IE60355B1 - Gemstone polishing apparatus - Google Patents

Abstract

In order to centre the residual imbalance of a scaife (5), the scaife (5) is carried on an air bearing (6) which is axially stiff but allows radial float, and is driven by a motor (2) which is carried on silent blocks (3) which are axially stiff but allow radial float of the motor (2). The motor (2) is driven at a speed above the first radial critical frequency of the system formed by the motor (2), motor shaft (4) and scaife (5) and its mounting.

Description

The present invention relates to a genstone polishing apparatus comprising a scaife, a supporting structure for the scaife, a bearing for the scsife, and a drive for the scaife. Further, the invention relates to a method of polishing a gemstxr®.

A gaisixsne polishing apparatus in ecoocdsrce with the preamble of claim 1 and, respectively, a netted of polishing a gssietooe according to the preamble of claim 17 is known, far example, from 3E-A-4G0 215 .

A scaife is a wheel which is used te polish gemstones, 1Q e.g. polishing facets on a brilliant-cut diamond. The scaife runs at a high speed, e.g. up to 6000 rpm (3000 rpm for standard ecaifes), normally about a vertical axis, and a flat face of the scaife is used for the polishing, usually with the application of an abrasive oil to the face. Normally, the scaife has a diameter of e.g. 150 to 350 s and a thickness of 10 to 20 mm and is made of soft steel or cast iron, so that it is heavy, for example· weighing 10 to 15 kg. in the art, though not in this specification, the term scaife” is also used to include the whole item of equipment or apparatus. The supporting structure is normally a flat table. The gemstones can be applied to the scaife in. hand-held dops, but are. normally mounted on polishing machines, referred to as tangs, which held the stones in the correct, orientation, and more than one tang can be used at the same time on the same scaife.

To obtain a very high quality polished diamond surface, any vibration of the scaife and table must be avoided. This is a severe problem for direct-driven scaifes where the. drive is a motor generally coaxial with the scaife, as motor-induced vibrations are transmitted through the table and the scaife. This problem can be reduced by special motor drives, or fay using a special motor and bearing design, or fay using a normal motor with a radial-axial air bearing combination for the scaife.

Such solutions are quite expensive, for example ten to twenty times the cost of a standard drive motor, and they cannot reduce the residual inbalance remaining after assembling the balanced scaife.

The Invention The present invention provides gemstone polishing apparatus as set forth in Claim 1 and a, method as set forth in claims 17. The remaining Claims set forth optional features of the invention.

The system is run over-critically, i.e. between nodes of the critical frequency, so that the scaife is self-balancing - although the scaife (and the motor) should he separately balanced, the radial float of the scaif© centres the residual imbalance.

The technique of balancing by operating at over-critical t speed has been, used in the past, it is believed is turbines, in centrifugal separators and domestic spin driers,.

In polishing, axial position stability is important, the necessary axial stiffness must be introduced, for instance using the rear face or backplane of the scaife as as air bearing ssrfacela a first approximation, the first radial critical frequency of the scaife is gives, by f = 2Π yfe/in,, where k is the radial stiffness and Si is the mass of the / system. The running frequency must be higher than the first radial critical frequency, but the amount depends upon the desired running accuracy and the damping in the system. Higher damping requires a larger difference between the running frequency and the first radial critical frequency. As to achieve perfect 2o auto-centering, the unbalance vector has to be opposite to fhe displacement vector, a irSO* shift or phase angle. For low damping, the magnitude of unbalance is very high when going through the critical frequency, but above critical frequencies the magnitude s©on becomes very small, with a phase angle very close to 160°, High damping, however far above critical frequency, maintains a residual macnitude, while the phase angle goes J gradually towards 180”, The running speed can he calculated by predetermining a minimum phase shift.

Hence a system with very low damping will result in a running speed about 20 to 30¾ above the critical frequency, while high damping systems will result in a running speed of 5 to 10 times the critical frequency. xo The advantage of using damping is avoiding a large unsafe unbalance magnitude when running through the critical frequency. The disadvantage is a larger residual unbalance and a weaker spring system. Also, the higher the applied drag force due to the polishing I5 actios of the stone, the greater the difference required between the frequencies as the grinding force may affect the position of the axis of rotation.

The radial float may be free, i.e. not against any elastic force, ia ideal conditions, but in -general there will be some radial elastic restraint or stiffness (see the equation above for the first radial critical frequency) ,.

Te minimise the effect of vibration modes due to an elastic drive system or an elastic mount of the drive sctor, it is advisable to use a light-weight sotor and to have the centre ofi gravity of the scaife, motor and motor shaft approximately on the plane of support of the axial scaife bearing - this takes advantage of the low power needed to drive the scaife (less than. 1 kw) and t the heavy weight of the seaife.

Aa axial bearing pre-load can be applied e.g. by direct magnetic action on the scaife or air pressure calls * and/or by the deadweight df the motor, and/or pre-loading an air bearing by use of the motor mounting θ means.

The motor drive shaft may be rigidly fixed to the scaife or there may be a universal or flexible coupling, i.e. a flexible or swivel coupling where rotary motion is permitted between the -motor drive shaft aad the scaife t about transverse axes, os eves a coupling which permits radial float. Such a universal, flexible or floating coupling must be able to transmit torque, and must provide (if necessary in association with other means) a stiffness corresponding to as over-critical drive, and is some eases, depending upon the pre-load system, must be capable of transmitting preload to the axial scaife i> bearing. i.

In general, whether using a universal, flexible or floating coupling or another arrangement, there may be means for preventing substantial radial float of th© scaife, at will. Such means make it possible to autobalance the system at will by running the scaife over-critical without using the means; by actuating the means, the scaife can be run under-critically but balanced and for instance can bear high tangential loads such as. may occur during multi-tang polishing. An advantage of such ao arrangement is that during start-up, one does sot have to go through the critical xo speed- A disadvantage is that the motor alignment must be sore accurate because when the radial float is prevented, misalignment cannot be taken up,, resulting in excitation forces and hence increased vibration.

Various means for preventing radial float at will, are 15 disclosed below. An alternative, at least in theory, is to use a fluid (e.g. air) racial bearing whose radial stiffness can be changed by changing the fluid pressure.

Preferred Embodiments The invention will be further described, by way ef example, with reference to the accompanying drawings, in which the Figures illustrate four different embodiments of the invention in side view, partly in axial section7 Figure 1 Figure 1 shows a gemstone polishing apparatus having a supporting structure including a table 1 carrying a drive motor 2 (such as a high quality AC motor with limited mechanical and magnetic Imbalance) by way of flexible couplings in the form of blocks. 3. which are axially stiff but radially weak. The motor shaft 4 is rigidly fixed to a scaife 5. In order to provide a bearing which is axially stiff but allows radial float of the scaife, the scaife has as axial air bearing one past of which is the rear or bottom face of the scaife S and the other part of which is indicated at 6. Axial pre-load is provided by the deadweight of the motor 2. shaft 31 and scaife S„, but if desired, further axial pre-load can be provided by the ·' blocks 3 or by f magnets 7 exerting direct magnetic action on the scaife (which will be ferromagnetic), la order to limit the radial float cf the scaife 5, there is an anti-friction bearing S around the shaft «. In the case of a soft steel or cast iron scaife 5 having a diameter of 3OO-3SO mm and a thickness of 10-20 bb, a radial gap can be provided between the bearing 8 and the shaft 4 (when the shaft Is central) of about 0.2 to 0.3 mm, for example» i.e. at least the sum of the eccentricities of the scaife S and of the shaft 4.

Though the air bearing is shown as extending to th© outer periphery of the scaife 5« it can for instance j have an outer diameter of 110-235 sub. The air bearing should he effective enough to limit axial movement of the scaife 5 to less than * 1 sicroc» One of the advantages of the use· of the axial air bearing underneath th© scaife S is the high stiffness and the fact that bearing errors of the drive have negligible effect on the vertical vibration of the scaife, and hence one can use a traditional, cheap motor drive. The vertical gevesent of the polishing surface of the scaife is nearly completely determined by the flatness of the lower side of the scaife (and if a multiped air seariac is used, that error is averaged out to about one third of its actual value) and the aos-parallelism of the scaife 5, which can be kept very low. Hence the bearing os the back of the scaife S provides good vertical running accuracy» The motor 2 is of relatively light weight whereas the scaife £ is heavy® and the centre cf gravity of the rotatioaally rigid system forced by the motor 2. shaft 4 λ and scaife 5 is at S, approximately on the plane of the , axial air bearing or just slightly below the plane.

Is this case, the first radial critical frequency is given by Ρ=2Π /k/a where k is the radial stiffness of the silent blocks 3 and m is the saass of the rigid motor/shaft/scaife system. The motor 2 is run at a frequency higher than this first radial critical frequency.

Purely as an example, the scaife running speed can be 3,000 rpm, with a scaife mass of 15 kg and a mass of the motor 2 and the remainder of the system of 7 kg. The blocks 3 have a damping ratio of 0.3. At the working speed, the phase angle is assumed to be 165® '10 (instead of the theoretical 180°>- The speed ratio is theoretically 3, giving a natural frequency 105” s 24.0 ft/mm. The axial stiffness Is determined by the stiffness of the axial air bearing and is preferably / from half to one tenth of the radial stiffness of the blocks 3, the choice depending upon mounting accuracy and bearing pre-load.

If the air bearing is an aerostatic bearing, an air pressure reservoir is necessary to avoid running the isatos 2 without pressurised air- The motor 2 is only energised if a certain minimum air pressure Is present. r The reservoir should contain at least sufficient air to j pressurise the faeariog during running out (i.e. as the 9c seaife 5 slows to a. stop), and preferably for sufficient time to polish a facet (or even a whole stone) plus th© running out time. The electrical resistance of the air gap can be checked to avoid starting the motor 2 before the electrical resistance reaches a threshold, e.g. 100 ohms. Such measures are not necessary when using an aerodynamic (e.g. herringbone) air bearing.

Fleurs 2 Figure 2 shows as arrangement similar to that ©£ Figure 1, but the shaft 4 carries a universal joint 10 which permits rotary motica between the shaft 4 and the scaife 5 about transverse axes, whilst transmitting torque (a splined arrangement can be used). However, the radial movement of the scaife 5 can be blocked using a magnetic clamp 11. When blocked, the system is very similar to that of Figure 1 but is act sensitive to misalignment of the motor 2. However,-in a different arrangement, the blocks 3 can be replaced by rigid blocks to prevent lateral float (as well as axial float) of the motor 2 and the scaife S can be run under-critically so that it cat bear high tangential loads e.g, for mlti-fang polishing.

Figured Figure 3 shows a somewhat different arrangement in which the motor shaft 4! is connected to the scaife 5 by a torque transmitter 12 which permits limited movement in any radial direction and limited axial movement- There is a radial spring system 13 which applies an. elastic t bias to radial movements of the scaife 5. in addition, there is as axially-aovable clutch plate 1¾ which cas. he made to hear against the underside of the scaife 5, The motor 2 is carried os the table 1 by means of blocks 15 which allow axial movement as well as radial float, and a controlled preload is applied to the casing of the motor 2 hy as arrangement indicated schematically as a pivoted an 16 having a pre-load applied by a spring 17 which can be reduced by means of a coil is. During the stop and start cycle, the saotor 2 is lifted up and keeps the scaife 5 ic balance due to the engagement of the clutch plate 14 with the underside of the scaife 5.

During over-critical running, the air bearing can be pre-loaded by the deadweight of the aotsr 2 via the torque transmitter 12, possibly additionally using a magnetic pre-load as ia Figures 1 and 2. The first radial critical frequency is determined by the mass of the scaife 5 and the spring constant of the spring system 13. Γ Figure 4 t Figure 4 shows an arrangement in which, with a heavy scaife 5 and well engineered mounting of the scaife 5 onto the motor drive, the radial hearing is ss the housing of the motor 2. Because the motor housing makes only very small oscillatory movements, there is so air 5 bearing and the blocks 3 are replaced by axially-stiff rolling balls 21 and the radial stiffness is purely determined by a radial working spring or spring and damper system 22 (shown.schematically). The ball bearing system is carried by as. annular rase 23 hung ©ο, pre-stressed bolts 25 and engages, a motor bousing flange 25.

As the unbalance ecomtxicity becomes quite small when running over critically, and the proper frequency can be kept low by low spring stiffness and damping, the force 15 transferred to the table 1 (which is approximately / determined by the product of the spring stiffness and the displacement) can be kept low and hence the fable excitation is very low, giving smoother running equipment.

Claims (5)

Claims

1. « A gemstone polishing apparatus comprising a scaife (5), a supporting structure (1), as axial bearing (6 or 21,23) supporting the scaife ¢5), and a drive ¢

2. ) for 5 the scaife ¢5), characterised in that the drive (2) is arranged to drive the scaife ¢5) at a speed above Its first radial critical frequency, and the axial bearing ¢6,21,23) Is axially stiff but allows radial float of the scaife ¢5). Ί q 2. 'The, apparatus of Claim 1, wherein the drive is a motor (2) generally coaxial with the scaife ¢5) and souatecl. ©a the supporting structure (I).

3. The apparatus of Claim 2, wherein the motor (2) is , mounted se the supporting structure ¢1) by elastic 15 mount lag means (3 or IS).

4. The apparatus of Claim 2 or 3, wherein the motor drive ©haft (4) Is rigidly fixed to the scaife <5). 5. The apparatus of claim 4, wherein the centre of 20 gravity (9) of the scaife ¢5), motor (2) and motor sha] ¢4) is approximately on the plane of tspj<)0—s. u«, whe axial scaife bearing ( 6). δ. The apparatus of ©ny of Claims 1 to 3, wherein the motor (2) is connected to the scaife (5) by way of a \ flexible coupling (10,13)Ύ 7- Th® apparatus of any of Claims 1 to 3, wherein 5 rotary motion is permitted about transverse axes between the motor drive shaft (4) and the scaife (5), S- The apparatus 10 5>- The apparatus of any of the preceding Claims, and comprising means ( 11,14) for preventing radial float.of the scaife (5), at will. 10- The apparatus of any of the preceding Claims, wherein the axial scaife bearing is an axial fluid 15 bearing (6)XX. The apparatus or any of Claim 10, wherein one part of the axial fluid bearing (6) is the rear face of the ~ scaife ¢5)I 12- The apparatus of any of the preceding Claims, 20 wherein the scaife ¢5) is at least in part ferro-masnetie, and a bearing pre-load is obtained by direct, magnetic action on the scaife (5) by a magnetic means (7) fixed to the supporting structure (1). r ; 13, The apparatus of any of the preceding Claims, wherein the drive is a motor (2) generally coaxial with 5 the scaife (5) and mounted on the supporting structure hy mounting means (3,15) which apply aa axial pre-load to the scaife axial bearing (6), 14.. The apparatus of any of the preceding Claims, wherein the radial float of the scaife (5) is limited by 10 a bearing (S) around the scaife drive shaft (4). 15. The apparatus of any of th© preceding Claims, wherein a radial spring system <225 applies an elastic bias to radial movements of the scaife <5). 16. The apparatus of Claisa 15, wherein the radial spring system ¢22) includes damping, 17. A method of polishing a gemstone, comprising using a scaife (5) which is supported by as axial bearing is ( driven at a speed .above its first radial critical frequency. 18. Gemstone polishing apparatus, substantially as 4r> herein described with reference to, and as shown in, any j one of . the Figures of the accompanying drawings. 19. A method of polishing a gemstone, substantially as

5. Herein described with reference to any of the Figures of fhe accompanying drawings.