rotated around the cylinder axis during machining. Ideally, the axis of rotation and the longitudinal axis of the workpiece are identical mathematically. In practice, however, there are tolerances that have many reasons. For example, the repeatability when clamping the workpiece is finite. Also, bearing tolerances of the spindle and machining forces acting on the workpiece reduce the precision of the finished tools. However, 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.
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Der Erfindung liegt die Aufgabe zugrunde eine Werkzeugmaschine bereitzustellen, die eine gegenüber dem Stand der Technik erhöhte Präzision der Bearbeitung und eine einfachere Handhabung ermöglicht.The invention has for its object to provide a machine tool that allows over the prior art increased precision machining and easier handling.
Diese Aufgabe wird durch eine Spindel nach Anspruch 1 gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen angegeben.This object is achieved by a spindle according to
Die Erfindung beruht auf der Erkenntniss, dass eine präzise Führung des Werkstücks am besten durch ein oder vorzugsweise zwei Lünetten gelänge. Die Wiederhohlgenauigkeit beim Einspannen der Werkstücke in die Spannzange ist aber schlechter als die Führung des Werkstücks durch Lünetten, so dass die Gefahr besteht, dass Spindel und/oder Werkstücke beim Drehen derselben um Ihre Längsachsen verspannen was der Präzision abträglich ist. Die im Stand der Tech nik vorgeschlagene hydrostatische Spindellagerung überzeugt nicht, weil entweder die Lager weich eingestellt sind, um die Taumelbewegung auszugleichen oder aber steif sind um die radialen Bearbeitungskräfte aufzunehmen. Dieser Zielkonflikt bei der Einstellung des Lagerdrucks kann nicht gelöst werden.The invention is based on the finding that precise guidance of the workpiece is best achieved by one or preferably two steady rests. The Wiederhohlgenauigkeit 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.
Kern der Erfindung ist eine Spindel mit einem Lager, das einen Taumelausgleich und optional die Kompensation eines Radialversatzes zwischen einem hinteren Spindelabschnitt, d.h. der Antriebswelle und der Längsachse eines in einer Spannzange der Spindel festgelegten Werkstücks ermöglicht.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.
Wie üblich hat die Spindel einen vorderen Abschnitt, der als Spindelkopf bezeichnet wird und der wie üblich eine Spannzange für ein Werkstück aufnehmen kann, d.h. z.B. eine Ausnehmung für eine Spannzangenaufnahme hat. Die entsprechende Spannzangenaufnahme kann beispielsweise in eine axiale Ausnehmung des Spindelkopfes eingesetzt werden. Alternativ kann die Spannzangenaufnahme ein integraler Teil des Spindelkopfs sein. Die Längsachse des Spindelkopfs entspricht zumindest in etwa der Längsachse der Spannzange und wird auch als erste Längsachse bezeichnet. Zudem hat die Spindel einen hinteren Spindelabschnitt, der in der Verlängerung der ersten Längsachse angeordnet ist. Der hintere Spindelabschnitt ist die Antriebswelle des Spindelkopfes und hat eine zweite Längsachse. Der hintere Spindelabschnitt kann wie üblich von einem Lagerbock bzw. Spindelstock einer Werkzeugmaschine aufgenommen und angetrieben werden und ist entsprechend ausgebildet. Beispielsweise kann der hintere Spindelabschnitt wenigstens einen Sitz für wenigstens ein Lager zur drehbaren Lagerung des hinteren Spindelabschnitts an einem Lagerbock sein. Alternativ (oder zusätzlich) kann wenigstens eine Lagerfläche eines Drehlagers an dem hinteren Spindelabschnitt ausgebildet sein. An den hinteren Spindelabschnitt können sich weitere Spindelabschnitte anschließen. Zwischen dem Spindelkopf und dem hinteren Spindelabschnitt, d.h. der Antriebswelle ist wenigstens ein Lager, das eine Verkippung der ersten Achse relativ zur zweiten Achse ermöglicht. Vorzugsweise erlaubt das Lager auch eine radiale Verschiebung der ersten Achse relativ zur zweiten. Mit Verkippen bzw. Verkippung ist hier ein Schwenken der beiden Achsen in zwei von einander linear unabhängigen Richtungen gemeint, so dass eine Taumelbewegung zwischen dem Spindelkopf und dem hinteren Spindelabschnitt möglich wird. Vorzugsweise überträgt das Lager Druck- und/oder Zugkräfte in axialer Richtung der ersten bzw. der zweiten Achse zwischen dem Spindelkopf und dem hinteren Spindelabschnitt. Zur Übertragung von Drehmomenten von der Antriebswelle auf den Spindelkopf ist das Lager entweder drehsteif oder wird von einer drehsteifen Kupplung überbrückt.As usual, 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. Alternatively, 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. In addition, 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. As usual, the rear spindle section can be received and driven by a bearing block or headstock of a machine tool and is designed accordingly. For example, 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. Alternatively (or additionally), 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. Preferably, the bearing also allows a radial displacement of the first axis relative to the second. By 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. Preferably, 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. To transmit torques from the drive shaft to the spindle head, the bearing is either torsionally rigid or is bridged by a torsionally rigid coupling.
Die erste und die zweite Achse liegen in der Praxis extrem eng zusammen und sind auch nur minimal gegeneinander verkippt. Der typische Radialversatz ist in der Größenordnung weniger hundertstel Millimeter (entspricht weniger100 bis 10µm). Die Verkippung ist typischerweise in der Größenordnung weniger hundertstel Grad. Das Lager sollte vorzugsweise einen Radialversatz um wenige Millimeter und eine Verkippung um wenige Grad erlauben, u.a. weil dann die Gängigkeit des Lagers händisch überprüft werden kann.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 μm). 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.
Nachfolgend wird nicht unterschieden, ob die Kupplung Teil des Lagers ist oder nicht, denn es macht funktionell keinen Unterschied, ob eine entsprechende Kupplung in das Lager integriert ist oder ob die Kupplung als zusätzliches Bauelement betrachtet wird. Im Rahmen der Anmeldung wird als Lager die Summe der Bauelement verstanden, die eine eingeschränkte Bewegung des Spindelkopfes relativ zum hinteren Spindelabschnitt zulässt. Als Kupplung wird die Summe der Bauelement verstanden, die eine Übertragung von Drehmomenten zwischen dem Spindelkopf und dem hinteren Spindelabschnitt erlaubt. Auch durch diese Abgrenzung wird klar, dass die (Dreh-)Kupplung streng genommen immer Teil des Lagers ist, weil es die rotatorische Bewegungen zwischen dem Spindelkopf und dem hinteren Spindelabschnitt vorzugsweise vollständig unterbindet und damit die Bewegung einschränkt.In the following it is not distinguished whether the coupling is part of the bearing or not, because it makes functionally no difference whether a corresponding coupling is integrated into the bearing or whether the coupling is considered as an additional component. In the context of the application is understood as a bearing the sum of the component, which allows a limited movement of the spindle head relative to the rear spindle portion. As a coupling, the sum of the device is understood, which allows a transfer of torque between the spindle head and the rear spindle portion. Even this distinction makes it clear that the (rotary) coupling is strictly speaking always part of the bearing, because it preferably completely suppresses the rotational movements between the spindle head and the rear spindle section and thus limits the movement.
Eine Werkzeugmaschine mit der zuvor beschriebenen Spindel erlaubt es das Werkstück an zwei Stellen durch festlegbare Stützelemente wie z.B. Lünetten abzustützen und/oder festzulegen, z.B. durch einen oder mehrere Klemmfinger (wobei eine Drehung um die Längsachse möglich bleiben sollte). Die Position und Lage des stabförmigen Werkstücks wird folglich ausschließlich von den abstützenden und die Bearbeitungskräfte zumindest in radialer Richtung aufnehmenden statischen Stützelementen bestimmt. Insbesondere die radial auf das stabförmige Werkstück wirkenden Bearbeitungskräfte können dadurch zuverlässig abgefangen werden ohne dass eine nennenswerte Lage oder Positionsänderung des Werkstücks erfolgt. Eventuelle Ungenauigkeiten die durch das Einspannen des Werkstücks in der Spannzange entstehen, werden durch das Lager zwischen dem Spindelkopf und dem hinteren Spindelabschnitt kompensiert, wodurch die Präzision erhöht wird. Axial auf das Werkstück wirkende Bearbeitungskräfte können ebenso wie Drehmomente über das Lager vom Spindelkopf auf den hinteren Spindelabschnitt übertragen und z.B. über einen Spindelstock in die Struktur der Werkzeugmaschine eingeleitet werden. Eine einmal gefundene Einstellung der Stützelemente muss nicht verändert werden, wenn ein neues Werkstück einer Serie identischer Werkstücke bearbeitet werden soll. Erst für eine neue Serie, wenn also Werkstücke mit anderen Abmessungen bearbeitet werden sollen, ist für die neue Serie eine einmalige Einstellung der Stützelemente notwendig. Die Lagerung zwischen dem Spindelkopf und der Antriebswelle ermöglicht somit gegenüber starren Spindeln drei Vorteile: Es wird nicht nur die Genauigkeit der Positionierung des Werkstücks erhöht, sondern zudem die Rüstzeit verkürzt. Zudem kann die Lagerung der Antriebswelle an der Werkzeugmaschine vergleichsweie einfach erfolgen, weil eine teure Präzisionslagerung nicht mehr notwendig ist. Wenn die Präzision der Lagerung der Antriebswelle relativ zum Lagerbock reduziert wird, müssen jedoch zum ersten Einmessen bzw. Einjustieren der Position eines Werkstücks bzw. eines Kalibierdorns die Lünetten entsprechend verstellt werden. Oft ist es daher einfacher die Präzision der Lagerung der Antriebswelle relativ zum Lagerbock nicht zu reduzieren. Das erlaubt es das Werkstück oder einen Kalibrierdorn zu Positionieren (d.h.,Einzumessen') und anschließend die Lünetten an das Werkstück bzw. den Kalibrierdorn anzulegen.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. In particular, 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. Once a setting of the support elements has been found, it does not have to be changed if a new workpiece is involved a series of identical workpieces to be processed. Only for a new series, ie when workpieces with other dimensions are to be machined, a unique adjustment of the support elements is necessary for the new series. The storage between the spindle head and the drive shaft thus offers three advantages over rigid spindles: It not only increases the accuracy of the positioning of the workpiece, but also shortens the setup time. In addition, the storage of the drive shaft on the machine tool comparatively simple can be done because an expensive precision storage is no longer necessary. However, if the precision of the support of the drive shaft relative to the bearing block is reduced, 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.
Vorzugsweise hat die Spindel eine Zentriervorrichtung um den Spindelkopf und den hinteren Spindelabschnitt zueinander zu zentrieren. Mit dem Begriff "zentrieren" ist gemeint, dass der Spindelkopf und der hintere Spindelabschnitt so zueinander ausgerichtet werden, dass die erste Achse und die zweite Achse vorzugsweise zumindest in etwa fluchten oder zumindest in einer definierten Lage zueinander sind. Vorzugsweise erlaubt die Zentriervorrichtung den Spindelkopf in der definierten Lage zu dem hinterem Spindelabschnitt zu sperren und die Sperrung wieder aufzuheben.Preferably, the spindle has a centering device around the spindle head and the rear spindle section to center each other. By the term "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. Preferably, the centering device allows the spindle head in the defined position to lock the rear spindle section and cancel the blocking again.
Dazu können der Spindelkopf und der Schaft beispielsweise jeweils gegenüberliegende Zentrierflächen haben, zwischen denen wenigstens ein Zentrierschieber zwischen wenigstens einer ersten Position und einer zweiten Position verstellbar ist. In der ersten Position werden die Zentrierflächen durch den Schieber gegeneinander verspannt wodurch das Lager von dem Zentrierschieber sperrend überbrückt wird und wodurch der Spindelkopf und die der hintere Abschnitt zueinander zentriert werden. In der zweiten Position ist die Sperrung aufgehoben. Der Zentrierschieber kann beispielsweise einen verjüngten Bereich und einen verdickten Bereich haben, wobei zum Zentrieren der verdickte Bereich in einen Spalt zwischen den Zentrierflächen geschoben wird, um die Zentrierflächen gegeneinander zu verspannen. Der Zentrierschieber kann beispielsweise ein zwischen einem axialen Zentrierzapfen des Spindelkopfes und einer Zentrierbüchse des hinteren Spindelabschnitts axialverschiebbarer Ring oder ein Ringsegment sein. Natürlich kann die Zentrierbüchse auch an dem Spindelkopf und der Zentrierzapfen am hinteren Spindelabschnitt angeordnet sein.For this purpose, the spindle head and the shaft, for example, each have opposite centering surfaces, between which at least one centering slide between at least a first position and a second position is adjustable. In the first position, 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. In the second position 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. Of course, the centering can also be arranged on the spindle head and the centering pin on the rear spindle portion.
Die Zentriervorrichtung erlaubt es bei einem Werkstückwechsel das Werkstück präzise in den Spindelkopf einzusetzen und insbesondere dazu eine automatische Ladevorrichtung, z.B. einen Robotergreifer zu verwenden wie er beispielsweise aus der
Vorzugsweise hat das Lager ein erstes und/oder ein zweites Luftlager. Beispielsweise kann das erste Luftlager kugelflächensegmentförmige Lagerflächen aufweisen und das zweite Luftlager plane Lagerflächen, deren Flächennormalen zur ersten oder zweiten Achse parallel sind. Eine Ausführung des Lagers als Luftlager bzw. als Kombination zweier Luftlager ermöglicht ein Ausgleich von Taumelbewegungen und einem Radialversatz der ersten zur zweiten Achse, ohne dass eine Haftreibung überwunden werden müsste. Die Präzision wird folglich weiter erhöht. Zudem ermöglicht die Ausführung als Luftlager eine kompakte Bauform und eine sehr hohe Steifigkeit in axialer Richtung. Der Spalt zwischen den Lager-flächen der Luftlager beträgt wie üblich nur wenige Mikrometer (µm) und liegt daher in der Größenordnung der angestrebten Bearbeitungsgenauigkeit des Werkstücks. Dementsprechend ist das Luftlager in axialer Richtung der Spindel extrem steif, wodurch die mögliche Präzision der Positionierung des Werkstücks und damit seiner Bearbeitung weiter erhöht wird. Luftlager sind vereinfacht formuliert Gleitlager, bei denen die beiden Gleitflächen durch eine Luftpolster voneinander getrennt sind. Die Luft wirkt somit als Schmiermittel. Anstelle von Luft als Schmiermittel des Lagers können ebenso andere Fluide verwendet werden. Der Begriff Luftlager steht daher als pars pro toto für ein hydrostatisches Lager. Beispielsweise kann das beim Schleifen verwendete Kühlmittel als Schmiermittel für das Lager genutzt werden. Dadurch kann die bei anderen (nicht gasförmigen) Fluiden notwendige separate Abführung oder Abscheidung des Schmiermittels entfallen.Preferably, the bearing has a first and / or a second air bearing. For example, 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. In addition, the design as an air bearing allows a compact design and a very high rigidity in the axial direction. The gap between the bearing surfaces of the air bearing is, as usual, only a few microns (microns) and is therefore in the order of the desired machining accuracy of the workpiece. Accordingly, the air bearing in the axial direction of the spindle is extremely stiff, whereby the possible precision of the positioning of the workpiece and thus its machining is further increased. 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. The term air bearing is therefore pars pro toto for a hydrostatic bearing. For example, 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.
Beispielsweise kann das Lager ein ringförmiges oder wenigstens ein ringsegmentförmiges Zwischenstück aufweisen. Das Zwischenstück hat vorzugsweise wenigstens eine erste kugelflächensegmentförmige Lagerfläche und auf seiner der kugelsegmentförmigen Lagerfläche abgewandten Seite wenigstens eine zweite plane Lagerfläche. In diesem Sinne kann man das Zwischenstück auch als Zwischenblock bezeichnen. Durch die planen Lagerflächen wird ein Radialversatz der ersten zu der zweiten Achse ermöglicht. Durch die kugelsegmentförmigen Lagerflächen wird eine Verkippung der ersten zur zweiten Achse möglich. Daher ist der Kugelmittelpunkt des Kugelsegments vorzugsweise auf der ersten oder der zweiten Achse. Besonders bevorzugt liegt der Kugelmittelpunkt, also der Punkt, um den der Spindelkopf gegen den hinteren Abschnitt schwenkbar ist auf der entsprechenden Achse vor der Spannzange. Dadurch wird der Winkel zwischen der Längsachse des Werkstücks und der Längsachse des hinteren Spindelabschnitts, der durch die Taumelbewegung kompensiert werden muss kleiner. Besonders bevorzugt liegt der Kugelmittelpunkt oberhalb des Schwerpunkts des Spindelkopfs (vorzugsweise mit eingespanntem Werkstück. Bei einer vertikalen Spindelachse weist dann die Spannzangenöffnung immer nach oben.For example, 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. Particularly preferably, 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. Thereby, the angle between the longitudinal axis of the workpiece and the longitudinal axis of the rear spindle portion, which must be compensated by the wobbling movement is smaller. 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.
Alternativ können die beiden Lagerflächen des Zwischenblocks Segmente von Zylindermantelflächen sein. Entsprechend sind auch die jeweils komplementären Lagerflächen des Spindelkopfs und des hinteren Spindelabschnitts Segmente von Zylindermantelflächen. Anders formuliert hat das Lager ein erstes und/oder ein zweites vorzugsweise als Luftlager (allgemeiner hydrostatisches Lager) ausgeführtes Teillager, wobei das erste Teillager zwei zueinander komplementäre erste Lagerblöcke mit ersten Zylindermantelflächensegmentförmigen Lagerflächen aufweist und das zweite Teillager zwei zueinander komplementäre zweite Lagerblöcke mit zweiten zylindermantelflächensegmentförmigen Lagerflächen aufweist. Jedes der beiden Teillager erlaubt eine Kippbewegung der entsprechenden Lagerblöcke in der die Mittelachse der Längsachse der jeweiligen Zylindermantelflächensegmente orthogonal schneidenden Ebene und eine Translation in der dazu orthogonalen Ebene. Gleichzeitig können Drehbewegungen um die Schnittachse der beiden Ebenen und damit Drehmomente zwischen den Lagerblöcken übertragen werden. Nur der Vollständigkeit halber wird angemerkt, dass die Zylinderlängsachsen der beiden Zylindermantelflächensegmente nicht parallel zueinander sein sollten, sondern vorzugsweise zumindest bei einer Axialprojektion entlang der ersten und/oder der zweiten Achse einen vorzugsweise rechten Winkel bilden. Vorzugsweise liegen die beiden Zylinderlängsachsen in einer Ebene, dadurch ergibt sich wie bei einem Kugelgelenk die Möglichkeit den Spindelkopf um einen Punkt in zwei linear unabhängige Richtungen zu schwenken. Die Zylinderlängsachsen können über eine entsprechende Anpassung der Radien der Zylindersegmentflächen und/oder durch die Ausrichtung der Zylindersegmentflächen aufeinander gelegt werden.Alternatively, the two bearing surfaces of the intermediate block can be segments of cylinder jacket surfaces. Accordingly, the respective complementary bearing surfaces of the spindle head and the rear spindle section are segments of cylinder jacket surfaces. In other words, 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. At the same time rotational movements about the cutting axis of the two planes and thus torques between the bearing blocks can be transmitted. For the sake of completeness, it is noted that 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. Preferably, 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.
Wenn man auf den Taumelsaugleich verzichten kann, dann kann man anstelle von zylindermantelflächensegmentförmigen Lagerflächen auch nicht rotationsymmetrische Lagerflächen verwenden, beispielsweise prismatische Lagerflächen. Im einfachsten Fall sind die Lagerflächen V-förmig.If you can dispense with the Taumelsaugleich, then you can use instead of cylindrical outer surface segment-shaped bearing surfaces and non-rotationally symmetric bearing surfaces, such as prismatic bearing surfaces. In the simplest case, the bearing surfaces are V-shaped.
Die Lagerflächen sind typischerweise Oberflächen entsprechender komplementärer Lagerblöcke zwischen denen ein von den Lagerflächen begrenzter Luftspalt (allgemeiner Fluidspalt) ist .Vorzugsweise sind die einander gegenüberliegenden, d.h. komplementären Lagerflächen bzw. die entsprechenden Lagerblöcke wenigstens eines Luftlagers vorzugsweise magnetisch gegeneinander vorgespannt. Unter "Vorspannen" wird das Ausüben einer die Lagerflächen zusammendrückenden Kraft verstanden, welche bei einem gegebenen Luftdurchsatz durch das Lager die Spaltdicke festlegt. Dies ermöglicht ein besonders kompaktes und steifes Luftlager. Die Vorspannkraft übersteigt vorzugsweise die in axialer Richtung wirkenden Bearbeitungskräfte, so dass diese kein nennenswertes Lagerspiel verursachen. Vorzugsweise ist die Vorspannkraft Fv mindestens das 1,2 fache der in axialer Richtung abzufangenden Bearbeitungskräfte FBax (Fy ≥ 1.2·FBax, besonders bevorzugt Fy ≥ 2·FBax, weiter bevorzugt Fy ≥ 10·FBax). Diese hohen Vorspannkräfte lassen sich durch in die Lagerblöcke eingelassene Permanentmagnete leicht erzielen.The bearing surfaces are typically surfaces of corresponding complementary bearing blocks between which an air gap limited by the bearing surfaces (general fluid gap). Preferably, the opposing, ie complementary bearing surfaces or the corresponding bearing blocks of at least one air bearing are preferably magnetically biased against each other. By "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. Preferably, 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). These high preload forces can be easily achieved by embedded in the bearing blocks permanent magnets.
Magnetisches Vorspannen kann vorzugsweise durch Permanentmagnete erfolgen, die in zueinander komplementären Lagerblöcken eingelassen sind. Im einfachsten Fall werden beidseits des Spaltes Magnete derart angeordnet, dass der magnetische Fluss den Spalt überbrückt, also vom Nordpol eines ersten Magneten in einem ersten Lagerblock den Spalt durchsetzend zu einem Südpol wenigstens eines zweiten Magneten im gegenüberliegenden zweiten Lagerblock verläuft. Es kann aber auch ein einziger, Magnet genügen, wenn seine beiden Pole über wenigstens einen magnetischen Leiter miteinander verbunden werden, wobei der magnetische Fluss den Spalt durchsetzt. In allen Fällen wird, der magnetischer Fluss zwischen Nord- und Südpol wenigstens eines Magneten oder aber wenigstens zweier verschiedener Magnete den Luftspalt zwischen den Lagerflächen überbrückend geführt.Magnetic biasing may preferably be done by permanent magnets embedded in mutually complementary bearing blocks. In the simplest case, 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. But 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. In all cases, 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.
Dazu können Nord- und Südpol der Magnete in den komplementären Lagerblöcken so zueinander ausgerichtet werden, dass die Magnete sich anziehen und damit eine die Lagerflächen zusammendrückende Kraft auf die Lagerblöcke ausüben. Natürlich können auch Rückschlussbleche oder dergleichen verwendet werden um die Magnetfelder zu führen. Nur der Einfachheit halber ist im Rahmen der Anmeldung lediglich von Nord- bzw. Südpolen die Rede, denn die aus diesen aus- bzw. in diese eintretenden Feldlinien können durch magnetische Leiter mit einer besseren magnetischen Leitfähigkeit als das sie umgebende Material, wie sie üblicherweise für magnetische Rückschlussbleche verwendet werden, an nahezu beliege Orte ,verlegt' werden. Wesentlich ist nur, dass der üblicherweise durch Magnetfeldlinien veranschaulichte magnetische Fluss von einem magnetischen Nordpol eines sich an einem ersten Lagerblock abstützenden Magneten vorzugsweise orthogonal zur entsprechenden Lagerfläche aus der Lagerflächen in den Luftspalt eintritt und auf der gegenüberliegenden Seite in einen Südpol eines sich am gegenüberliegenden Lagerblock abstützenden Magneten eintritt. Alternativ kann der magentische Fluss vom Nordpol eines Magneten durch den Luftspalt und mit einem magnetischen Leiter durch den gegenüberliegenden Lagerblock geführt werden, so dass er den Luftspalt erneut durchsetzt zum Südpole eines anderen oder desselben Magneten fließt. Nord- und Südpol können daher in nahezu beliebiger Lage und Position angeordnet werden, sofern der magnetische Fluss z.B. über einen magnetischen Leiter den Luftspalt durchsetzend geführt wird.For this purpose, 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. Of course, 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 Poland, 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'. It is only essential that the magnetic flux typically illustrated by magnetic field lines from a magnetic north pole of a supported on a first bearing block magnet preferably orthogonal to the corresponding bearing surface from the bearing surfaces enters the air gap and on the opposite side in a south pole of the opposite bearing block supporting Magnet enters. Alternatively, 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.
In einer besonders einfachen Ausführungsform haben die Lagerblöcke je wenigstens eine Ausnehmung, in denen jeweils wenigstens ein Permanentmagnet angeordnet ist. Beispielsweise kann der Permanentmagnet in einer Ausnehmung der entsprechenden Lagerfläche angeordnet sein. Nachdem der (wenigstens eine) Permanentmagnet in die Ausnehmung eingebracht wurde, kann die Ausnehmung z.B. mit einem Polymer verschlossen werden, vorzugsweise so dass der Verschluss die Lagerfläche fortsetzt. Damit ist gemeint, dass der Spalt zwischen den Lagerflächen möglichst gleichmäßig ist. Da Lagerflächen von hydrostatischen Lagern üblicherweise eingeschliffen werden, ist das entsprechend leicht möglich, wenn man zunächst die Magnete einsetzt, die Ausnehmung mit dem Polymer verschließt und nach dem Aushärten die Lagerflächen einschleift, bzw. poliert, besonders bevorzugt wird dabei der Nord- oder der Südpol oder ein mit einem solchen verbundener magentischer Leiter freigelegt und dadurch Teil der Lagerfläche. Dadurch kann eine besonders hohe Vorspannung erreicht werden. Alternativ kann der (wenigstens eine) Magnet von der der Lagerfläche abgewandten Rückseite oder einer die Lagerfläche mit der Rückseite verbindenden Schmalseite in eine beispielsweise sacklochartige Ausnehmung eingesetzt werden, wobei der Abstand des Magnets von der Lagerfläche möglichst klein sein sollte. Der Nord- und/oder der Südpol des Magneten sollte vorzugsweise in Richtung der gegenüberliegenden Lagerfläche weisen.In a particularly simple embodiment, the bearing blocks each have at least one recess, in each of which at least one permanent magnet is arranged. For example, the permanent magnet may be arranged in a recess of the corresponding bearing surface. After the (at least one) permanent magnet has been introduced into the recess, 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. Since bearing surfaces of hydrostatic bearings are usually ground, this is correspondingly easily possible if one first uses the magnets, closes the recess with the polymer and after hardening the bearing surfaces einschleift or polished, particularly preferred is the north or south pole or a magenta conductor connected to such and thus part of the bearing surface exposed. This allows a particularly high bias voltage can be achieved. Alternatively, 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.
Natürlich kann auch ein ganzer Lagerblock oder ein Segment eines Lagerblocks aus einem permanentmagnetischen Werkstoff gefertigt sein.Of course, an entire bearing block or a segment of a bearing block can be made of a permanent magnetic material.
Eine Drehmomentübertragung zwischen dem hinteren Spindelabschnitt und dem Spindelkopf kann durch eine das Lager überbrückende Kupplung erfolgen.A torque transmission between the rear spindle portion and the spindle head can be effected by a clutch bridging the bearing.
Beispielsweise kann die Kupplung ein mit Bezug auf die erste und/oder zweite Achse frei verschiebbares und vorzugsweise kippbares Kupplungselement haben. Das Kupplungselement umgibt vorzugsweise das Lager, oder einen Teil davon ringförmig. Der hintere Spindelabschnitt ist über mindestens eine, vorzugsweise jedoch zwei zumindest näherungsweise parallele (±15°) erste Streben mit dem Kupplungselement verbunden. Die ersten Streben sind vorzugsweise auf gegenüberliegenden Seiten der ersten und/oder der zweiten Längsachse seitlich an der Antriebswelle und dem Kupplungselement angeordnet und verlaufen vorzugsweise zumindest in etwa (±15°) in einer die erste und/oder zweite Achse orthogonal schneidenden Ebene. In der Aufsicht auf die Ebene weisen die an dem Kupplungselement befestigten Enden vorzugsweise in zumindest näherungsweise (±15°) diametral entgegengesetzte Richtungen. Dadurch wir bei der Übertragung eines Drehmoments von der Antriebswelle auf das Kupplungselement mittels der Streben unabhängig von der Richtung des Drehmoments immer eine der beiden Streben auf Zug belastet, wodurch die Kupplung sehr steif ist. Das Kupplungselement ist in ähnlicher Weise mit dem Spindelkopf verbunden, nämlich über wenigstens eine, vorzugsweise zwei zueinander zumindest in etwa (±15°) parallele zweite Streben. Auch die beiden zweiten Streben sind vorzugsweise auf zwei einander gegenüberliegenden Seiten der ersten und/oder der zweiten Achse angeordnet und zumindest in etwa (±15°) parallel zueinander. Vorzugsweise liegen die Längsachsen der zweiten Streben in der gleichen Ebene wie die der ersten Strebens oder in einer dazu zumindest in etwa (±15°) parallelen Ebene, sind jedoch gegen die ersten Streben verdreht, d.h. die Längsachsen der Streben bilden zumindest in der Projektion auf einer der beiden Ebenen ein Parallelogramm. Die an dem Kupplungselement befestigten Enden weisen vorzugsweise in zumindest näherungsweise (±15°) diametral entgegengesetzte Richtungen.For example, 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. In the plan view of the plane fastened to the coupling element ends preferably in at least approximately (± 15 °) diametrically opposite directions. As a result, when transmitting a torque from the drive shaft to the coupling element by means of the struts, regardless of the direction of the torque, we always load one of the two struts on train, whereby the coupling is very stiff. 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. Also, 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. Preferably, 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.
Über die Streben können Drehmomente zuverlässig von dem als Antriebswelle für den Spindelkopf dienenden hinteren Spindelabschnitt auf den Spindelkopf übertragen werden. Ein radialer Versatz des Spindelkopfs gegenüber dem hinteren, üblicherweise in einem Lagerbock der Werkzeugmaschine aufgenommenen hinteren Spindelabschnitts, d.h. der ersten gegenüber der zweiten Achse wird auch bei einer Drehung der Spindel von der Kupplung nicht behindert, die Streben werden lediglich etwas elastisch verformt. Diese radialen Ausgleichsbewegungen sind aber vergleichsweise klein, typischerweise im Bereich weniger hundertstel Millimeter (etwa 10 bis 100 µm). Bei einer Strebenlänge von z.B. 10 cm sind die auf das Lager wirkenden Rückstellkräfte daher vernachlässigbar. Bei einer Kippbewegung werden die Streben leicht tordiert und auch entlang ihrer Längsachse gekrümmt. Die dadurch erzeugte Rückstellkraft ist jedoch wegen der bei Werkzeugspindeln nur geringen Verkippung von typischerweise nur wenigen hundertstel Grad der ersten Achse zur zweiten Achse sehr klein und beeinträchtigt den Rundlauf eines an Lünetten geführten Werkstücks nicht messbar. Die Kupplung bietet den Vorteil einer hohen Drehsteifigkeit bei gleichzeitigem Ausgleich eines Radialversatzes sowie einer Taumelbewegung der ersten und der zweiten Achsen zueinander zu günstigen Kosten und mit einem sehr geringen Raumbedarf. Letzteres gilt insbesondere, wenn die Streben aus einem bandartigen elastischen Material sind, z.B. aus Federstahlstreifen. Solche bandartigen Streben können beispielsweise in einer Querebene rund um den Zwischenblock angeordnet sein, d.h. die Längsachsen der Streben liegen in der Ebene. Die Querebene wird vorzugsweise orthogonal von der Längsachse des Zwischenblocks durchsetzt. Die Längsachse des Zwischenblocks fällt vorzugsweise mit der ersten und/oder der zweiten Achse zusammen.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 μm). For example, with a strut length of 10 cm, the restoring forces acting on the bearing are negligible. In a tilting movement, the struts are easily twisted and also curved along its longitudinal axis. However, 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.
Vorzugsweise hat der Spindelkopf eine durchgehende Ausnehmung, in deren einen Seite eine Spannzange sitzt. Die Spannzange kann mit einem in der Ausnehmung verschiebbaren und gegen den Spindelkopf vorgespannten Zugelement, beispielsweise einer Stange verbunden sein. Dadurch kann die Spannzange durch Verschieben der Stange geöffnet und/ geschlossen werden. Vorzugsweise ist die Stange in einer Richtung vorgespannt, z.B. auf Zug. Zum Öffnen der Spannzange genügt es dann mit einem z.B. im hinteren Spindelabschnitt oder einem nachgeordneten Spindelabschnitt angeordneten Kolben die Stange gegen die Vorspannung in Richtung des Spannfutters zu verschieben.Preferably, 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. Preferably, 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.
Die Werkzeugmaschine hat die oben beschriebene Spindel mit einer Spannvorrichtung zum möglichst präzisen Einspannen des Werkstücks, beispielsweise einer Spannzange für das Werkstück. In diesem Sinne wird der Begriff Spannzange als Synonym für ein beliebiges Spannmittel verwendet. Der hintere Spindelabschnitt ist in wenigstens einem Lagerbock gelagert. Zudem hat die Werkzeugmaschine vorzugsweise zumindest eine, vorzugsweise zwei Lünetten, von denen wenigstens eine als Führungsprisma ausgeführt ist. Solche Führungsprismen sind prismatische Blöcke mit einer meist V-förmigen Nut an die ein Werkstück angelegt werden kann. Ein Spannfinger kann das Werkstück gegen das Führungsprisma belasten. Zudem hat die Werkzeugmaschine wie üblich einen Schleif- und/oder Fräskopf, eine Maschinensteuerung, meist auch eine Kabine und/oder einen Be- und Entladevorrichtung.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. In this sense, the term collet is used as a synonym for any clamping device. The rear spindle section is mounted in at least one bearing block. In addition, 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. In addition, as usual, the machine tool has a grinding and / or milling head, a machine control, usually also a car and / or a loading and unloading device.
Die Erfindung wird nachstehend ohne Beschränkung des allgemeinen Erfindungsgedankens anhand von Ausführungsbeispielen unter Bezugnahme auf die Zeichnungen exemplarisch beschrieben.
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zeigt eine isometrische Ansicht einer SpindelFigur 1 -
zeigt erste Seitenansicht einer Spindel,Figur 2 -
Figur 3 zweite eine zweite Seitenansicht der Spindel -
Figur 4 zeigt eine Aufsicht auf die Spindel. -
Figur 5 zeigt eine Seitenansicht der Spindel mit montierter Abdeckung. -
Figur 6 zeigt einen Längsschnitt der Spindel entlang der Ebene A-A ausFig. 5 . -
Figur 7 zeigt einen Längsschnitt der Spindel entlang der Ebene B-B ausFig. 6 . -
Figur 8 zeigt eine Spindel in einer teilmontierten Werkzeugschleifmaschine.
-
FIG. 1 shows an isometric view of a spindle -
FIG. 2 shows first side view of a spindle, -
FIG. 3 second a second side view of the spindle -
FIG. 4 shows a view of the spindle. -
FIG. 5 shows a side view of the spindle with mounted cover. -
FIG. 6 shows a longitudinal section of the spindle along the plane AAFig. 5 , -
FIG. 7 shows a longitudinal section of the spindle along the plane BBFig. 6 , -
FIG. 8 shows a spindle in a partially assembled tool grinding machine.
Die Spindel 1 in
Nach hinten, also auf der der Spannzange 42 abgewandten Seite hat die Spindel 1 eine Antriebswelle 20, die auch als hinterer Spindelabschnitt 20 bezeichnet wird. An die Antriebswelle 20 schließt sich eine Luftzuführungs- und Betätigungseinheit 60 an. Über die Antriebswelle 20 kann die Spindel 1 mit einer Werkzeugmaschine verbunden werden, d.h. die Antriebswelle kann mit einem Antrieb verbunden und von einem Lagerbock der Werkzeugmaschine aufgenommen werden. Der Lagerbock erlaubt dabei wie üblich nur eine Rotation der Antriebswelle um ihre Längsachse, d.h. um die zweite Achse.To the rear, ie on the side facing away from the
Wie am besten Anhand von
Das vordere Teillager wird ebenfalls von ersten und zweiten Lagerflächen 33, 13 gebildet, die vorzugsweise zueinander komplementäre Kugelflächensegmente sind. Dazu kann auf der der kreisringförmigen Lagerfläche 34 entgegengesetzten Seite des Zwischenblocks 30 eine erste kugelflächensegmentförmige Lagerfläche 33 sein. Dieser Lagerfläche 33 liegt eine Lagerfläche 13 des Spindelkopfs 10 gegenüber. Wieder kann der Spalt zwischen den Lagerflächen 33, 13 mit Druckluft oder einem anderen Fluid gespeist werden. Das vordere Teillager erlaubt folglich eine Verkippung des Spindelkopfs 10 relativ zum dem hinteren Spindelabschnitt 20 um den gemeinsamen Mittelpunkt der Kugelflächensegmente (2 Freiheitsgrade). Der Spindelkopf 10 wäre ohne die weiter unten beschriebene Kupplung auch gegenüber dem Zwischenstück 30 drehbar, daher hat auch das vordere Teillager strenggenommen drei Freiheitsgrade. Im gezeigten Beispiel ist der Mittelpunkt der Kugelflächensegmente im Bereich des nicht dargestellten Werkstücks. Das hat den Vorteil, dass der Radialversatz beim Taumelausgleich sehr gering bleibt und dass der Schwerpunkt des Spindelkopfs unterhalb des Drehpunkts bei einer Verkippung liegt, der Spindelkopf kippt deshalb nicht um sondern ist bei stehend montierter Spindel selbstzentrierend zur Vertikalen.The front part bearing is also formed by first and second bearing surfaces 33, 13, which are preferably complementary spherical surface segments. For this purpose, on the
Das erste Teillager und auch das zweite Teillager, sind durch Permanentmagnete gegeneinander vorgespannt. Diese liegen jedoch außerhalb der beiden um 90° zueinander versetzten Schnittebenen und sind daher nicht sichtbar. Die Magnete sind ringförmig um die Längsachsen der entsprechenden Bauteile in Ausnehmungen der Lagerblöcke angeordnet.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.
Anders als dargestellt könnte auch das vordere Teillager ein Linearlager sein und das hintere Teillager ein Kugelgelenk. Wichtig ist für die Erfindung nur, dass das Teillager zusammen vorzugsweise sowohl eine Verkippung mit zwei Freiheitsgraden als auch einen Radialversatz (mit ebenfalls 2 Freiheitsgraden) der Längsachsen des Spindelkopfs 10 und des hinteren Spindelabschnitts 20 erlauben, sowie möglichst drehsteif sind, wozu eine Kupplung vorgesehen sein kann.Other than shown, 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
Um das Lager drehsteif zu machen wird es im gezeigten Beispiel von einer Drehkupplung überbrückt. Deren Elemente sind am besten auf den
Zur Befestigung der ersten Streben 51 hat der hintere Spindelabschnitt 20 an zwei einander mit Bezug auf die Längsachse der Antriebswelle diametral gegenüberliegenden Seiten Befestigungselemente 55, z.B. die gezeigten Winkelstücke 55 an denen je ein Ende einer ersten Strebe 51 befestigt ist. Das andere Ende der ersten Streben 52 ist kraftschlüssig mit dem Kupplungselement 53 verbunden. Wie dargestellt verlaufen die Längsachsen der ersten Streben 51 vorzugsweise zumindest in etwa parallel (±15°, besonders bevorzugt ±5°, weiter bevorzugt ±1°) zueinander in einer die Längsachse des Zwischenstücks orthogonal schneidenden Ebene. Vorzugsweise in der gleichen Ebene können zwei weitere (zweite) Streben 52 angeordnet sein. Die weiteren Streben 52 sind in gleicher Weise an zwei diametral gegenüberliegenden Seiten mit dem Kupplungselement 53 verbunden, jedoch gegenüber den ersten Streben 51 um 90° versetzt. Das andere Ende der zweiten Streben 52 ist über zweite Befestigungselemente 56 (z.B. Winkelstücke 56) mit dem Spindelkopf 10 kraftschlüssig verbunden. Die Streben 51, 52 bilden folglich zusammen mit dem Kupplungselement 53 eine Drehkupplung (vgl.
Wie in
An ihrem hinteren Ende ist die Spannzange mit einem Zugelement 48, hier einer Stange verbunden (vgl.
Die Stange 48 hat eine axiale Ausnehmung 46, die als Luftkanal 46 zum Zuführen von Druckluft (oder einem anderen Fluid) für das Lager und gleichzeitig zum Öffnen der Zentriervorrichtung dient. Dazu ist der Luftkanal 46 über entsprechende Bohrungen 461, bzw. Einstiche 462 mit den Spalten zwischen den Lagerflächen 13, 33 und 24, 34 ebenso verbunden wie mit dem angedichteten Ringspalt 431 in dem der Zentrierschieber sitzt. Wird der Luftkanal 46 mit Druckluft beaufschlagt, wird folglich zunächst der Zentrierschieber verschoben und das Lager freigeben. Sobald der Druck groß genug ist, dass die magnetische Vorspannung kompensiert wird, ist das Lager frei beweglich.The
Zum Öffnen der Spannzange 42 sitzt in der axialen Verlängerung des hinteren Spindelabschnitts 20 eine Kolbenstange 61 der Luftzuführungs- und Betätigungseinheit 60, die mit (wenigstens einem) Kolben 62 verbunden ist. Der Kolben 62 sitzt in einer als Zylinder für den Kolben 62 dienenden Ausnehmung 63 des Gehäuses 64 der Luftzuführungs- und Betätigungseinheit 60 und ist gegen die Kraft eines Rückstellelementes 65 mit Druck beaufschlagbar, wodurch der Kolben 62 und damit auch die Kolbenstange 61 in Richtung der Spannzange verschoben wird und damit das Zugelement, d.h. die Stange 48 entlastet. Auch die Kolbenstange 61 und die Kolben 62 haben einen axialen Kanal 66 der mit dem Luftkanal 46 kommunizierend verbunden ist. Zur Verbindung des axialen Kanals 66 und des Luftkanals 46 hat die Stange 48 an ihrem distalen Ende einen radialen Vorsprung, der eine komplementäre Ausnehmung der Kolbenstange eingeführt und dann durch eine Drehung um 90° in der Ausnehmung verriegelt werden kann.To open the
In
Zum Schleifen eines Werkstücks, wird zunächst ein Werkstück oder vorzugsweise ein Kalibrierdorn in die Spannzange eingesetzt. Dabei ist das Lager zwischen dem Spindelkopf 10 und dem hinteren Spindelabschnitt vorzugsweise mittels der Zentriervorrichtung gesperrt. Nun können das Führungsprisma und die Lünette an den Kalibrierdorn bzw. das Werkstück angelegt werden und in der entsprechenden Position fixiert werden. Vor dem Fixieren der Position und Lage des Führungsprismas 70 wird vorzugsweise der Spannfinger 71 in Richtung des Führungsprismas 70 belastet wodurch letzteres sauber an das Werkstück angelegt wird. Anders formuliert liegt das Werkstück nun in den entsprechenden Nuten 711, 751, des Führungsprismas bzw. der Lünette an. Nun kann sofern nötig der Kalibrierdorn gegen ein Werkstück ausgetauscht werden. Anschließend wird die Zentriervorrichtung geöffnet, d.h. das Lager wird freigegeben und die Bearbeitung des Werkstücks kann beginnen. Die Bearbeitungskräfte, sofern sie in radialer Richtung auf das Werkstück wirken, werden ausschließlich von dem Führungsprisma 70 bzw. der Lünette 75 abgefangen. Auch bei einer Drehung des Werkstücks in den V-Nuten 711, 751 wird (zumindest in radialer Richtung) die Lage des Werkstücks nur durch das Führungsprisma 70 und die Lünette 75 bestimmt. Auch bei einer Drehung des Werkstücks werden aufgrund des Lagers zwischen Spindelkopf 10 und dem hinteren Spindelabschnitt 20 keine radialen Kräfte auf das Werkstück vom hinteren Spindelabschnitt auf das Werkstück übertragen, wodurch die Genauigkeit der Positionierung des Werkstücks bei der Bearbeitung verbessert wird.For grinding a workpiece, a workpiece or preferably a calibration mandrel is first inserted into the collet. The bearing between the
- 1010
- Spindelkopf (kurz: "Kopf")Spindle head (short: "head")
- 1111
- Lagerblock des Spindelkopfes (kurz: "Kopfblock")Bearing block of the spindle head (in short: "head block")
- 1313
- Lagerflächestorage area
- 1414
- axialer Zapfenaxial pin
- 141141
- Anlagefläche für Zentrierring / ZentrierflächeContact surface for centering ring / centering surface
- 1616
- durchgehende Ausnehmungthrough recess
- 2020
- hinterer Spindelabschnitt / AntriebswelleRear spindle section / drive shaft
- 2424
- Lagerflächestorage area
- 3030
- Zwischenstück/ZwischenblockAdapter / intermediate block
- 3333
- Lagerflächestorage area
- 3434
- Lagerflächestorage area
- 4040
- Kammer für SpannelementChamber for clamping element
- 4141
- Spannzangenaufnahme, allgemeiner: SpannmittelaufnahmeCollet chuck, more general: Clamping fixture
- 4242
- Spannzange, allgemeiner: SpannmittelCollet, more general: clamping device
- 4343
- Zentrierschieber/ sich verjüngender SchieberCentering slide / tapering slide
- 431431
- Ringspaltannular gap
- 4444
- konischer Mantelflächenabschnittconical lateral surface section
- 4545
- konische Anlagefläche für Zentrierschieberconical contact surface for centering slide
- 4646
- Luftkanalair duct
- 461461
- Bohrungdrilling
- 462462
- Einstichpuncture
- 4747
- elastische Elementeelastic elements
- 4848
- Zugelement, hier StangeTension element, here rod
- 4949
- Spannelement, z.B. TellerfederClamping element, e.g. Belleville spring
- 5050
- Abdeckungcover
- 5151
-
erste Streben (von Antriebswelle 20 zum Zwischenblock 30)first struts (from
drive shaft 20 to intermediate block 30) - 5252
-
zweite Streben (von Zwischenblock 30 zum Spindelkopf 10)second struts (from
intermediate block 30 to spindle head 10) - 5353
- Kupplungselementcoupling member
- 5555
- erste Befestigungselemente für Streben 51 (z.B. Winkelstücke)first fasteners for struts 51 (e.g., elbows)
- 5656
- zweite Befestigungselemente für Streben 52 (z.B. Winkelstücke)second fasteners for struts 52 (e.g., elbows)
- 6060
- Luftzuführungs- und BetätigungseinheitAir supply and operating unit
- 6161
- Kolbenstangepiston rod
- 6262
- Kolbenpiston
- 6363
- Ausnehmung/ZylinderRecess / cylinder
- 6464
- Gehäusecasing
- 6666
- Kanalchannel
- 7070
- Prisma / Führungsprisma / StützprismaPrism / Guide prism / Support prism
- 7171
- Spannfingerclamping finger
- 7575
- Lünettebezel
- 7373
- Einstelleinheit für StützprismaAdjustment unit for support prism
- 7676
- Einstelleinheit für LünetteAdjustment unit for steady rest
- 8080
- Abstützeinheitsupport unit
Claims (11)
- A spindle (1) for a tool grinding machine comprising at least:- a spindle head (10) having a first longitudinal axis and being configured for receiving a clamping means (42), and- a rear spindle portion (20), having a second longitudinal axis and being configured for being received in a bearing support and as well configured as a drive shaft (20) for the spindle head (10),- a bearing being arranged between the spindle head (10) and the rear spindle portion (20) in order to connect same, wherein- the bearing transmits compressive and/or tensile forces in longitudinal direction from the spindle head (10) to the drive shaft (20) and wherein the bearing is bridged by at least one coupling (51, 52) for transmission of torques between the rear spindle portion (20) and the spindle head (10),characterized in that
the bearing being arranged between the spindle head (10) and the rear spindle portion (20) allows a tilting of the first longitudinal axis relative to the second longitudinal axis. - Spindle (1) according to claim 1,
characterized in that
the spindle head (10) and the rear spindle portion (20) have centering surfaces (45, 141) being respectively opposite to each other, between which centering surfaces a tapered centering slider (43) can be altered between at least a first position and a second position, wherein in a first position the bearing is bridged in a locking manner, whereby the spindle head (10) and the rear spindle portion are mutually centered. - Spindle (1) according to claim 1 or 2,
characterized in that
the bearing has a first and/or second partial bearing, wherein the first partial bearing has two complementary first bearing blocks with spherical-segment-shaped bearing surfaces (13, 33), and the second partial bearing has two complementary second bearing blocks with planar bearing surfaces (24, 34), the surface normals of which are parallel to the first or the second axis. - Spindle (1) according to claim 1 or 2,
characterized in that
the bearing has a first and/or a second partial bearing, wherein the first partial bearing has two mutually complementary first bearing blocks with first cylinder-segment-shaped bearing surfaces (13, 33), and the second partial bearing has two mutually complementary second bearing blocks with second cylinder-segment-shaped bearing surfaces (24, 34). - Spindle (1) according to claim 3 or 4,
characterized in that
the bearing has a ring-shaped or at least ring-segment-shaped intermediate portion (30) having at least one spherical-segment-shaped or cylinder-segment-shaped first bearing surface (33), and comprises at least one planar or a cylinder-segment-shaped second bearing surface (34) on its side facing away from the first bearing surface (33). - Spindle (1) according to any one of claims 3 to 5,
characterized in that
at least one of the partial bearings is a hydrostatic bearing with a fluid gap between at least two of the bearing surfaces (13, 24, 33, 34). - Spindle according to claim 6,
characterized in that
the bearing blocks of at least one of the partial bearings are magnetically preloaded against each other. - Spindle according to claim 7,
characterized in that
at least one permanent magnet is arranged in at least a first of two complementary bearing blocks for magnetic preloading, wherein the magnetic flux of the at least one permanent magnet is guided from a magnetic north pole thereof to a magnetic south pole thereof, thereby bridging at least once the air gap between the bearing surfaces. - Spindle according to any one of the preceding claims,
characterized in that
the spindle head (10) has a continuous recess (16), in one side of which at least one clamping means is located, which is connected to a tension element (28) being arranged in the recess and being preloaded against the spindle head (10). - Spindle (1) according to any one of claims 1 to 9,
characterized in that
the coupling has elastically deformable struts (51, 52) on both sides of the first and/or second axis, which struts connect the spindle head (10) and the spindle portion at least indirectly torsion-proof to each other. - Spindle according to any one of claims 1 to 10,
characterized in that
the bearing allows a radial displacement of the first longitudinal axis relative to the second longitudinal axis.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PL14786498T PL2934816T4 (en) | 2013-10-21 | 2014-10-17 | Spindle of a grinding machine tool |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013111599.3A DE102013111599A1 (en) | 2013-10-21 | 2013-10-21 | Spindle of a tool grinding machine |
PCT/EP2014/072304 WO2015059046A1 (en) | 2013-10-21 | 2014-10-17 | Spindle of a grinding machine tool |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2934816A1 EP2934816A1 (en) | 2015-10-28 |
EP2934816B1 true EP2934816B1 (en) | 2017-03-29 |
Family
ID=51752122
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14786498.7A Active EP2934816B1 (en) | 2013-10-21 | 2014-10-17 | Spindle of a grinding machine tool |
Country Status (8)
Country | Link |
---|---|
US (1) | US10065287B2 (en) |
EP (1) | EP2934816B1 (en) |
JP (1) | JP6205054B2 (en) |
KR (1) | KR101777147B1 (en) |
CN (2) | CN204277753U (en) |
DE (1) | DE102013111599A1 (en) |
PL (1) | PL2934816T4 (en) |
WO (1) | WO2015059046A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102016006092A1 (en) * | 2016-05-20 | 2017-11-23 | Klingelnberg Ag | TOOLS SPLIT MlT FORMWORK SYSTEM, OVERALL SYSTEM THAT COMBINES THE NEw TOOL SPLIT WITH MULTI-WAY SYSTEM AND METHOD FOR OPERATING A TOOL SPINDLE WITH A WALKING SYSTEM |
CN108673341B (en) * | 2018-08-01 | 2024-03-15 | 台州小助手智能科技有限公司 | Quick centering clamping mechanism |
JP6775276B2 (en) * | 2019-03-15 | 2020-10-28 | 株式会社ソディック | Hydrostatic fluid bearing equipment |
CN110369735B (en) * | 2019-08-19 | 2024-03-08 | 珠海格力智能装备有限公司 | Machine tool |
TWI785717B (en) * | 2021-08-04 | 2022-12-01 | 全鑫精密工業股份有限公司 | Direct-drive high-speed hydrostatic pressure grinder spindle structure |
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US2833544A (en) * | 1956-04-09 | 1958-05-06 | Prec Proc Co | Compensating tool holder |
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JPS61121860A (en) * | 1984-11-17 | 1986-06-09 | M S Ee:Kk | Holder device for grinding drill |
DD240157A1 (en) * | 1985-08-09 | 1986-10-22 | Mikromat Dresden Betrieb | WORKING SPINDLE FOR A TOOL MACHINE FOR FINISHING |
US4919547A (en) * | 1987-04-03 | 1990-04-24 | Schwartzman Everett H | Dynamically self-adjusted fluid bearing |
JP2641898B2 (en) * | 1988-04-30 | 1997-08-20 | 株式会社日平トヤマ | Processing equipment |
JPH0239803U (en) * | 1988-09-07 | 1990-03-16 | ||
DE8915435U1 (en) * | 1989-03-22 | 1990-06-07 | J. E. Reinecker Maschinenbau GmbH & Co KG, 7900 Ulm | Device for machining an approximately rod-shaped rotating workpiece |
JP3555634B2 (en) * | 1995-11-24 | 2004-08-18 | 豊田工機株式会社 | Spindle device |
JP4358318B2 (en) | 1998-03-05 | 2009-11-04 | アイシン精機株式会社 | Seat frame |
IL131525A0 (en) * | 1999-08-23 | 2001-01-28 | Leonid Kashchenevsky | Hydrostatic spindle unit with automatic self centering of the workpiece |
DE10118664B4 (en) * | 2001-04-14 | 2009-11-05 | C. Stiefelmayer Gmbh & Co. Kg | Clamping device for workpieces to be machined with imbalance compensation |
EP1419852A1 (en) | 2002-11-12 | 2004-05-19 | Rollomatic S.A. | Spindle unit |
DE10259257A1 (en) * | 2002-12-11 | 2004-06-24 | Marquart, Ingeborg | Device for central tightening of rotary driven parts has device for detecting deviations of part from circular rotation, computer for computing required control parameters to achieve circular rotation |
JP4730939B2 (en) * | 2004-03-31 | 2011-07-20 | コマツNtc株式会社 | Spindle device |
CN2695169Y (en) * | 2004-04-28 | 2005-04-27 | 洛阳轴研科技股份有限公司 | Machining tool speed-up electric main shaft multipurpose clamping head |
JP4665440B2 (en) * | 2004-06-14 | 2011-04-06 | カトウ工機株式会社 | Machining tools |
DE102005007038B4 (en) | 2005-02-15 | 2009-10-15 | Alfred H. Schütte GmbH & Co. KG | Workhead |
JP4846410B2 (en) * | 2006-03-30 | 2011-12-28 | シチズンホールディングス株式会社 | Spindle head device and machine tool |
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DE102009031027A1 (en) * | 2009-06-29 | 2011-01-05 | Maschinenfabrik Berthold Hermle Ag | Tool spindle for a combined milling / lathe with stationary and rotating tool |
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-
2013
- 2013-10-21 DE DE102013111599.3A patent/DE102013111599A1/en not_active Withdrawn
-
2014
- 2014-07-16 CN CN201420393584.9U patent/CN204277753U/en not_active Expired - Fee Related
- 2014-10-17 CN CN201480057510.0A patent/CN105764647B/en not_active Expired - Fee Related
- 2014-10-17 EP EP14786498.7A patent/EP2934816B1/en active Active
- 2014-10-17 JP JP2016526136A patent/JP6205054B2/en not_active Expired - Fee Related
- 2014-10-17 WO PCT/EP2014/072304 patent/WO2015059046A1/en active Application Filing
- 2014-10-17 PL PL14786498T patent/PL2934816T4/en unknown
- 2014-10-17 KR KR1020167013480A patent/KR101777147B1/en active IP Right Grant
-
2016
- 2016-04-21 US US15/134,709 patent/US10065287B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
WO2015059046A1 (en) | 2015-04-30 |
CN105764647A (en) | 2016-07-13 |
KR101777147B1 (en) | 2017-09-11 |
PL2934816T3 (en) | 2018-03-30 |
EP2934816A1 (en) | 2015-10-28 |
JP6205054B2 (en) | 2017-09-27 |
KR20160085275A (en) | 2016-07-15 |
US20160229027A1 (en) | 2016-08-11 |
US10065287B2 (en) | 2018-09-04 |
CN204277753U (en) | 2015-04-22 |
PL2934816T4 (en) | 2018-03-30 |
CN105764647B (en) | 2018-05-08 |
JP2016535683A (en) | 2016-11-17 |
DE102013111599A1 (en) | 2015-08-06 |
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