Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B24—GRINDING; POLISHING
  • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
  • B24B33/00—Honing machines or devices; Accessories therefor
  • B24B33/08—Honing tools
  • B24B33/088—Honing tools for holes having a shape other than cylindrical
• • 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
  • B24B33/00—Honing machines or devices; Accessories therefor
  • B24B33/02—Honing machines or devices; Accessories therefor designed for working internal surfaces of revolution, e.g. of cylindrical or conical shapes

Definitions

• the invention relates to a machine according to the preamble of claim 1, preferably a honing machine or a drill.
• FIG. 1 shows a spatial representation of a bore surface machined in this way with a local formation or extension 11 and a local constriction 22.
• This shape is the desired shape which is to be produced by the machining and which then becomes a precisely cylindrical bore under load in the operating state deformed.
• Such contingent contours deviating from the cylindrical shape are defined as inverted deviations from a cylindrical ideal shape, and z. As determined by finite element calculations or experimentally.
• a method for producing such bore surfaces deviating from the cylindrical shape is e.g. from EP 1 321 229 A1 and DE 4 007 121 A.
• Japanese Patent Publication JP 2000-291487A discloses a honing tool having piezoelectric feeders between the tool body and the honing stones (see Figures 6 and 7, reference numeral 22, and portions [35 and 36] of the description).
• a piezoelectric adjusting mechanism is described which is arranged in the tool body between radially opposed cutting edges.
• EP 1 790 435 A1 a tool is described with a basic delivery for full-surface machining of the bore surface and an additional fine delivery for the production of deviations in the shape of the cylinder, which is formed by a piezoelectric element arranged between the cutting strip and the support strip.
• FIG. shows a cross section through such a machined bore surface with a formation 11, which is defined by a change in shape ds within an angle dphi.
• cylinder distortions with Fourier coefficients up to the 8th order must be able to be generated.
• the speed of the tool can be selected as high as possible. This requires a delivery dynamics, which can bring about the desired radial adjustment of the cutting means (eg a honing stone or a drill bit) correspondingly fast.
• the radial delivery speeds are to be defined, which result from the cutting speed required by the cutting tool.
• the object underlying the invention is therefore to provide a machine for producing non-cylindrical bore surfaces, which is simpler in construction and thus less expensive than the known machines and has an improved delivery dynamics.
• Tool receiving unit which contains the means for fine delivery in the form of an axially parallel direct acting linear drive, as a non-replaceable part of the machine spindle and thus the machine, whether a honing or a fine boring machine is formed, on which the tool unit - depending on the required tool - is interchangeable arranged.
• the device for fine delivery in this case preferably the linear drive, is therefore not, as in the prior art, separately installed for each tool in the tool unit, but is only once to be provided on the machine side, in the tool receiving unit to be arranged there, connected to the various tool units that can be the actual editing tools and the Deflection means for the delivery, but no longer the - relatively expensive - must contain means for fine delivery.
• one or more axially parallel acting linear drives for independent delivery of processing tools or cutting means (honing stones or drill bits) may be provided.
• the Linear drives, the z. B. are designed as piezoelectric linear actuators are activated by an electric drive and generate an axial movement of a shock ice with a certain force and speed, which acts on the feed rod for the radial delivery of the cutting means of the processing tools.
• the invention thus provides to constructively separate the tool unit and the tool holder with the linear drive and to associate the linear drive for the dynamic feed (fine feed) of the tool holder unit and thus of the machine or of an assembly that is independent of the interchangeable tool unit.
• the tool unit is interchangeably arranged.
• the tool unit only contains exclusively components for deflecting the machine-generated lifting movements in the feed movements for the processing tools and possibly the independent feed movements for the guide rails, and the processing tools and possibly the guide rails themselves.
• the feed rods are coaxial to the plunger or the Stoßein the linear drives of the tool holder unit.
• the plungers exert an axis-parallel force to the center on the aligned arranged Zustellstangen.
• the feed force is transmitted to the radially movable machining tools.
• the end faces are designed so that no normally acting pushing forces can be transmitted.
• the Zustellstangen wedge surfaces are worked, which deflect the axial movement in a radial feed movement.
• the desired nominal shape can be achieved at high cutting speeds and small deformation segments with a large radial deformation with a high accuracy of a few micrometers.
• the application of the cutting means with a coarse feed improves the dynamic feed behavior, since the fine feed should only work in the area of the local shape changes. Since the tool holder unit with the m it integrated fine delivery of the tool unit is structurally separated, you need only m the tool unit to arrange only simple mechanically operated tools without their own delivery drives. The tool unit can be exchanged for different machining tasks.
• the Kuhl lubricant only direct contact with the tool, but not to the tool receiving unit, in which the means for fine delivery are arranged.
• the linear drives are thus protected against the harmful influence of aggressive liquids.
• FIG. 1 shows a bore surface with a local extension
• FIG. 2 shows the cross section of a bore surface according to FIG. 1;
• FIG. 3 shows a first exemplary embodiment
• Figure 5 shows a second embodiment
• Figure 5a is a view in the direction of the arrows Va-Va in Figure 6;
• Figure 5b is a view in the direction of arrows Vb-Vb in Figure 6;
• Figure 5c is a view in the direction of the arrows Vc-Vc in Figure 6;
• FIG. 6 shows a third exemplary embodiment
• FIG. 7 shows a fourth exemplary embodiment
• Figure 8 shows a fifth exemplary embodiment
• FIG. 9 shows a sixth exemplary embodiment
• FIG. 9a shows the detail indicated at IXa in FIG. 9 in an enlarged view.
• the first exemplary embodiment according to FIGS. 3, 4a and 4b shows, as part of a honing machine, a tool receiving unit 1 for fine delivery. It has axially parallel direct-acting linear drives 1-06, which can be arranged all around (see also FIG. 5a), of which only one is shown in FIG is shown.
• the tool unit 2 is interchangeably arranged on the tool-holder unit 1, the tool-holder, ie the honing blade 2-05 provided with the cutting-medium covering 2-06, and the guide bar 2-04 or guide rails shown radially opposite one another for supporting the honing stone or honing stones , and the associated feed rods 1- 03 (for the honing stone) and 2-02 (for the guide bar).
• the tool unit 2 rests with its end face 2- 09 on the end face 1-02 of the tool receiving unit. Both are interconnected by suitable means 1-16, for example screws.
• the tool receiving unit 2 is simple. It can be easily and simply replaced without the tool holder unit 1, in which the axially parallel linear direct-acting means for fine delivery, namely the linear drive 1-06, are arranged to replace.
• the linear drive 1-06 When using a - expensive - piezoelectric Linearzustellelementes means a significant cost reduction.
• Embodiments of a direct-acting linear drive is mentioned, it is meant that initially no Hubver alleviatrungen by gear-like translations, which are possible, however, are taken into account.
• the tool receiving unit 1 and the tool unit 2 abut each other with the end faces 1-02 and 2-09 and are easily detachable from each other.
• the means 1-16 for this purpose are familiar in the art and therefore only hinted at.
• the tool receiving unit 1 is located in the housing 1-01, which is connected at its upper end to the machine spindle 5. On the machine side, as is customary in honing, rotational movement, stroke movement and feed movement are forwarded to the tool receiving unit 1.
• the delivery takes place in double mode via the delivery rod 1-09 for the guide bar 2-04 and the infeed tube 1-10 for the rough delivery of the honing stone 2-05.
• the feed rod 1-09 is guided in the infeed tube 1-10.
• the feed tube 1-10 is connected to the carrier 1-13. Both the infeed rod 1-09 and the infeed tube 1-10 are independent of each other. Both are for delivery axially - independently - by the control of honing or fine boring machine on which the machine spindle 5 is arranged, moved down.
• the lower end of the feed rod 1-10 is connected to the upper flange 1-14 of the carrier 1-13.
• linear drive 1-06 is arranged between the two flanges 1-14 of the carrier 1-13 serving for fine delivery of the honing stone 2-05 in the axial direction. It is moved from the bottom of the upper of the two flanges 1-14 down and actuated as an actuator the plunger 1-05.
• the linear drive 1- 06 is powered by the electrical lines 1-07 with Ant ⁇ ebs intricate and control signals. The supply of energy and control signals via slip rings 1- 08. Also contactless inductive telemet ⁇ sche transmission systems can be used.
• the linear direct drive 1-06 operates e.g. piezoelectric with a stroke of up to
• piezoelectric actuators are designed with a high level of centrifugal force. Also electromagnetic drives according to the principle of the plunger coil or the magnetostriction, electro-rheological or magneto-rheological actuators are possible.
• the summation means 1-12 are formed by at least one linear actuator 1-6 (as shown). However, as already mentioned above with reference to FIG. 5a, it is possible to arrange further linear drives between the flanges 1-14 about the axis of the system, so that a separate linear drive can be assigned to each honing stone.
• the housing 1-01 has a sealing air hole 1-11 through which a (otherwise generated) low pressure in the housing held and thus the penetration of liquid is prevented by leaks existing outside.
• the linear drive 1-06 is, as already mentioned, provided at its lower end with a plunger 1-05 as an actuator whose linear motion is transmitted to the Zustollstange 1-03. In this way, the fine feed effected by the linear drive 1-06 is superimposed on the coarse feed predetermined by the feed rod 1-10 on the machine side.
• the installation of linear direct drives 1-06 is free of lateral forces.
• the play and lateral force-free power transmissions 1-04 are only symbolically represented as a ball and can be designed as joints as flat or curved sliding surfaces or otherwise. You must transfer train and pressure without play and also have rotational degrees of freedom, so that the Zustollstange 1-03, which rests with its wedge-shaped Zustellflache 1-031 at its lower end to the also wedge-shaped Zustellflache 1-031 the honing stone 2-05 m vollflachiger Plant can align to this. So you have u. U. can tilt slightly on the power transmission 1-04 from the plunger 1-05. They can only do this if the power transmission 1-04 does not transmit any lateral forces. Similarly, a compensation of a small axial offset between plunger 1-05 and Zustellstange 1-03 is possible.
• Em linear drive which is formed by a piezoelectric element, can move the feed bar with great force down.
• For restoring the linear drive 1-06 only a smaller force is available.
• the return is therefore supported by the return spring 2-07 or even completely applied.
• the tool body 2-01 contains the feed rod 2-02 provided with two cone-shaped infeed surfaces, on which the infeed rod 1-09 acts from above.
• the conical Zustellflachen 2-021 and 2-022 cooperate with wedge-shaped Zustellflachen on the support bar 2-03, where immediately adjacent radially a guide bar 2-04 is arranged so that in this way the axial movement of the Zustellstange 1-09 in a radial movement of the guide rail (s) implemented (deflected) is.
• a guide bar 2-04 may be arranged along the circumference of a workpiece 4, between which four Zustollstangen 1-03 can be arranged along the circumference.
• Both Zustellierien are superimposed on the Zustollstange 1-03 effective and m the tool unit 2 in a radial Feed movement of the Schneidmxttelbelages 2-06 reacted to the bore surface 4-01 of a workpiece 4 or deflected (see., The drawn arrow).
• the return spring 2-07 supports the play and lateral force-free power transmission 1-04 in the feed line between linear drive 1-06 and feed bar 1-03 at a relief (return) of the Zustellstranges.
• the feed rod 1-03 may also be made of a material of lower density, so that the movement of the linear drive can be transmitted even more reliably without delay due to a low mass inertia.
• the restoring spring 2-07 is to be designed so that when relieving the honing stone with the spring force an upward acceleration is achieved, which is at least as large as the upward acceleration of the shock ice 2-05, so that an axial positive engagement between the feed rod and plunger is ensured.
• the feed rod 2-02 is designed so that it forms an angle with the chamfer face 1-31 of the feed rod 1-03, which lies outside the range of a self-locking.
• the feed rod 1-09 is moved axially downwards on the machine side. It strikes the infeed bar 2-02, by which the guide rails 2-04 are applied against the bore surface 4-01.
• the infeed tube 1-10 moves the carrier 1-13 of the means 1-12 for fine delivery and over this the feed rods 1-03 axially downwards and thus prints the Schneidstoffbelag 2-06 of the honing stones 2-05 to the bore surface 4-01 of Workpieces 4.
• the linear actuator 1-06 is controlled along the circumference of the bore, ie as a function of the angle dphi and m depending on the vertical position of the bore. In this case, each honing stone is assigned to a position change to be achieved at this point.
• a honing stone can also be mounted on a support strip with multiple wedge surfaces, as shown by the example of the guide bar 2-04 and their arrangement on the support bar 2-03.
• Integrated dimensional, position and shape measuring devices determine the quality either m process or post process in a separate measuring stroke (see also the force sensor 130 in Figure 7 and 9).
• FIG. 4a shows the mode of operation of the linear drive 1-06 with a delivery force F within a formation 11.
• the delivery force F always has a constant value, as shown in the diagram m FIG. 4a above, ie independent of the delivery travel s. For each overrun within this shape-changing segment, therefore, the currently present shaping 11 'is extended by a likewise constant amount ds.
• FIG. 4b Another mode of operation of the linear drive 1-06 is shown in Figure 4b.
• An appropriate power application is controlled so that the delivery force F with increasing Delivery path s decreases (see the diagram), so that at the beginning of processing at each overreach a relatively large shape 11 'is generated.
• the radial feed path ds and therefore also the radial material removal ds become smaller.
• the exemplary embodiment of Figure 5 differs from that of Figure 3 by an improved leadership of the tool holder unit 1 in the housing 1-01. This is ensured by the fact that the linear drive 1-06 is applied directly to the upper flange 1-14 of the carrier 1-13 and thereby, that the power transmission from the plunger 1-05 of the linear actuator 1-06 on the Zustollstange 1-03 via a friction - and wear-resistant carbide plate 1-17 takes place.
• the stroke of the coarse adjustment by means of the Zustellrohres 1-10 is denoted by 1-15.
• the stroke of the fine adjustment is determined by the linear drive 1-06.
• the two flanges 1-14 of the carrier 1-13 are formed relatively thick and matched with their outer dimensions on the cylindrical inner surface 1-18 of the housing 1-01 so that the carrier 1-13 m the housing 1-01 in his up and Off movement is guided safely and backlash-free. This makes the guided surface more stable.
• the inner surface 1-18 is processed accordingly as tribologically stressed Fuhrungsflache.
• the flanges are 1-14 housed in the housing 1-03 against rotation.
• they have grooves 1-19, into which a feather key 1-20 (or a pin) protrudes radially as rotation, so that although a longitudinal movement of the flanges 1-14, but not a rotational movement is possible.
• This arrangement thus represents an anti-rotation device for the carrier 1-13 in the housing 1-01.
• four linear drives 1-06 are provided in the exemplary embodiment according to FIGS. 5, 5a-5c along the circumference (circular line K). These are, as also shown for the linear drive 1-06 in Figure 5, on the underside of the upper flange 1-14 of the support 1-13.
• the plungers 1-05 arranged at the lower end of the linear drive 1-06 are designed to be as short as possible, so that possibly occurring bending moments, which could act on the linear drive, are as small as possible.
• the tungsten carbide plate 1-17 ensures high wear resistance even with permanent pulse operation.
• the end face of the feed rod 1-03 is designed as a dome, so that only one point contact takes place (see also the comments in the description of the embodiment of Figure 7).
• the linear actuators 1-06 can be force-controlled via a force measuring sensor, regulated by a strain gauge or operated in unregulated operation (the feed travel is proportional to the applied voltage).
• the feed rod which was provided in the embodiments described above with the reference numeral 1-03, now formed by two Zustellstangen sections 1-30 and 1-31, which are formed separately from each other and via a compression spring 1- 32 are in operative connection with each other.
• the linear drive 1-06 is active as a power transmission and not directly as an actuating means.
• the feed tube 1-10 is formed as shown in FIG. It moves down and pushes the linear actuators 1-06 over the bottom of the upper flange 1-14 down and thus acts on the Zustollstangenabêt 1-30 on the compression spring 1-32 on the Infeed bar sections 1-31.
• Characterized the honing stones 2-05 are pressed against the cylindrical inner surface of a bore of the force of the compression spring 1-32, as is particularly appropriate when smoothing a pre-machined shape.
• the exemplary embodiment according to FIG. 7 provides for suitable measures in order to generate the opposing forces which, upon activation of the linear drive 1-06, are produced by the pressure of the honing stones 2-05 on the inner surface 4-01 of a bore in the workpiece 4 and, for example, in the exemplary embodiment according to FIG 5 tend to print the infeed tube 1-10 upwards. This is done by a locking device.
• the locking device is formed by the fact that the delivery of the honing stones 2-05 no longer by a directly from the machine operated Zustellrohr (like the infeed tube 1-10 of Figure 3, 5 and 6), but by a feed motor
• the feed motor 111 rotates via a shaft 113, a gear 114 which is in engagement with a ring gear 115 to a feed nut 116.
• the feed nut is mounted by bearings 117 in the housing 112.
• the feed nut 116 is internally provided with a trapezoidal thread 118, which is in engagement with the trapezoidal thread 119 on the outside of a spindle nut 120.
• the Zustellhulse 125 is internally provided with an annular groove 126 in which a flange 127 of a Zustellrohres 128 is added, which is an integral part of the Zustellrohres 128.
• the feed tube 128 now acts - with the interposition of a force measuring sensor 130 - on the upper flange 1-14 of the carrier 113.
• the flanges 1-14 are secured in the housing 1-03 by Nut-feather Verbmditch 131 against rotation.
• the force measuring sensor 130 is used for readjusting the coarse adjustment, which is required with progressive removal by the fine feed.
• the honing stones are therefore always created with constant force and superimposed by the locally acting delivery force of the fine adjustment.
• the lower surface of the upper flange 1-14 presses on the linear drive 1-06, of which only one is shown, of which, however, analogously to FIG. 5a, in a circle K can be arranged around the axis of the arrangement, for example, four pieces.
• the lower end of the linear drive 1- 06 acts on a hard metal plate 1-17 without lateral force on the rounded tip 136 of a Zustellstattes 135 of the Zustollstange 1-03, which is provided with two oblique Zustellflachen 1-31, the axial adjustment with appropriately trained Schragflachen a Collation 2-05 cooperate, move them in the radial direction outwards and thus bring the thereon disposed Schneidstoffbelag 2-06 to act on the inner surface 4-01 of the workpiece 4, wherein, as shown, the coarse feed by the feed motor 111 and the fine feed through the linear drive 1-06 takes place.
• the housing 1-01 of the tool receiving unit is surrounded by a device 1-40 which, as schematically illustrated in FIGS. 1-41, is rotationally arranged on the machine frame by an anti-twist device and has the slip rings 1-42, which form an electrical connection to slip rings 1-43, which are arranged on the component 1-44, which rotates with the horroderemheit.
• a device 1-40 which, as schematically illustrated in FIGS. 1-41, is rotationally arranged on the machine frame by an anti-twist device and has the slip rings 1-42, which form an electrical connection to slip rings 1-43, which are arranged on the component 1-44, which rotates with the convinced Wegfactemheit.
• Schleifrmgverbmdung carried the electrical control and power supply of the linear actuators 1-06.
• FIG. 8 shows a further exemplary embodiment, in which the tool unit is designed as a fine boring tool 3.
• the end face 3-06 of a forming tool 3 abuts.
• the means for fine delivery 1-12 with energy supply and structural design largely correspond to those of the exemplary embodiment according to FIG. 3.
• the infeed bars 1-03 actuate a shaping tool, ie a cutting means with a defined cutting geometry.
• a feed pin 3-05 On the wedge-shaped Zustellflache 1-031 is a feed pin 3-05 with its Zustellflache 3-051 on. With axial displacement of the feed rod 1-03 of the feed pin 3-05 is printed radially outward.
• the presetting of the cutting takes place analogous to the coarse adjustment, as in the embodiments described above, by a centric force which moves the fine feed 1-12 down and thus brings the cutting plates 3-04 radially in the processing position.
• the individual local deformation segments are then produced again by independently making a fine feed for each cutting edge to be produced at the point where the cutting insert is currently located.
• the exemplary embodiment according to FIG. 9 is constructed essentially the same as that according to FIG. 7, but with the proviso that, as in the case of FIG. 8, it again is a tool receiving unit which receives as a shaping drilling tool.
• the feed sleeve 125 and the feed tube 128, surrounded by the non-rotating housing 112 on a feed motor 111 is arranged, which axially displaces the spindle nut 120 in the manner described above, as indicated by the double arrow.
• an oblique feed surface 3- 51 (see Figure 9a) is provided which presses a fixed to a blade holder 301 Feinbohrschneide 301 in the radial direction to the outside and thus delivers to the bore surface 4-01 in the workpiece 4 ,
• the blade holder 300 is fixedly connected to the tool body 3-01, for example screwed thereto.
• the cutting edges 3-04 can be arranged radially and / or axially in different positions.
• Both embodiments describe a tool for producing molds 11 and constrictions 22 at a bore.
• a machine side arranged
• Tool holder unit with integrated linear direct drives is merely the tool unit to adapt to the respective process.

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• 2007
  • 2007-08-04 DE DE102007038123A patent/DE102007038123B4/de not_active Expired - Fee Related
• 2008
  • 2008-07-30 CN CN2008800203189A patent/CN101765480B/zh active Active
  • 2008-07-30 EP EP08785211.7A patent/EP2170556B1/de active Active
  • 2008-07-30 US US12/665,112 patent/US8292695B2/en active Active
  • 2008-07-30 BR BRPI0812894A patent/BRPI0812894B1/pt not_active IP Right Cessation
  • 2008-07-30 WO PCT/EP2008/006265 patent/WO2009018949A2/de active Application Filing
  • 2008-07-30 JP JP2010516430A patent/JP5121931B2/ja not_active Expired - Fee Related

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