EP0903199A2 - Perfectionnements relatifs au calibrage - Google Patents

Perfectionnements relatifs au calibrage Download PDF

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Publication number
EP0903199A2
EP0903199A2 EP98307304A EP98307304A EP0903199A2 EP 0903199 A2 EP0903199 A2 EP 0903199A2 EP 98307304 A EP98307304 A EP 98307304A EP 98307304 A EP98307304 A EP 98307304A EP 0903199 A2 EP0903199 A2 EP 0903199A2
Authority
EP
European Patent Office
Prior art keywords
gauge
workpiece
region
movement
wheelhead
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.)
Granted
Application number
EP98307304A
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German (de)
English (en)
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EP0903199B1 (fr
EP0903199A3 (fr
Inventor
Michael Laycock
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Intermec Europe Ltd
Original Assignee
Unova UK Ltd
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Filing date
Publication date
Priority claimed from GBGB9720088.5A external-priority patent/GB9720088D0/en
Priority claimed from GBGB9815625.0A external-priority patent/GB9815625D0/en
Application filed by Unova UK Ltd filed Critical Unova UK Ltd
Publication of EP0903199A2 publication Critical patent/EP0903199A2/fr
Publication of EP0903199A3 publication Critical patent/EP0903199A3/fr
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Publication of EP0903199B1 publication Critical patent/EP0903199B1/fr
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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
    • B24B49/00—Measuring or gauging equipment for controlling the feed movement of the grinding tool or work; Arrangements of indicating or measuring equipment, e.g. for indicating the start of the grinding operation
    • B24B49/02—Measuring or gauging equipment for controlling the feed movement of the grinding tool or work; Arrangements of indicating or measuring equipment, e.g. for indicating the start of the grinding operation according to the instantaneous size and required size of the workpiece acted upon, the measuring or gauging being continuous or intermittent
    • B24B49/04—Measuring or gauging equipment for controlling the feed movement of the grinding tool or work; Arrangements of indicating or measuring equipment, e.g. for indicating the start of the grinding operation according to the instantaneous size and required size of the workpiece acted upon, the measuring or gauging being continuous or intermittent involving measurement of the workpiece at the place of grinding during grinding operation
    • 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
    • B24B5/00—Machines or devices designed for grinding surfaces of revolution on work, including those which also grind adjacent plane surfaces; Accessories therefor
    • B24B5/36—Single-purpose machines or devices
    • B24B5/42—Single-purpose machines or devices for grinding crankshafts or crankpins

Definitions

  • This invention concerns methods and apparatus for gauging the diameter of a workpiece as it is ground and the invention is of particular application to grinding machines incorporating CBN grinding wheels.
  • Workpiece diameter has been monitored during grinding by engaging diametrically opposite regions of the workpiece by probes during the grinding process and monitoring the distance between the probes electronically.
  • By resiliently urging the probes into contact with the workpiece so an accurate indication of the mean diameter of the workpiece is obtained and as the diameter reduces due to grinding, this is monitored and when a given diameter threshold is reached the necessary control signals are generated to adjust the grinding process accordingly.
  • the rotating workpiece can be engaged by the two fingers of a relatively fixed probe since relative to the machine frame, the workpiece remains static but for the rotational movement of its surface.
  • the axis of the cylindrical ground region itself describes a circular motion as the workpiece is rotated about its main axis.
  • Example of such workpiece regions are the crankpins of a crankshaft for an internal combustion engine. Each crankpin must be cylindrical about its own axis but itself is displaced by the throw of the crankshaft relative to the main axis about which the crankshaft rotates.
  • crankpins It is of course necessary to control the diameter of the crankpin just as accurately as the cylindrical journal bearing regions of the crankshaft and gauges have been developed for following the crankpins as they rotate about the axis of the crankshaft during the grinding operation.
  • crankpin At any point in the rotational movement of the crankpin around the main axis of the crankshaft, tangential movement of the crankpin relative to the machine frame can be expressed as two orthogonal components, one parallel to the generally horizontal motion of the wheelhead and the other perpendicular thereto.
  • the horizontal component will be zero at the two midway positions between top and bottom dead centre of the circular path described by the pin, and the vertical component of the motion will be zero at top and bottom dead centre.
  • the gauge in a process of in-process gauging whilst grinding a cylindrical part of a workpiece which is radially offset relative to the workpiece axis, such as the crankpin of a crankshaft, using a grinding machine, the gauge is power driven so as to cause the gauge to mimic in phase the crankpin motion about the crankshaft axis.
  • a linkage between an anchor point and the gauge extends over or below the workpiece to locate the gauge on the opposite side thereof from the grinding wheel, so that while gauging, the gauge is suspended from the linkage remote from the grinding wheel and is moved by the linkage into engagement with the workpiece and is positively driven through the linkage so as to minimise the rotation of the offset workpiece region engaged by the gauge, about the workpiece axis, in phase therewith.
  • the method includes the step of compensating for the weight of the gauge and linkage so that at least during gauging, the gauge is subject only to its own inertia.
  • the method comprises the steps of engaging opposite regions of the workpiece part by gauging fingers of a gauge to determine the distance between the fingers and therefore the diameter of the gauged part, moving the gauge fingers along a first path parallel to the movement of the wheelhead containing the grinding wheel, in synchronism and phase with the wheelhead movement, so that relative movement parallel to the said first path between the cylindrical part being ground and the gauge, is substantially eliminated, and further characterised by moving the gauge along a second path orthogonal to the first path and in synchronism with the movement along the first path, so that the gauge describes a circular path around the workpiece axis which is similar in radius to that of the circular path of the cylindrical part being ground and is controlled so s to be in phase with the movement of the said part as it rotates theraround
  • Both of the two orthogonal motions may be achieved by servo motor drives.
  • the drives may be controlled by information derived from the wheel feed, but preferably additional information for controlling the drives may be obtained from an encoder associated with the rotation the workpiece.
  • the gauge may be attached to a support which is mounted on or is driven by the wheelhead, so as to effect the movement of the gauge along the said first path, while a separate drive is provided for effecting movement of the gauge along the said second path.
  • the said separate drive may comprise a linear actuator drive, operating at right angles to the first path.
  • the gauge may be suspended from the end of an oscillating beam structure, pivotally mounted to a wheelhead mounted support, counterbalanced to compensate for the gauge and linkage weight, and driven by a reciprocating drive.
  • a preferred beam structure comprises of a pair of rigid struts forming part of a parallelogram which at their inboard ends are pivoted about two axes separated in a direction perpendicular to the direction of the said first motion on the wheelhead support, and at their outboard ends are joined by another rigid member so as to space apart the two outboard ends by the same distance as the spacing between the two said separated axes.
  • the movement along the said second path is effected by reciprocally pivoting the parallelogram structure so that the two parallel rigid members are lifted above and lowered below a mean position in each case by a distance which is equal to that between the main axis of the workpiece and the axis of the cylindrical part being ground. In the case of a crankpin, this equates to the so-called throw of the crankshaft.
  • the struts forming the two parallel sides of the parallelogram are generally parallel to the said first path.
  • the gauge housing is suspended from the outboard end of the parallelogram by an elongate structure pivotally joined to the outboard parallelogram strut, and extending in a downward direction therefrom to position the gauge near to the workpiece, to enable the gauge and the fingers thereof to be moved generally laterally into and out of engagement with the workpiece region to be gauged by movement of the said elongate structure.
  • the lateral movement of the gauge may be achieved by angular movement of the said elongate structure relative to the main parallelogram of struts.
  • the elongate structure may comprise a further pair of struts the lower ends of which are pivotally attached at two spaced apart points to the gauge housing, and the method further includes the step of altering the length of one of the said further pair of struts.
  • the angular movement of the gauge housing will approximate to straight line movement, which facilitates the engagement and disengagement of the gauge fingers with the workpiece region to be gauged.
  • the length of the struts forming the parallelogram of struts and the length of the two said second pair of struts is selected so that the actual movement of the gauge relative to the wheelhead approximates to a vertical straight line.
  • one of said further pair of struts is pivotally attached to a pivot displaced to one side of the outboard strut joining the outboard ends of the parallel struts forming the parallelogram of struts, and the position of the displaced pivot is selected so as to lie generally vertically above the workpiece axis.
  • the other of said further pair of struts is pivotally attached to a pivot displaced to the other side of the said outboard strut.
  • the radius of the arcuate path through which the gauge moves as it follows the cyclic displacement of the workpiece region being ground is selected to be equal to the distance between the grinding wheel axis and the axis of the cylindrical workpiece region being ground when the latter is at a mid-way position between the top and bottom dead centre of its movement, and if the centre of curvature of the said arcuate path corresponds to the axis of the grinding wheel.
  • the invention also lies in a gauge for determining the diameter of an off-axis cylindrical workpiece region during grinding (which region describes a circular path around the main axis of rotation of the workpiece during the grinding process), wherein the gauge has two spaced apart fingers for engaging the region to be gauged, and two drives are provided to positively drive the gauge so that a midpoint between the spaced apart fingers traverses the same locus as does the axis of the cylindrical region being ground, in phase therewith so that relative movement between the gauge and the workpiece region being ground is limited to non-circularity or eccentricity of the workpiece region relative to its own central axis.
  • a gauge according to the present invention is therefore distinct from devices hitherto proposed where reaction forces between the workpiece and the workpiece engaging fingers of the gauge have been relied on to introduce at least one component of motion of the gauge, to enable the workpiece engaging fingers to follow the movement of the workpiece region and remain in contact therewith during the rotation thereof.
  • a gauge operating in accordance with the present invention theoretically requires no reactive force between it and the workpiece to cause the gauge fingers to follow the movement of the workpiece.
  • a small spring or other force producing device may be provided to urge the fingers towards the workpiece region to cause the latter to be lightly gripped therebetween.
  • the spring may be dispensed with if one of the fingers is L-shaped and pivoted about the apex of the gauge is moved into contact with the workpiece region, so that the leg of the L-shaped finger makes contact with the said region causing the L-shaped finger to pivot and bring the other limb of the L into contact with the said region opposite the point engaged by the other finger of the gauge.
  • any forces acting on the gauge fingers therefore merely arise where the fingers have to move from the position which the positive drive to the gauge determines they should occupy, due to out-of-roundness or eccentricity of the workpiece region being gauged.
  • a drive rapidly retracts the grinding wheel relative to the workpiece so as to disengage the two.
  • the gauge is carried by a linkage which itself is rigidly attached to the wheelhead, (as is preferred), and the linkage extends over and beyond the workpiece so that the gauging fingers engage the workpiece from the side opposite to that engaged by the grinding wheel, any sudden reverse motion of the wheelhead could damage the workpiece, the gauging fingers, and/or the gauge, as well as other parts of the machine.
  • the gauge in a method of in-process gauging the diameter of an off-axis cylindrical workpiece region during grinding, in the manner as aforesaid, in the event of an emergency stop the gauge is either positively retracted away from the workpiece in a direction opposite to the movement of the wheelhead, or is permitted rapid and unimpeded movement relative to the wheelhead.
  • Unimpeded movement may be achieved by forming part of the gauge supporting structure from one or more collapsible, or telescopic, members or from at least one member which includes a fracture link which breaks when subjected to excessive force, thereby to enable immediate and unimpeded relative movement of the two parts now separated, and thereby unimpeded movement between the gauge and the wheelhead assembly.
  • a preferred apparatus for performing a gauging method as aforesaid comprises three pivotally joined rigid struts forming with a rigid support a jointed parallelogram, the two parallel struts being pivotally joined at their inboard ends to the said rigid support, and the latter being carried by the wheelhead of a grinding machine whereby the parallelogram of struts will advance and retract in synchronous phase with the wheelhead, and wherein the strut which is pivotally joined to the outboard ends of the two parallel struts (the outboard strut) comprises a mounting for two spaced apart pivots which are displaced from the points at which the said outboard strut is pivotally joined to the two said parallel struts, from which pivots two further struts are pivotally connected, and wherein the said two further struts are pivotally joined at their outboard ends to a gauge housing having two fingers for engaging during gauging two diametrically opposite points of a cylindrical off-axis workpiece region, and drive means is provided for reciprocally pivoting the
  • one of the two spaced apart pivots at the outboard end of the parallelogram to which one of the said two further struts is attached lies vertically above the axis of the workpiece.
  • one of the said two further struts is adjustable in length and drive means is provided to achieve the alteration of the strut length so that relative movement can be obtained between the gauge and the non-adjustable strut therefore the parallelogram of struts.
  • the gauge is relatively fixed in relation to the other strut, adjustment of the length of the said one strut will produce arcuate movement of the gauge relative to the parallelogram of struts.
  • the gauge can be swung in an arcuate path and where the gauge is adjacent the workpiece this movement enables spaced apart fingers protruding from the gauge to straddle the workpiece region which is to be gauged to enable the fingers to lightly grip diametrically opposite regions of the said workpiece region.
  • the support for the parallelogram of struts may be separate from the wheelhead and movement of the said parallelogram of struts in sympathy with the wheelhead is achieved by a separate servo drive responsive to control signals derived from the wheelfeed signals and/or from signals from an encoder associated with the headstock.
  • the gauge includes two parallel spaced apart fingers for lightly engaging diametrically opposite regions of the workpiece region, and a further workpiece engaging element which is located approximately mid-way between the said two fingers and is displaced relative to a line joining the said two fingers by a distance commensurate with the radius of the workpiece region which is to be gauged, so that the said element will engage a point on the surface of the workpiece region which is diametrically opposite the point of contact with the grinding wheel.
  • the workpiece engaging element may be a separate member independently movable relative to the housing and therefore to the two fingers.
  • the element may comprise a right angled extension to one of the said two fingers.
  • this is pivotable about the apex of the L and the other finger is mounted so that its workpiece region engaging portion diametrically opposite one of the two workpiece region engaging portions of the composite finger, and is movable relative to the said composite finger in such a way as to accommodate diameter variations of the cylindrical workpiece region.
  • Variation in diameter is determined by noting movement of the second finger relative to the composite finger during grinding, inward relative movement of the said finger corresponding to a reduction in diameter.
  • a light spring may be provided so as to introduce positive engagement between the fingers and the workpiece region being gauged, so that they lightly grip the workpiece region therebetween.
  • Electrical signals corresponding to the mean diameter determined upon initial engagement between the fingers and the workpiece region, and subsequently to changes in diameter during grinding, may be derived from one or more transducers associated with the fingers.
  • the signals may be transmitted as feedback signals to a computer adapted to control the overall operation of the machine.
  • the pivot for the non-extensible strut joining the outboard strut of the parallelogram of struts to the gauge housing defines a pivot axis which is parallel to the axis of the off-axis cylindrical region of the workpiece being ground, and remains generally vertically thereabove as a consequence of its movement with the wheelhead.
  • the movement of the gauge and associated fingers must be capable of accommodating the different positions of the wheelhead and different distances through which it must move, to enable workpiece region engagement with the reducing wheel diameter due to wear.
  • the pivot on the said outboard strut of the parallelogram from which the non-extensible gauge supporting strut is pivoted is itself positioned generally above the axis of rotation of the workpiece region being ground, the movement of the gauge describes an arcuate path centered about the said outboard strut pivot axis.
  • the extensible strut may comprise at least in part a pneumatic cylinder, movement of the piston therein producing the variation in overall length of the strut, and control means is provided for supplying air to the cylinder to extend or retract the cylinder as required.
  • Alteration of the length of the strut pivotably moves the gauge housing about the end of the non-extensible strut and therefore relative to the parallelogram of rigid struts, and in turn relative to the workpiece region to be gauged, to facilitate the engagement and disengagement of the latter by the gauge fingers.
  • a single acting cylinder with spring return may be employed, the latter acting to shorten the length of the strut if air pressure is removed. If a strong spring is employed, this feature may be used to retract the gauge in an emergency stop scenario.
  • air pressure may be removed and the cylinder fully vented as soon as the fingers are in contact with the workpiece region.
  • Emergency retract may be required before the cylinder has been fully vented (for example during the approach of the probe to the workpiece), and to this end a pressure relief valve is preferably provided in the airline feeding the cylinder to extend the strut length, such that if an emergency stop occurs during the said approach, any reaction force due to the sudden engagement of the fingers with the workpiece will be transmitted back to the cylinder to generate a back pressure in the airline which overcomes the relief valve and enables the cylinder to vent, thereby to accommodate rapid reverse movement of the gauge due to retraction of the wheelhead.
  • torque generating means is provided so that a turning movement is produced about the pivot of at least one of the parallel struts of the said parallelogram, the direction and magnitude of which is such as to compensate for the opposite turning movement about that pivot created by the mass of the gauge linkage.
  • one of the two parallel struts of the parallelogram extends beyond the pivot point where it is attached to the wheelhead mounted support, and the turning moment of the extended section of the strut is adapted to generally counterbalance the weight of the gauge and supporting structure, so that a very small force is needed to reciprocally pivot the array of struts and the gauge (and/or to move the gauge relative to the struts for engagement and disengagement of the workpiece region), and no additional force is required to counterbalance the gravitational forces acting about the pivot occasioned by the weight of the gauge and the supporting structure.
  • the counterbalancing may be achieved by the weight of the extended section of the said strut.
  • a spring may be employed acting about the pivot.
  • a servo drive acting at the pivot point or any combination of spring/weight/drive may be employed.
  • the reciprocal pivoting movement imparted to the gauge support structure is preferably simple harmonic motion with frequency and amplitude control.
  • a positive reciprocal pivoting of the parallelogram of struts is most simply obtained by means of a reciprocating servo drive acting about the axis of an appropriate pivot point.
  • the preferred pivot point is one of the pivots on the said support.
  • the drive means serves to reciprocally pivot the rigid strut associated therewith about the pivot axis, and by virtue of the pivoted parallelogram structure, this reciprocal motion is transmitted to the gauge.
  • the gauge mounted outboard from the parallelogram of struts will normally follow the same locus as the axis of the off-axis cylindrical region of the workpiece being ground (as it rotates about the main axis of the workpiece).
  • the gauge will describe the same circular movement around the crankshaft axis as does the crankpin it is gauging, thereby removing all need for the crankpin to drive the gauge.
  • the reciprocating servo mechanism is controlled by signals derived from a computer
  • the latter is preferably programmable to adjust the frequency and amplitude and phase of the reciprocal movement, to compensate for any variation in the speed of rotation of the workpiece region during rotation and/or to cater for different eccentricities.
  • the gauging process does not rely on maintaining contact between the workpiece and the gauge to transfer movement of the workpiece region to the gauge to ensure that the latter follows its movement. Instead it is only necessary for the gauge to handle any movement of the gauging fingers relative to the gauge housing, due to variation in diameter and/or circularity and/or eccentricity of the workpiece region which is being gauged. There is likewise no requirement to provide a mechanism for ensuring contact between gauge fingers and workpiece surface during gauging except insofar as to ensure that contact is maintained between the diametrically opposite regions of the workpiece region.
  • an algorithm or look-up table or other software mechanism may be provided for determining the primary motion of the gauge support structure, and additional software may be provided for adjusting parameters of the algorithm, or values in the look-up table, or the control signals derived therefrom, so as to permit fine tuning of the motion as required.
  • gauge support structure for example the parallelogram of struts
  • a further such drive may still be provided between the wheelhead and the said support for the gauge support structure, which itself is also under computer control, to allow for fine tuning of the advance and retract movement of the probe in the direction of the wheelhead movement.
  • Such additional movement as provided by the intermediate drive may for example assist in engagement and dis-engagement of the gauge fingers with the workpiece region.
  • an emergency retract condition may generate a control signal for operating this drive to accelerate the gauge support structure so as to move the gauge away from the workpiece opposite to the direction of movement of the wheelhead, so that the probe is positively retracted in an opposite sense to any emergency retract movement of the wheelhead.
  • Such a drive (such as a servo drive) is provided between the support structure and the wheelhead, it may also be activated during an emergency retract so as to further assist in moving the gauge clear of the workpiece.
  • the headstock rotates the workpiece and an encoder is normally associated with the headstock which allows instantaneous rotational positional information of the workpiece to be obtained and therefore additionally information about the rotational position of the region of the workpiece which is being ground where this is off-axis.
  • Information from the headstock drive, and in particular the encoder therefor, allows complete synchronisation of the machine and the region being ground, and in the same way as accurate positioning of the wheelhead can be achieved using appropriate servo control signals and servo motors, so a servo drive associated with the gauge support structure (such as a parallelogram of struts as described herein), and acting thereon to reciprocally move the struts so that in combination with the advance and retract movement of the wheelhead the gauge is caused to describe a circular movement, the servo drive can be synchronised with the rotation of the workpiece using the encoder output signals from the headstock.
  • the gauge can be maintained in strict phase with the rotational movement of the headstock, and therefore the workpiece, so that any variation in instantaneous speed of rotation around the circular path can be detected and transmitted into the movement of the gauge so as to remove any unwanted force between the workpiece and the gauging fingers.
  • a gauge constructed in accordance with the invention becomes quite distinct from any previous gauge since the gauge fingers can be driven in perfect synchronism and phase with the rotating off-axis workpiece region which is to be gauged and no force needs to act between the gauging fingers and the gauged surface to cause the gauge to follow the movement of the workpiece region.
  • the gauge housing is preferably attached to the lower end of the said strut, through a lost motion connection.
  • the gauge housing preferably includes a rigid extension carrying an adjustable stop which is engageable with an external surface of the strut to which the gauge housing is pivotally connected, and the stop is adjustable to prevent the housing from pivoting beyond a certain position relative to the strut. Freedom to accommodate eccentricity and out of roundness is achieved by ensuring that the stop disengages from the strut to create a clearance gap between it and the strut when the gauge has been advanced and the fingers have fully engaged the workpiece region of the gauging.
  • the gap between the stop and the strut is selected so as to be greater than the maximum relative movement expected between the gauge housing and the strut during gauging.
  • the latter may be operated so as to generate the gap previously referred to, by adjusting the length of the strut containing or comprised of the cylinder, (typically by shortening the strut length) after engagement of the workpiece region by the gauge fingers, so as to generate said gap. This permits a free floating movement of the gauge and the fingers relative to the supporting strut.
  • a pressure relief valve may be provided such that any sudden increase in pressure will be vented immediately through the relief valve.
  • An alternative arrangement for achieving the rotatable movement of the gauge comprises a pair of rotating cranks mounted for rotation about two vertically spaced apart axes, parallel to the main axis of the workpiece, and joined by a rigid link which extends downwardly below the lower of the two cranks where it is secured to a gauge housing having fingers for engaging diametrically opposite regions around an off-axis cylindrical workpiece region which is rotating about the main axis of the workpiece during grinding, wherein the radius of the cranks and the speed of rotation is selected so as to correspond to the radius of the circular motion of the said off-axis cylindrical region, and to the rotational speed of the said region around the main axis of the workpiece, so that the gauge describes the same circular path in phase with the movement of the said region around the workpiece axis.
  • cranks do not therefore need to be mounted to the wheelhead, but can be mounted on a carriage mounted to the machine structure and driven or pivotable so as to permit engagement and disengagement of the fingers with the workpiece part.
  • the wheelhead must be indexed axially relative to the workpiece to allow the wheel to engage different cylindrical regions therealong such as crankpins along a crankshaft.
  • the gauging device must also follow the axial movement of the wheelhead so that it is always aligned with the workpiece region which is to be ground.
  • An advantage of an arrangement in which the gauge is supported by a structure which is not attached to the wheelhead, is that during an emergency stop, no emergency withdrawal of the gauge is required and it can stay in contact with the rotating workpiece if desired.
  • a wheelhead is shown at 10 and the unworn and worn perimeters of a CBN grinding wheel are denoted by 12 and 14 respectively.
  • crankpin to be ground by the grinding wheel 16 are denoted by 18 and 20 respectively. These correspond to the unworn and worn conditions of the CBN wheel and in accordance with the invention a probe 22 having an upper composite finger 24 and lower movable finger 26 is shown engaging the pin in the position 18 of the pin at the beginning of the life of the wheel.
  • Pads 28 and 30 on the composite finger 24 engage two regions of the pin separated by a right angle, and a pad 32 on the finger 26 engages the pin diametrically opposite the region engaged by pad 28.
  • the probe 22 includes one or more transducers (not shown) for determining the spacing between the subsequent movement of the fingers, and therefore the diameter, and changes in the diameter, of the pin being ground.
  • the probe is itself pivotally attached at 34 to the lower end of a rigid link 36 the upper end of which is pivotally attached at 38 to a closure plate 40.
  • a second separate pivot point 42 on the plate 40 provides the upper mounting point for a pneumatic piston and cylinder 44 the outboard end of the piston rod being pivotally connected at 46, at the lower end of the rigid strut 36.
  • the plate 40 provides a closure to a parallelogram of struts the longer sides of which are made up of the two struts 48 and 50, which are pivotally attached to the plate 40 at 52 and 54 respectively. At their opposite ends they are pivotally attached to an upright rigid support member 56 at 58 and 60 respectively.
  • the support 56 is mounted on the wheelhead 10 and moves therewith.
  • a servo drive 64 reciprocally pivots the rigid strut 50 about the pivot axis 60 so as to reciprocally raise and lower the probe 22 and since the motion is arcuate, the mid-position between the two pads 28 and 32 (denoted by reference numeral 66) will in fact describe an arcuate path as identified by 68.
  • the effective centre of the arcuate path 68 the same as the centre of rotation of the wheel 16 (denoted by reference numeral 70), so the arcuate path described by the centre of the rotating workpiece region being ground as it maintains contact with the wheel 16, as the latter advances and retracts, will correspond substantially with the arcuate path 68 described by the mid-position of the pads 28 and 32.
  • a pressure relief valve 72 is provided to vent the airline supplying the pneumatic cylinder 44 in an emergency.
  • the cylinder 44 may be vented at both ends as soon as the probe pads 28, 30 and 32 are in contact with the workpiece region to be ground, so that in the event of an emergency retract, the cylinder 44 presents no resistance to the rapid inward movement of the piston (not shown) thereby permitting rapid relative movement between the wheelhead and the probe, as the wheel is retracted.
  • a counterbalance weight 74 is carried at the end of an extension 62 of the arm 48.
  • Figures 2 and 3 show how the support 56 can be mounted laterally of a grinding wheel housing 76. Similar reference numerals are employed in Figures 2 and 3 to denote the same parts as shown in Figure 1 and by comparing Figures 1 and 3 it will be seen that the two arms 48 and 50 are bent approximately midway along their length to cause the outboard ends of 48 and 50 to finish up generally opposite the grinding wheel housing 76, but displaced by a suitable distance from the wheel 16 to allow for the gauge housing 22 and its probes 24, 26 to be mounted thereon from the arms 36, 44, beyond the region occupied by the crankshaft workpiece whose pins are to be ground and gauged.
  • a lost motion connection is provided between the arm 36 and the housing 22, which pivots relative to 36 at 34.
  • a finger 82 extends rearwardly and upwardly from the housing 22 and includes a locking nut and threaded adjuster screw 84 which can be rotated so as to alter a gap between the end of the screw and the arm 36.
  • the gauge assembly then "floats" if the cylinder 44 is depressurised. The weight of the housing 22 will introduce a turning movement about 34 when the feelers are disengaged from the pin, but clockwise pivoting of the housing 22 about 34 is restricted by engagement of the screw 84 with the arm 36.
  • Re-engagement of another pin by the gauge causes the housing 22 to rotate in a counter clockwise sense as the two feelers 28, 32 grip the pin, causing the screw 84 to move away from the arm 36 again, to once again produce the operating gap.
  • the two arms 48, 50 are replaced by a triangular assembly 86 mounted on the wheelhead adjacent the wheel housing and carrying a vertical slideway on which a linear motion drive 90 is carried.
  • the latter is programmable under computer control to slide up and down the slideway 88 as required to raise and lower a plate 92 carried by the drive unit.
  • the drive 90 may be pneumatic of electromagnetic.
  • gauge housing 22' is positioned to the lower end of an arm 36' at 34' and the upper end of arm 36' is pivoted to the plate 90 at 38.
  • a pneumatic piston and cylinder 44' is pivoted at 42' and 46'.
  • a similar stop 84 and arm 82 is provided to provide lost motion between arm 36' and housing 22' as described in relation to Figure 1.
  • the drive 90 is programmed so as to move in synchronism with the wheel feed and crankshaft rotation, so that the gauge follows the circular path of the pin being ground.
  • Figure 5 shows how two rotating cranks 94, 96 can transmit a simple harmonic motion via rigid connecting rod 98 to a gauge housing 22" pivotally attached at 100 to the lower end of the rod 98, with lost motion provided by an arm 82" and screw 84", similar to the similar items described with reference to Figure 1 and Figure 4.
  • a computer (not shown) suitably programmed, provides the control signals.
  • cranks are carried on a slide 102, itself slidable relative to a support 104 attached to the machine structure (as opposed to the wheelhead) and also be capable of horizontal or rotational displacement relative to the machine structure for engaging and disengaging the gauge fingers 24", 26" from the workpiece W.
  • Horizontal movement of the slide 102 is also under computer control, and is provided to allow for initial engagement and final disengagement of the fingers 24", 26" and the workpiece W.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Grinding Of Cylindrical And Plane Surfaces (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
  • A Measuring Device Byusing Mechanical Method (AREA)
EP19980307304 1997-09-23 1998-09-09 Perfectionnements relatifs au calibrage Expired - Lifetime EP0903199B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GB9720088 1997-09-23
GBGB9720088.5A GB9720088D0 (en) 1997-09-23 1997-09-23 Improvements in and relating to workpiece gauging
GBGB9815625.0A GB9815625D0 (en) 1998-07-18 1998-07-18 Improvements in and relating to workpiece gauging
GB9815625 1998-07-18

Publications (3)

Publication Number Publication Date
EP0903199A2 true EP0903199A2 (fr) 1999-03-24
EP0903199A3 EP0903199A3 (fr) 1999-07-14
EP0903199B1 EP0903199B1 (fr) 2002-11-27

Family

ID=26312292

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19980307304 Expired - Lifetime EP0903199B1 (fr) 1997-09-23 1998-09-09 Perfectionnements relatifs au calibrage

Country Status (4)

Country Link
EP (1) EP0903199B1 (fr)
DE (1) DE69809667T2 (fr)
ES (1) ES2189094T3 (fr)
GB (1) GB2329472B (fr)

Cited By (17)

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EP1118833A2 (fr) * 2000-01-18 2001-07-25 Marposs Societa' Per Azioni Appareil pour vérifier les dimensions de pièces cylindriques
WO2001070456A2 (fr) * 2000-03-20 2001-09-27 Control Gaging, Inc. Systeme automatique de positionnement pour tete de calibrage
EP1197294A1 (fr) * 2000-10-11 2002-04-17 Douglas Curtis Limited Machine à rectifier sans centre avec dispositif de mesure
WO2002070195A1 (fr) * 2001-03-02 2002-09-12 Marposs Società per Azioni Appareil conçu pour verifier les caracteristiques dimensionnelles et geometriques de broches
WO2003106108A1 (fr) * 2002-06-12 2003-12-24 Marposs Società per Azioni Dispositif permettant de verifier les caracteristiques geometriques et dimensionnelles de tiges
US7607239B2 (en) 1995-10-03 2009-10-27 Marposs, Societá per Azioni Apparatus for checking diametral dimensions of cylindrical parts rotating with an orbital motion
WO2011013710A1 (fr) * 2009-07-28 2011-02-03 コマツＮｔｃ 株式会社 Rectifieuse et dispositif de mesure
GB2475391A (en) * 2009-07-28 2011-05-18 Komatsu Ntc Ltd Grinding machine and measurement device
WO2012136992A1 (fr) * 2011-04-08 2012-10-11 Cinetic Landis Limited Ensemble support destiné à être utilisé avec une machine-outil et procédé de commande de cet ensemble
US8336224B2 (en) 2009-09-22 2012-12-25 Hommel-Etamic Gmbh Measuring device
US8429829B2 (en) 2010-03-26 2013-04-30 Hommel-Etamic Gmbh Measuring device
US8725446B2 (en) 2009-07-08 2014-05-13 Hommel-Etamic Gmbh Method for determining the shape of a workpiece
US9393663B2 (en) 2010-08-23 2016-07-19 Hommel-Etamic Gmbh Measuring device
US9562756B2 (en) 2012-09-20 2017-02-07 Jenoptik Industrial Metrology Germany Gmbh Measuring device with calibration
JP2019063962A (ja) * 2017-10-04 2019-04-25 株式会社ジェイテクト 工作機械
CN110274562A (zh) * 2019-08-06 2019-09-24 安徽理工大学 一种维护简便的刚度可调型十字梁微纳测头
CN110411389A (zh) * 2019-08-12 2019-11-05 重庆市吉盛刀具有限公司 飞轮同轴度和端面跳动检测工装

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CN100368761C (zh) * 2006-03-30 2008-02-13 上海大学 跟踪式圆度和直径在线测量机构
DE102011115254A1 (de) 2011-09-27 2013-03-28 Fritz Studer Ag Werkzeugmaschine und Verfahren zur Vermessung eines Werkstücks
CN102513934A (zh) * 2011-12-26 2012-06-27 广州市敏嘉制造技术有限公司 随动磨削检测装置

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US5542188A (en) * 1994-06-09 1996-08-06 Zeiss Messgeratebau GmbH Measuring apparatus for checking the dimensions of cylindrical workpieces
WO1997012724A1 (fr) * 1995-10-03 1997-04-10 Marposs Societa' Per Azioni Appareil destine a verifier le diametre de tourillons animes d'un mouvement orbital
WO1997013614A1 (fr) * 1995-10-06 1997-04-17 Sagem S.A. Dispositif de mesure ou de controle de l'usinage d'une piece cylindrique a mouvement orbital

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GB9509294D0 (en) * 1995-05-06 1995-06-28 Western Atlas Uk Ltd Improvements relating to guaging the diameter of cylindrical workpiece sections
DE19616353A1 (de) * 1996-04-24 1997-10-30 Schaudt Maschinenbau Gmbh Verfahren und Vorrichtung zum Messen des Durchmessers exzentrisch umlaufender Werkstücke

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DE4419656A1 (de) * 1994-06-06 1996-01-11 Naxos Union Schleifmittel Einrichtung zur Durchmesser- und/oder Rundheitsmessung beim exzentrischen Rundschleifen
US5542188A (en) * 1994-06-09 1996-08-06 Zeiss Messgeratebau GmbH Measuring apparatus for checking the dimensions of cylindrical workpieces
WO1997012724A1 (fr) * 1995-10-03 1997-04-10 Marposs Societa' Per Azioni Appareil destine a verifier le diametre de tourillons animes d'un mouvement orbital
WO1997013614A1 (fr) * 1995-10-06 1997-04-17 Sagem S.A. Dispositif de mesure ou de controle de l'usinage d'une piece cylindrique a mouvement orbital

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8667700B2 (en) 1995-10-03 2014-03-11 Marposs Societa' Per Azioni Method for checking the diameter of a cylindrical part in orbital motion
US7607239B2 (en) 1995-10-03 2009-10-27 Marposs, Societá per Azioni Apparatus for checking diametral dimensions of cylindrical parts rotating with an orbital motion
US7954253B2 (en) 1995-10-03 2011-06-07 Marposs Societa' Per Azioni Apparatus for checking diametral dimensions of a rotating cylindrical part during a grinding thereof
US8286361B2 (en) 1995-10-03 2012-10-16 Marposs Societa' Per Azioni Apparatus for checking diametral dimensions of a cylindrical part in orbital motion in a numerical control grinding machine
US6848190B2 (en) 2000-01-18 2005-02-01 Marposs Societa' Per Azioni Apparatus for the in-process dimensional checking of orbitally rotating crankpins
EP1118833A3 (fr) * 2000-01-18 2003-04-16 Marposs Societa' Per Azioni Appareil pour vérifier les dimensions de pièces cylindriques
US6643943B2 (en) 2000-01-18 2003-11-11 Marposs Societa' Per Azioni Apparatus for the in-process dimensional checking of orbitally rotating crankpins
US7690127B2 (en) 2000-01-18 2010-04-06 Marposs, S.P.A. Apparatus for the dimensional checking of an orbitally rotating crankpin of a crankshaft
EP1118833A2 (fr) * 2000-01-18 2001-07-25 Marposs Societa' Per Azioni Appareil pour vérifier les dimensions de pièces cylindriques
US7024785B2 (en) 2000-01-18 2006-04-11 Marposs Societa' Per Azioni Method for the in-process dimensional checking of orbitally rotating crankpins
US7325324B2 (en) 2000-01-18 2008-02-05 Marposs Societa' Per Azioni Method for the in-process dimensional checking of orbitally rotating crankpins
US7464482B2 (en) 2000-01-18 2008-12-16 Marposs, S.P.A. Apparatus for the dimensional checking of orbitally rotating pins
EP2028437A1 (fr) * 2000-01-18 2009-02-25 Marposs Societa' Per Azioni Appareil et méthode pour vérifier les dimensions de pièces cylindriques
WO2001070456A3 (fr) * 2000-03-20 2001-12-20 Control Gaging Inc Systeme automatique de positionnement pour tete de calibrage
WO2001070456A2 (fr) * 2000-03-20 2001-09-27 Control Gaging, Inc. Systeme automatique de positionnement pour tete de calibrage
EP1197294A1 (fr) * 2000-10-11 2002-04-17 Douglas Curtis Limited Machine à rectifier sans centre avec dispositif de mesure
US6952884B2 (en) 2001-03-02 2005-10-11 Marposs Societa' Per Azioni Apparatus for checking dimensional and geometrical features of pins
WO2002070195A1 (fr) * 2001-03-02 2002-09-12 Marposs Società per Azioni Appareil conçu pour verifier les caracteristiques dimensionnelles et geometriques de broches
WO2003106108A1 (fr) * 2002-06-12 2003-12-24 Marposs Società per Azioni Dispositif permettant de verifier les caracteristiques geometriques et dimensionnelles de tiges
US7020974B2 (en) 2002-06-12 2006-04-04 Marposs Societa′ per Azioni Apparatus for checking the dimensional and geometric features of pins
US8725446B2 (en) 2009-07-08 2014-05-13 Hommel-Etamic Gmbh Method for determining the shape of a workpiece
GB2475391A (en) * 2009-07-28 2011-05-18 Komatsu Ntc Ltd Grinding machine and measurement device
JP5064571B2 (ja) * 2009-07-28 2012-10-31 コマツＮｔｃ株式会社 研削盤及び計測装置
GB2475391B (en) * 2009-07-28 2013-02-27 Komatsu Ntc Ltd Grinding machine and measurement device
US8678879B2 (en) 2009-07-28 2014-03-25 Komatsu Ntc Ltd. Grinding machine and measuring apparatus
WO2011013710A1 (fr) * 2009-07-28 2011-02-03 コマツＮｔｃ 株式会社 Rectifieuse et dispositif de mesure
US8336224B2 (en) 2009-09-22 2012-12-25 Hommel-Etamic Gmbh Measuring device
US8429829B2 (en) 2010-03-26 2013-04-30 Hommel-Etamic Gmbh Measuring device
US9393663B2 (en) 2010-08-23 2016-07-19 Hommel-Etamic Gmbh Measuring device
US20140004774A1 (en) * 2011-04-08 2014-01-02 Cinetic Landis Limited Support Assembly For Use With A Machine Tool And Methods Of Operation Thereof
WO2012136992A1 (fr) * 2011-04-08 2012-10-11 Cinetic Landis Limited Ensemble support destiné à être utilisé avec une machine-outil et procédé de commande de cet ensemble
US9562756B2 (en) 2012-09-20 2017-02-07 Jenoptik Industrial Metrology Germany Gmbh Measuring device with calibration
JP2019063962A (ja) * 2017-10-04 2019-04-25 株式会社ジェイテクト 工作機械
JP7000785B2 (ja) 2017-10-04 2022-01-19 株式会社ジェイテクト 工作機械
CN110274562A (zh) * 2019-08-06 2019-09-24 安徽理工大学 一种维护简便的刚度可调型十字梁微纳测头
CN110411389A (zh) * 2019-08-12 2019-11-05 重庆市吉盛刀具有限公司 飞轮同轴度和端面跳动检测工装

Also Published As

Publication number Publication date
DE69809667T2 (de) 2003-04-24
GB9819538D0 (en) 1998-10-28
ES2189094T3 (es) 2003-07-01
GB2329472A (en) 1999-03-24
EP0903199B1 (fr) 2002-11-27
EP0903199A3 (fr) 1999-07-14
DE69809667D1 (de) 2003-01-09
GB2329472B (en) 2002-03-27

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