BORING HEAD FOR MACHINE TOOLS AND RELATED MACHINING METHOD

Abstract: Accurate bores can be obtained automatically on CNC boring machines by a controllable radius boring bar. A deliberately undersized pilot bore is first made then the correct bore is approached in several more machining operations, thus allowing for boring bar deflection and other errors. In the present invention, a boring bar (113) with a tool tip (114) carries strain gauges (128 to 130) and is part of a boring head (110). The boring head includes a U-axis (115) driven by a motor (116), and a sensor (138) generating a signal representative of the rotational speed of the boring head. A computer (136) uses signals from the strain gauges and the sensor to determine the swept diameter of the tool tip taking account of boring bar deflection and centrifugal force, and applies a signal to the motor (116) to change the U-axis (115) of the boring bar to compensate for any difference from a target diameter. Using the boring head the number of machining operations required to produce an accurate bore is reduced, sometimes to a single operation.

Description: BORING HEAD FOR MACHINE TOOLS AND RELATED MACHINING METHOD The present invention relates to a boring head, particularly for use in CNC machining and to a method of machining using the head. Accurate internal or external bores are, at present, obtained automatically and unmanned on CNC boring and milling machine centres by using a boring head that has a controllable radius boring bar. In order to obtain accurate diameter bores, the controllable radius, i.e. the U-axis, is automatically adjusted to give a deliberately undersize pilot bore for internal boring or oversize for external boring. A tool change is then made in which the boring head is replaced by a touch trigger probe which is used to measure the diameter of the pilot bore. The difference between the diameters of the target bore and the pilot bore is determined by a machine computer and the boring head is replaced in the machine tool spindle. Next the U-axis is changed by half the aforementioned difference in diameters and the pilot bore is re-machined. The measuring operation using the touch trigger probe is repeated and if the bore is not in tolerance, the boring head is replaced, the U-axis adjusted in the same way and the bore re-machined. The process is repeated until the bore is within tolerance. The method outlined in the preceding paragraph suffers from bore diameter repeatable errors which are mainly caused by shank reseating errors, tool tip wear and boring bar deflection. Shank reseating errors cannot be eliminated using the above technique because the touch trigger probe and boring head are used alternately. Tool tip wear is reduced by periodic bore diameter measurement using a touch trigger probe or by a specialised tool tip wear measurement and compensation system. Boring bar deflection error caused by cutting forces is reduced by taking more than one cut which is time-consuming and becomes less effective as the tool tip wears. According to a first aspect of the present invention there is provided a method of machining internal or external bores to a target diameter, comprising mounting a boring head in a machine tool spindle, the boring head having a boring bar with an integral tool tip and U-axis drive means, coupled to one end of the boring bar, for moving the boring bar in a direction normal to that axis of the machine tool shank about which the tool tip rotates, carrying out a boring operation using the boring head and the machine tool with the U-axis initially set to cut the target diameter, obtaining a signal representative of any deflection in the boring bar between the tool tip and the said end as the boring operation proceeds, and making adjustments to the U-axis to minimise any difference between the target diameter and the swept diameter of the tool tip, based on the deflection signal and taking into account centrifugal forces in the boring bar. According to a second aspect of the present invention there is provided a machine tool boring head comprising an elongated boring bar having a tool tip, a shank for mounting the boring head in the machine tool spindle, U-axis drive means, coupled to one end of the boring bar, for moving the boring bar in a direction normal to that axis of the shank about which the tool tip rotates when rotated by a machine tool, sensing means for providing a signal representative of any deflection in the boring bar between the said end and the tool tip, and means for providing a signal representative of the rotational speed of the boring bar. The U-axis drive means is preferably capable of providing substantially all adjustment necessary to set the swept diameter of the tool tip. Alternatively the U-axis drive means may be capable of providing adjustment of the tool tip over a range of at least 5% (or, better, 10%) of the maximum possible swept diameter of the tool tip. According to a third aspect of the present invention there is provided a system comprising the boring head of the second aspect, and means for determining change in swept diameter of the tool tip from, at least, the deflection signal and for providing an error signal representative of the difference between the swept radius so determined and a target radius, the said means being coupled to the U-axis drive means to drive the boring bar in a direction which minimises the error signal. The main advantage of the invention is that the tool tip can machine a bore to the target diameter in one operation, or at least in fewer operations than would otherwise be required. The shank reseating error mentioned above can be eliminated and tool tip wear and boring bar deflection errors can be practically eliminated. Further the time for machining each bore is much reduced since usually only one cut is required and the technique of alternately measuring and cutting is avoided. The sensing means may comprise four strain gauges axially mounted on the boring bar near that end which is coupled to the U-axis drive means. The means for determining change in swept radius of the tool tip may comprise a computer coupled to receive input signals from the strain gauges, a U-axis displacement sensor for providing a signal representati e of movement of the tool tip in the U-axis direction and a rotary position sensor for providing a signal indicating the speed of rotation of the tool tip. The U-axis drive means may comprise a lead screw coupled to the said one end of the boring bar, a clutch for engaging a U-axis drive motor mounted on a machine tool spindle, and belt drive means coupling the clutch to means for driving the lead screw while machining takes place. Certain embodiments of the invention will now be described by way of example with reference to the accompanying drawings, in which:- Figure 1 is a schematic cross-section showing a boring head according to the invention, Figure 2 is a cross-section in the direction I-I of the boring bar of Figure 1 , Figure 3 is a flow chart of an algorithm for deriving a signal to correct the position of the tool tip of the boring head while machining is in progress, Figure 4a is a schematic perspective view of a rotary datumiπg probe using a planar spring, Figures 4b and 4c are plan views of part of the probe of Figure 4a and of another embodiment showing how they are used in practice, Figure 5 is a graph showing deflection of the planar spring versus rotation of a spindle carrying the spring, Figure 6 shows an exploded view of a rotary datuming touch trigger probe (RDTP) using fixed arcuate surfaces, Figure 7 shows an RDTP employing three arcuate surfaces enabling internal and external datuming, Figure 8 shows a mounting for the arrangement of Figure 6 which allows "overtravel" when a tool tip is brought into contact with the arcuate surface, and Figure 9 shows an RDTP employing four parts of an arcuate surface and four overtravel units. The boring head 110 shown in Figure 1 is a tool changeable device which can be mounted on a machine tool spindle for use with CNC boring, milling and flexible manufacturing machine tools. In operation, a shank 111 is mounted on a machine tool spindle 112 so that a boring bar 113 with a tool tip 114 is rotated to machine a diameter Dj shown, in this example, as an—internal diameter. The U-axis 115 is driven by an external motor 116 mounted on the machine tool spindle 112. The motor 116 drives through a clutch 117 to a belt drive 118 contained in a static collar 119. Within the static collar the belt drive 118 drives a wheel 121 (shown in section) having bearings 122. A gear wheel 123 meshes internally with the wheel 121 driving a worm 124 and a worm wheel 125 fixed to a lead screw 126. The root of the boring bar 113 is mounted to move along as the lead screw 126 rotates. Thus the U-axis 115 can be adjusted from the drive motor 116. Four strain gauges 127 to 130 are axially mounted on the boring bar adjacent to the end coupled to the lead screw. Connections from the strain gauges are taken to a strain gauge amplifier 132 and then by way of a data transmitter 133 and non-contact interfaces 134 and 135 to a computer 136 associated with the boring head. A U-axis displacement sensor 137 provides a signal representative of change in position of the boring bar and this signal is passed by way of the data transmitter 133 and the interfaces 134 and 135 to the computer 136. A signal representative of the rotational speed of the boring head is provided by a rotary sensor 138 coupled by way of the interface 135 to the computer 136. Electrical power for the strain gauge amplifier and the data transmitter is provided by two contacting or non-contacting interfaces 139 and 140 indicated schematically. As is explained in more detail below, the computer 136 determines change in swept diameter of the tool tip due to the radial deflection Δ D and the tangential deflection ΔJG (see Figure 2) of the tool tip 114 from the signals from the strain gauges 127 to 130. These deflections are caused by the tool tip radial and tangential cutting forces FR and Fj, respectively, together with centrifugal force loading the boring bar. The boring bar deflects under centrifugal loads which are approximately uniformly distributed along the length of the boring bar, and the cutting forces which are concentrated loads at the end of the cantilevered boring bar cause further deflection. The computer 136 calculates the centrifugal loading from the- boring bar mass and geometry, the U-axis displacement as sensed by the sensor 137 and the rotational speed of the boring head as sensed by the sensor 138. A signal representative of target bore diameter is applied to the computer and the computer determines the change in swept diameter of the tool tip 111 during boring operations from the data sent to it. An output signal is sent by the computer to a motor drive control 141 whereby the U-axis is adjusted to make the swept diameter Dj equal to the target diameter. The above procedure does not explain how the position of the tool tip is datumed in relation to the U-axis before machining is started. This operation may for example be carried out unmanned on the machine tool and in process by using either the rotary datuming probe (RDP) or the rotary datuming touch trigger probe (RDTP) described in a copending application of even date (Inventor: F.M.J. Nickols) and also described later in this specification. The RDP or the RDTP allows the computer 136 to determine an offset UOFF for the U-axis so that the swept diameter Dj is calculated by the computer from the following equation: Dj = 2(u + UOFF) + ΔD where ΔD is the increase of tool tip swept diameter brought about by cutting and centrifugal forces, and U is the output of the U-axis sensor. The U-axis is initially set with Dy = 2(U + UOFF) -° 9 ive tne required value of Dj and then as soon as machining starts ΔD is taken into account and corrections are automatically made. An error which is likely to occur is caused by the tool tip being misaligned with respect to a line passing through the centre of rotation of the boring head and parallel to the U-axis. This lateral misalignment, Δ m produces a swept diameter error which is zero at the datumed radius but progressively increases in magnitude above and below this diameter. The computer 136 may carry out a calculation to determine the misalignment Δ m from multiple values of UOFF calibrated at different radii. The misalignment value is then used by the computer in calculating Dj. The tool tip cutting forces produce deflections in the machine tool and workpiece itself and the computer 136 can take account of these deflections which would otherwise produce errors in bore diameter and circularity. Usually, however, where very accurate bores are required a last fine cut is taken where the deflection of the machine tool and workpiece are negligible. An explanation of the way in which the change in swept diameter or radius under the influence of various forces is calculated by the computer is now given. Change in swept radius of the boring bar is due to the following forces:- a) centrifugal force (a distributed load acting along the bar), b) a radial component of the cutting force, FR c) a tangential component of the cutting force, Fj, and d) torsional force which is likely to have an insignificant effect. The signals from the strain gauges 127 to 130 and the sensor 138 allow the change in swept radius to be calculated. The increase in swept radius due to centrifugal force is given by Δrjp = k-| ω2r where -\ is a constant found empirically but approximately equal to k D , and 8EI where L is the length of the boring bar, m is the mass of the boring bar, E is Young's Modulus for the material of the boring bar, and I is the second moment of area of the cross-section of the boring bar. The swept radius change due to the radial component of the cutting force is calculated from the radial strain CR obtained from the output of the strain gauges 128 and 130. However the strain due to centrifugal force CCF must first be subtracted from CR to give the strain e r due to the radial cutting force component, that is The strain CQF due to centrifugal force is given by where <2 is a constant found empirically but approximately equal to , 2EI ω is the angular velocity of the boring bar, r is the distance of the centre of gravity of the boring bar from the axis of rotation, and y is the radius of the boring bar (which is assumed to be cylindrical). Finding CQF allows c r to be found and then swept radius Δ r change due to the radial cutting force component is given by Δ r = -k3e r where k3 is a constant found empirically but approximately equal to L2 3 V Note that the radial cutting force reduces the swept radius. It can be shown that the change 5 in swept radius due to the tangential component is given by ϋa? 2 5 = 2r ε T where e- j - is tangential strain obtained from the strain gauges 127 and 129, and k_Λ is a constant found empirically but approximately equal to _=_ 3y Any change in swept radius δ r due to torsion in the boring bar is a function of ey and r, where f(r,ey) can be determined theoretically and confirmed by experiment. Thus the total change ΔR in swept radius is given by Δ R = &CF + Δ r + 5R + δ r An algorithm for the computer 36 to determine ΔR is given in Figure 3. Although δ r is shown in Figure 3 it is usually not necessary to take change in swept radius due to torsion into account. The invention can be put into practice in many other ways than those specifically described above, for example in various types of machining operations, and by using a different type of U-axis drive. The deflection of the boring bar can be measured optically, preferably using a laser, as an alternative to using strain gauges. A description of an RDP and an RDTP now follows. In Figure 4a a rotary datum probe (RDP) includes a circular spigot 10, a hardened steel half cylinder 11, a planar spring 12 and an axle 13, all mounted by way of a fixed member 14 on a machine table 15. The axes of the spigot 10, trie half cylinder 11 and the axle 13 are all coaxial and, for example, the components 10, 11 and 13 may all be manufactured by turning in a lathe with half of the complete cylinder cut by the lathe later milled away to provide the half cylinder 11, and with the planar spring milled into the section between the half cylinder 11 and the axle 13. The half cylinder is mounted for rotation on the axle 13 by way of two precision angular contact bearings 16 and 17 which are axially preloaded to eliminate radial and axial play. A flat plate 18 is attached to the half cylinder 11 over a plane coincident with the axis of the half cylinder. The plate 18 projects a little beyond the diameter of the half cylinder. In operation, a machine tool locates the position of the spigot 10 using a touch trigger probe 21 indicated in various positions by means of . chain dotted lines. The touch trigger probe is then exchanged for a boring head set so that its axis of ■ rotation is nominally coincident with the axle 13. The boring head carries a boring tool 22 with a cutting tool tip 23. The radial position of the tool 22 is controlled by a drive which moves the tool along a U-axis to vary the radius described by the tool tip. The boring head is now used to drive the tool tip to a radius greater than that of the half cylinder 11 and the boring bar is rotated to position the U-axis at an angle 24 (see Figure 4b) which is typically 5° to the X-axis. The boring head is now lowered over the half cylinder 11 so that the tool tip takes up a position alongside the half cylinder as shown at 25 in Figure 4b and the U-axis is now driven with no change in X, Y or Z coordinates to bring the tool tip into contact with the half cylinder as shown at 26 -in Figure 4b. The tool tip is driven a little further towards the half cylinder so deflecting the planar spring. The U-axis is now rotated to move the tool tip into contact with the plate 18 (see position 27 in Figure 4b). Up to this point the half cylinder 11 is held stationary by a detent system consisting of a disc 28 mounted on the axle 13 and having an inset 29 which engages with a rotary bearing 31 mounted on spring- loaded plunger 32. When the tool tip 23 engages the plate 18 the detent torque is overcome and continued rotation of the U-axis causes the tool tip to rotate the half cylinder 11. Rotation of the U-axis is continued through a further 360° and the half cylinder also rotates. In general the axes of the boring bar and the axle 13 are not exactly aligned and deflection of the planar spring 12 varies during rotation as shown in Figure 5. The initial deflection of this spring is chosen to be within the measurement range of the planar spring and to ensure that contact between the tool tip and the half cylinder is maintained when the U-axis is rotated through 360°. Deflection is measured by two strain gauges which are mounted inside the planar spring 12. For small radial displacements of the half cylinder 11 movement is essentially orthogonal to the axis of the axle 13 with very little axial displacement of the half cylinder 11. The position of the tool on the boring bar is held in a register of a computer associated with the machine tool which may be the computer 136. The contents of this register (U) are now set according to: U = ^ ~ Δ where D is the diameter of the half cylinder 11, and Δ is the mean deflection of the planar spring 12. The mean deflection is calculated by the computer from the outputs of the strain gauges 33 and 34 as the tool tip is rotated in engagement with the plate 18 through 360°. In a simplified but less accurate method, the mean of the minimum and maximum deflections only are taken. Having set the U-register in this way, any required change in the radius of the circle described by the tool tip may, assuming that movement along the U-axis is accurately measured, be set by driving the tool along the U-axis and updating the contents of the U-register from a counter whose contents represent movement along the U-axis. For example with an increase in radius of R the U-axis register is updated according to: U = U + R. Similarly if any decrease in radius R is required' then the U-axis is driven by the amount R and the U-axis register is updated as: U = U - R. The radius of a tool set for internal boring can be set using an RDP similar to that of Figure 4a except that a concave arcuate surface replaces the convex surface. Figure 4c is a plan view with the concave surface shown at 11'. When the tool tip 23 is brought into engagement with the cylinder it passes through positions 25', 26' and 27' analogous to positions 25, 26 and 27. In position 27* it engages one of two plates 18' having the same function as the plate 18. A spigot 10' extends from the top of the spring 12 and is of smaller diameter than the spigot 10 to allow room to manoeuvre the tool inside the cylinder. If more room is needed, the cylindrical surface may extend through 360° to allow the external surface to be used for locating the RDP. The spigot 10' is then not required. A rotary datuming touch trigger probe (RDTP), is shown in the exploded view of Figure 6, and comprises internal and external cylindrical datum surfaces 40 and 41, respectively. Three pillars 42a, 42b and 42c are used to mount the datum surfaces to a touch-trigger mounting member 43 which is located inside a collar 44 fixed to a base plate 45. The three pillars prevent build-up of swarf and coolant inside the datum surface 40. The base plate 45 is bolted to a machine table 46 and the whole arrangement of Figure 6 is such that the datum surfaces 40 and 41 are parallel to the Z-axis of the table 46. Three piezo-electric crystals 47a, 47b and 47c are mounted on the member 43 to fit tightly between this member and the collar 44. A radially compliant tab 48 allows tight contact between the piezo-electric crystals, the member 43 and the collar 44. The piezo-electric crystals are located at 120° around the cylindrical periphery of the member 43 and they are radially polarised to provide outputs when pressure is applied to either of the datum surfaces 40 and 41. Each piezo-electric crystal is connected to an amplifier which is coupled to a respective threshold circuit. The outputs of these threshold circuits- are connected to an OR circuit to provide an engagement signal when any threshold is exceeded. In operation with the boring head of Figure 1, a touch trigger probe is placed in a machine tool spindle and used to find the centre of the cylindrical datum surfaces, that is the X and Y coordinates (in the machine table) of an axis 50 of these surfaces. The boring head is placed in the spindle with the spindle axis coincident with the axis 50 and at such a distance from the surfaces 40 and 41 that the tool tip is clear of these surfaces. The tool tip is now moved radially by a U-axis drive of the boring head until it is clear of the datum surface which is to be used. For example if internal boring is to be carried out the U-axis is driven to position the tool tip at a diameter of about 1 mm less than the diameter of the datum surface 40 and vice versa for external boring when the tool tip is at a diameter of about 1 mm greater than the external cylindrical surface 41. Next the Z-axis is driven to place the tool tip alongside the relevant datum surface and the spindle is rotated to align a line joining the tool tip and the axis 50 with the X-axis. In th.s position the tool tip radius is increased for internal boring and decreased for external boring until the tool tip engages one of the datum surfaces. The engagement is sensed by the piezo-electric crystals which send a signal to the boring head computer stopping the U-axis movement and transferring the reading of a U-axis displacement sensor in the boring head to a first engagement counter in the computer. Next the radius of the tool tip is changed by about 0.5 mm to clear the tool tip from the datum surface and the machine tool spindle is rotated through 90° and the procedure for bringing the tool tip into contact with one of the datum surfaces repeated except that the reading of the U-axis displacement sensor is transferred to a second engagement counter in the computer. The procedure is Repeated with the spindle at 180° and 270° to the original position and on contact with the datum surface the U-axis displacement sensor readings are transferred to third and fourth engagement counters. Immediately after each transfer of a U-axis sensor reading to one of the engagement counters, the result of a calculation carried out by the computer and indicating the deflection of the tool tip may be subtracted from the contents of that counter to take account of the radial tool tip deflection brought about by the engagement force between the tool tip and the datum surface. However this force is usually small since position sensing is being carried out not cutting and therefore the deflection is usually insignificant. When the four engagement counters contain readings, corrected if necessary, the average of the contents of the counters UA E is calculated by the computer: Ui + U2 + U3 + U4 U AVE = 4 where U-| , U2, U3 and U4 are the contents of each of the engagement counters. Any difference in position in the X-Y plane between the centre of rotation of the tool tip and the axis 50 of the datum surfaces is taken into account by deriving UAVE- UAVE represents the radius of a circle described by an unknown point on, or associated with, the tool, since the U-axis displacement sensor does not provide the absolute position of a known point such as the tool tip. In order to determine the radius of the circle described by the tool tip, a constant offset UOFF is added to the output of the displacement sensor. This offset is given by UAVE + UOFF - Ros where RQS is the radius of the relevant cylindrical datum surface. Giving: u OFF = R DS " U AVE- Thus the diameter bored by the tool tip when subjected to cutting and centrifugal forces is as follows Dy = 2(u + UQFF) + ΔD where U is the U-axis displacement sensor reading and ΔD is the increase of tool tip swept diameter brought about by cutting and centrifugal forces and calculated by the boring head computer. An error which is likely to occur is due to the lateral misalignment of the tool tip and a line passing through the centre of rotation of the boring head and parallel to the U-axis. This error is zero at the datumed radius Rns, and progressively - increases with swept radii above and below that of RQS- It can be reduced to an acceptable amount by shimming the tool in order to minimise the lateral misalignment. Alternatively, a group of concentric cylindrical datum surfaces such as the surfaces 52, 53 and 54 in Figure 7 can be used instead of the surfaces 40 and 41. Such an arrangement not only compensates for the lateral misalignment of the tool tip but also has the added advantage of calibrating the U-axis over most of its displacement range. The surfaces of Figure 7 allow the U-axis to be datumed at upper and lower displacement positions for external boring and at an upper position for internal boring. U-axis sensor readings at the upper and lower limits allow a calculation to be carried out to determine the lateral misalignment value and the computer can then take this value into account when calculating the swept radius. In a more simple alternative method the upper and lower datumed diameters are used to calibrate the U-axis displacement sensor according to a first order linear equation so reducing the real time computing effort considerably. The cylindrical datum surfaces are manufactured from a hard material and surface hardened so as to resist any plastic deformation from the tool tip. However, in the event of any misuse of the RDTP or a malfunction of the touch trigger sensing arrangement, as described so far, the datum surfaces could be damaged. Also, the whole RDTP system or the boring head could be damaged if the boring bar is incorrectly positioned as the tool tip is driven in the Z-direction to be alongside a datum surface. Preferably therefore the RDTP has an overtravel repositioning system which produces an electrical output signal when overtravel occurs. The overtravel repositioning system allows movement along the axis of the cylindrical datum surfaces and in a plane orthogonal to this axis but only when a threshold force, set such that neither the datum surfaces nor the RDTP nor the boring head is damaged, is overcome. In one overtravel repositioning system the cylindrical datum surfaces are mounted on a member coaxial with the axis 50. Three rods project at 120° in a plane orthogonal to this member from the end which is remote from the cylindrical surfaces. Each rod is supported on a base plate by a pair of balls. The balls and the rods are electrically conducting but the base plate is not and a circuit is set up in which each pair of balls and the supporting rod form a switch which is broken when overtravel in a certain direction occurs. The switches are connected in series and when overtravel occurs an electrical signal is obtained which is supplied to the computer. x Another overtravel repositioning system is shown in Figure 8 where three overtravel repositioning units 56, 57 and 58 support the datum cylinders on a base plate 60. The axes of these units are parallel to the axis of the datum cylinders. The lines which are shaded on one side denote a common connection to the cylindrical datum surfaces and the overtravel repositioning units are such that axial movement is resiliently opposed while movement normal to the axes of the units 56, 57 and 58 is unrestricted. Three more overtravel repositioning units 61, 62 and 63 oppose movement normal to the axis of the cylindrical surfaces but allow movement in other directions. Again lines shaded on one side represent a common connection to the cylindrical datum surfaces. Each repositioning unit is constructed to act as a switch which operates when a certain amount of axial compression occurs. These switches are connected in series and give an electrical indication of overtravel . Provided the overtravel repositioning systmes are highly reproducible the electrical signals they produce may replace signals from the piezo-electric crystals 47a, 47b and 47c. Thus the cylindrical datuming surfaces can be directly mounted on the overtravel repositioning system without the use of the piezo-electric crystals and the U-axis sensor is read when an overtravel signal is given. Other forms of overtravel repositioning system may be devised and used to replace those specifically mentioned above. Each cylindrical datuming surface need not necessarily be a complete cylinder and may for example consist of three or four engagement surfaces normally at 120° or 90° separation, respectively, where each surface is part of the same cylindrical surface. Such an arrangement is shown in Figure 9 where four highly reproducible single axis touch trigger and overtravel units 65 to 68 are employed. Each unit supports a corresponding part 70 to 73, respectively, of a cylindrical datum surface indicated by the dotted lines. As before the overtravel units form switches which are connected in series so that when overtravel on any one surface part 70 to 73 occurs, a signal is given causing the U-axis displacement sensor to be read. The units 65 to 68 are mounted to a base plate 74 bolted to the machine table. Usually the tool and the cylindrical surfaces are made of electrically conducting material. If so, a continuity tester can be connected to the cylindrical surfaces and the tool, the latter by way of a machine tool spindle holding the tool, for example. Signals indicating continuity can then be used to indicate when the tool touches the cylindrical surfaces. Thus for this alternative the piezo-electric crystals are not required. Where a group of cylindrical datum surfaces is provided it is not necessary that they are concentric since the machine tool spindle can centre on each surface separately and UA E aπ be calculated for each surface. However concentric surfaces are preferable since the datuming procedure required is less cumbersome and minimises programming and machining costs. Where parts of cylindrical datuming surfaces only are provided, a minimum of two parts positioned nominally at 180° is adequate for datuming a boring head (that is determining the radius of the circle described by the tool tip of the head) so long as it is possible to determine the centre of curvature of the surfaces. If an RDTP is to be used with a horizontal boring machine then the base plate is mounted in the vertical plane and the weight of the cylindrical datum surfaces and any other movable mass which relies on an overtravel repositioning system for support is counterbalanced for correct operation. Since the datum surfaces are fixed they can be counterbalanced by means of a spring between a member which has the datum surfaces and a 'fixed support.

Claims: CLAIMS 1. A method of machining internal or external bores to a target diameter, comprising mounting a boring head in a machine tool spindle, the boring head having a boring bar with an integral tool tip and U-axis drive means, coupled to one end of the boring bar, for moving the boring bar in a direction normal to that axis of the machine tool shank about which the tool tip rotates, carrying out a boring operation using the boring head and the machine tool with the U-axis initially set to cut the target diameter, obtaining a signal representative of any deflection in the boring bar between the tool tip and the said end as the boring operation proceeds, and making adjustments to the U-axis to minimise any difference between the target diameter and the swept diameter of the tool tip, based on the deflection signal and taking into account centrifugal forces in the boring bar. 2. A method according to Claim 1 including deriving the swept diameter of the tool tip from the deflection signal taking into account the said centrifugal forces, and adjusting the U-axis to minimise any difference between the target diameter and the determined swept diameter. 3. A machine tool boring head comprising an elongated boring bar having a tool tip, a shank for mounting the boring head in the machine tool spindle, U-axis drive means, coupled to one end of the boring bar, for moving the boring bar in a direction normal to that axis of the shank about which the tool tip rotates when rotated by a machine tool, sensing means for providing a signal representative of any deflection in the boring bar between the said end and the tool tip, and means for providing a signal representative of the rotational speed of the boring bar. 4. A boring head according to Claim 3 comprising four strain gauges axially mounted on the boring bar near that end which is coupled to the U-axis drive means. 5. A boring head according to Claim 3 wherein the U-axis drive means comprises a lead screw coupled to the said one end of the boring bar, a clutch for engaging a U-axis drive motor mounted on a machine tool spindle, and belt drive means coupling the clutch to means for driving the lead screw while machining takes place. 6. A system for use in automatic boring comprising a boring head according to Claim 3 and means for determining change in swept radius of the tool tip from, at least, the deflection signal and for providing an error signal representative of the difference between the swept radius so determined and a target radius, the said means being coupled to the U-axis drive means to drive the - • <-?• boring bar in a direction which minimises the error signal. 7. A system according to Claim 6 wherein the means for determining change in swept radius of the tool tip comprises a computer coupled to receive input signals from the strain gauges, a U-axis displacement sensor for providing a signal representative of movement of the tool tip in the U-axis direction and a rotary position sensor for providing a signal indicating the speed of rotation of the tool tip. 8. A method of machining internal or external bores to a target diameter, comprising mounting a boring head in a machine tool spindle, the boring head having a boring bar with an integral tool tip and U-axis drive means, coupled to one end of the boring bar, for moving the boring bar in a direction normal to that axis of the machine tool shank about which the tool tip rotates, carrying out a boring operation using the boring head and the machine tool with the U-axis initially set to cut the target diameter, obtaining a signal representative of any deflection in the boring bar between the tool tip and the said end as the boring operation proceeds, and adjusting the U-axis, using at least the deflection signal, to minimise any difference between the target diameter and the swept diameter. 9. A machine tool boring head comprising an elongated boring bar having a tool tip, a shank for mounting the boring head in the machine tool spindle, U-axis drive means, coupled to one end of the boring bar, for moving the boring bar in a direction normal to that axis of the shank about which the tool tip rotates when rotated by a machine tool, and sensing means for providing a signal representative of any deflection in the boring bar between the said end and the tool tip. 10. A method of machining internal or external bores to a target diameter substantially as hereinbefore described. 11. A boring head substantially as hereinbefore described with reference to Figure 1 of the accompanying drawings.

Inventors: NICKOLS FRANCIS MALCOLM JOHN, NICKOLS, FRANCIS, MALCOLM, JOHN
Applicants: NICKOLS FRANCIS MALCOLM JOHN, NICKOLS, FRANCIS, MALCOLM, JOHN
Application year: 1988
Main classification: G05B19
IPC codes: B23B25, B23B39, B23B49, B23Q15, B23Q17, G01B21, G05B19