EP0649706B1 - Tête à faire le lapping et le polissage pour granit et des roches semblables - Google Patents

Tête à faire le lapping et le polissage pour granit et des roches semblables Download PDF

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Publication number
EP0649706B1
EP0649706B1 EP94202683A EP94202683A EP0649706B1 EP 0649706 B1 EP0649706 B1 EP 0649706B1 EP 94202683 A EP94202683 A EP 94202683A EP 94202683 A EP94202683 A EP 94202683A EP 0649706 B1 EP0649706 B1 EP 0649706B1
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EP
European Patent Office
Prior art keywords
lugs
head
spindles
oscillating
toothed
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.)
Expired - Lifetime
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EP94202683A
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German (de)
English (en)
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EP0649706A1 (fr
Inventor
Luca Toncelli
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B41/00—Component parts such as frames, beds, carriages, headstocks
    • B24B41/04—Headstocks; Working-spindles; Features relating thereto
    • B24B41/047—Grinding heads for working on plane surfaces
    • B24B41/0475—Grinding heads for working on plane surfaces equipped with oscillating abrasive blocks, e.g. mounted on a rotating head

Definitions

  • the present invention relates to a lapping and polishing head for slabs and panels of granite and similar ceramic materials of the type described in Italian Patent No. 1,175,191 in the name of Marcello TONCELLI and in DE-A-3408443.
  • the lapping head described in the aforementioned patent is of the type comprising a certain number of oscillating grinding segments (six in the preferred example of embodiment) rotating together with the head about a central shaft of the latter and made to oscillate by a mechanism formed by an inclined disc rotating at a speed varying by a few per cent with respect to that of the said head and connected to crank mechanisms ensuring oscillation of the said segments of the head.
  • the operating principle of said head is illustrated, for the sake of clarity, in Figures 1 to 3 of the drawings accompanying the present patent application.
  • the grinding segments which are made to oscillate both by a cam according to the aforementioned German patents and patent applications, and by the inclined rotating disc mechanism illustrated in the aforementioned Italian patent of Marcello Toncelli, perform a complete angular oscillation, over an amplitude of the order of a few tens of degrees for about every ten revolutions of the said head.
  • the grinding segments move forwards and backwards with respect to a central oscillation axis of theirs, at certain moments the oscillating velocity is added to the rotational velocity of the grinding elements, while at certain other moments the same oscillating velocity is subtracted from the rotational velocity; furthermore, since the oscillating movement is derived from different positions on the circumference of the inclined disc, the oscillating movements of the said grinding segments are mutually phase-displaced by angles corresponding to a trigonometric function (sine or cosine) of the respective angular positions on the circumference.
  • the angular velocity vector not only varies in terms of modulus from grinding element to grinding element by a percentage amount, due to the oscillating velocity, which in specific cases can be equal to about 10%, but also varies with time between a maximum value and a minimum value corresponding to the angular velocity of the casing of the head to which is added or subtracted 10% of the said angular velocity.
  • the pairs of toothed members connect together all the adjacent radial shafts and form an internally closed system for transmission of the oscillating movement of the said shafts because, if the radial shafts mounted on the same head are counted and provided that the number of said shafts is even, the first and last shaft are connected directly by a pair of toothed members, as well as indirectly by all the pairs of toothed members located in between.
  • This system consisting of a closed series of toothed members is able to function correctly in only two cases, namely if a single rolling roller is used against the cam so that all the radial shafts are driven by the single radial shaft connected by a crank mechanism to the said connecting roller, or else, if there is more than one roller (for example four), the crank mechanisms must take account of the phase differences which exist between the different rollers.
  • the crank mechanisms must take account of the phase differences which exist between the different rollers.
  • the mechanical stresses on them may be so severe as to give rise to the risk of breakage of the roller, its supports or the crank mechanism, or there is the risk of premature wear of the cam caused by the excessive stresses on the said roller.
  • a main aim of the present invention is to provide a roughing, lapping and polishing head for stone material such as granites or the like and ceramic materials, in which the aforementioned problems of an imbalance are reduced as far as possible or even eliminated entirely.
  • Another aim of the present invention is to provide a roughing, lapping and polishing head, as defined above, which reduces or eliminates imbalances using means which are as simple, cheap and efficient as possible.
  • a roughing and lapping head 10 comprises a central rotating shaft 12 descending from a connection flange 14 accommodated inside a housing 16 for moving parts, said housing 16 being connected at the bottom by means of a flange 18 to a fixed cover 20 which with an external guard 22 and an internal gasket 24 forms a hermetically sealed system for a casing 26 of the said head 10.
  • the casing 26 consists of two half-shells located one on top of the other, i.e. an upper one 28 and a lower one 30, and encloses all the mechanisms which perform rotational driving and oscillation about radial axes of grinding segments, such as the grinding element 32a which can be seen in Figure 1.
  • the grinding element 32a (like other similar grinding elements not shown herein) is fixed to a lug 34a connected to a shaft 36a penetrating into the lower half-shell 30 of the casing 26.
  • the number of grinding segments must be greater than one, six being a usual number which also facilitates the design.
  • the shafts 36a-f, about which the lugs 34a-f of the grinding segments 32a-f oscillate, are accommodated inside bush bearings 38a-f passing through the lower half-shell 30 and are connected to lever arms 40a-f which, by means of spindles 42a-f fixed to an outer ring 44 of an inclined rotating disc 46, receive from the same oscillating disc 46 an alternating movement substantially along the direction of the central axis 48 of rotation of the head 10.
  • the said oscillating disc 46 comprises, in addition to the outer ring 44, a ball bearing 50 and an inner ring 52 connected integrally to a hollow shaft 54 rotating coaxially with the central shaft 12 of the head 10, but at a different speed which is determined by a system of toothed members 56, 58, 60 and 62, known for some time in the prior art, for example already described in the aforementioned German Patent No. 800,112 to which the reader is referred with particular reference to Figure 1 thereof.
  • the inclined rotating disc 46 is substantially identical to the disc 7 which is shown in Figures 1 and 2 of the aforementioned Italian Patent No. 1,175,191 in the name of Marcello TONCELLI, compared to which it offers only an improved system for receiving the spindles 42a-f and an improved articulated connection 64 between the spindles 42a-f and the lever arms 40a-f.
  • the inclined disc 46 formed by the outer ring 44, the ball bearing 50 and the inner ring 52, carries, fixed to its periphery, six spindles 42a-f, each of which engages with a lever arm 40a-f which operates respectively a shaft 36a-f of each of the lugs 34a-f carrying the grinding segments 32a-f (not shown in Figure 3).
  • FIG. 3 is a very basic illustration of the head of the head shown in Figures 1 and 2, it can be seen that arbitrarily fixing an axis of the origins 0 emerging from the centre of the said head and passing through a position A corresponding to a first spindle 42a, the lug 34a connected thereto via the lever arm 40a is moved for example forwards, with respect to the head, at a velocity V determined by the axial displacement of the inclined disc 46.
  • the spindle 42b emerging from the point B on the circumference of the disc 46 displaced by 60° moves at a velocity equivalent to that of the spindle at the point A multiplied by the cosine of the angle between the two points and, consequently, the velocity of the lug 34b moved by the spindle 42b emerging from the point B will be equivalent to Vcos60° , i.e. 1/2.V.
  • the lug 34c controlled by the spindle 42c emerging from the point C will move at a velocity Vcos120° , i.e. -1/2.V.
  • the lug 34d controlled by the spindle 42d emerging from the point D will move at a velocity Vcos180 , i.e.
  • the rotational velocity of the said grinding elements which is obtained from the vectorial sum of the rotational velocity of the head and the oscillating velocity about the spindles 36a-f, is variable about a mean value, obtained from rotation of the head, about which the value of the oscillating velocity of the grinding elements varies. Since the centrifugal forces acting on the grinding segments are directly proportional to the square of their angular velocity and since this angular velocity could undergo variations of the order of 10% on account of the oscillations imparted to the said grinding segments, it follows that there would be variations in centrifugal forces of the order of 20% on the grinding elements with the induction of dynamic imbalance vibrations. Vibrations of this type are very difficult to dampen because the velocity variations are quite considerable and the only way to reduce or eliminate them is to reduce these variations or compensate them in pairs.
  • FIG. 4 A schematic representation of this compensation system of the prior art is illustrated in Figure 4 which shows six lugs 34'a-f of grinding segments moved by four rollers 66a-d resting on a circular cam 68, obviously inclined, rotating inside a head 10' at different speeds according to the universally known method of gear groups, the rollers 66a-d actuating by means of lever arms 40'a, 40'c, 40'd e 40'f the respective lugs 34'a, 34'c, 34'd and 34'f via their shafts 36'a, 36'c, 36'd and 36'f and all the shafts 36'a-f of the lugs 34'a-f being connected together by identical gears 70a-f, whereby the gears all engage with each other so as to form inside the said head 10' a chain of toothed members forming an internally closed system.
  • An inclined disc 146 is provided with an outer ring 144 of a bearing 150 and hollow shaft 154 identical to the outer ring 44 and hollow shaft 54 of the embodiment of the prior art illustrated in Figures 1 and 2 and functions in exactly the same manner as the inclined disc 46 of the said two figures, with the sole exception that, instead of six spindles 42a-f, it accommodates only three spindles 142b, 142d and 142f.
  • the distribution of the oscillating velocity of the lugs 134a-f is that illustrated in Figure 5 where, the oscillating velocity of the lug 134a having been indicated by V, for reversal caused by the pair of toothed members 180a and 140b, the oscillating velocity of the lug 134b is equivalent to -V.
  • phase-displacement, by 120°, of the spindle 142d with respect to the spindle 142b results in the oscillating velocity of the lug 134d being equivalent to 1/2.V and the reversal caused by the pair of toothed members 140d and 180c produces an oscillating velocity equivalent to 1/2.V of the lug 134c.
  • the phase-displacement, by 240°, of the spindle 142f with respect to the spindle 142b results in the oscillating velocity of the lug 134f being equivalent to 1/2.V and reversal of the pair of toothed members 140f and 180e produces an oscillating velocity equivalent to 1/2.V of the lug 134e.
  • the distribution of the oscillating velocity, from the lug 134a to the lug 134f, is: V, -V, -1/2.V, 1/2.V, -1/2.V and 1/2.V. It can be seen that the pair of lugs 134a and 134b compensate internally the oscillating velocity V and -V, as do the pairs of lugs 134c and 134d and 134e, 134f, compensating internally the oscillating velocity -1/2.V and 1/2.V, -1/2V and 1/2V.
  • the spindles 242c and 242f are connected at diametrically opposite points of the outer ring 244 of the inclined disc 246 which is similar to the inclined disc 46 of the prior art, but is provided with only two opposite spindles, i.e. phase-displaced by 180°.
  • the pair of toothed members 240f, 260e reverses the oscillating movement so that the oscillating velocity of the lug 234e is equal to V and hence the pair of toothed members 260e, 280d again reverses the oscillating movement so that the oscillating velocity of the lug 234d is -V again.
  • examining the lugs 234a-f it can be seen that they are made to perform alternately opposite oscillating movements having in succession the velocities V, -V, and V, -V. This means that each lug has an oscillating velocity exactly opposed by that of the adjacent lug and hence that the oscillating velocities compensate each other exactly in pairs, not reversing substantially in any way the equilibrium of the grinding segments of the head 210.
  • Said lever arms 140 and 240 comprise a stirrup section 310 provided with a recess 312 designed to receive an articulation of one of the spindles 242c or 242f, for example, such as the articulated joint 64 shown in Figure 1, followed by a flat section 314 provided with a central hole with grooved walls 316 designed to engage with one of the shafts 136b, 136d and 136f of the lugs 134b, 134d and 134f, of the head 110, or one of the shafts 236c and 236f of the lugs 234c and 234f of the head 210.
  • the flat section 314 has connected to it an inclined section 318 provided with teeth designed to couple the lever arm 140 with the truncated gear 180 or the lever arm 240 with one of the double-toothed member segments 260, depending on whether they are used in the head 110 or in the head 210.
  • Figures 11 and 12 show one of the double-toothed member segments designed to transmit movement to the shafts 236b and 236c of the lugs 234b and 234c of the head 210.
  • Said segment 260 comprises a flat central zone 320 provided with a central hole 322 with grooved walls designed to engage with one of the shafts 236b or 236c and connected to two inclined sections 324 and 326 provided with teeth for receiving the movement from the lever arms 240 and transmitting it to the truncated toothed-member segments 280.
  • Figures 13 and 14 show the truncated toothed-member segments 180 and 280 designed to transmit the movement from the shaft 136b to the shaft 136a, from the shaft 136d to the shaft 136c and from the shaft 136f to the shaft 136e in the head 110, or from the shaft 236b to the shaft 236a and from the shaft 236c to the shaft 236d in the head 210.
  • Said truncated toothed-member segments comprise a flat zone 330 provided with a hole 332 with grooved walls for engagement with one of the shafts 236a or 236d of the respective lugs 234a and 234d and connected to an inclined section 334 provided with teeth driven by the teeth 318 of the lever arms 140 in the head 110 and by the teeth 326 of the double toothed-member segments 260 in the head 210.
  • These segments 180 and 280 are truncated at their ends to prevent closure of the chain of toothed members inside the head 110 and 210 so as to accommodate all possible manufacturing tolerances in the lever arms 140 and 240, the teeth 318, 324, 326 and 334 and the angular positions of the spindles 142b, 142d and 142f of the head 110 and the spindles 242c and 242f of the head 210.
  • the lever arms 140 and 240 must not necessarily be made in the form of segments with flattened sides, but, if there is sufficient space, they could also be made so as to have a circular shape or in the form of a circular segment with diverging sides. The same is applicable to the double toothed members 260 or the truncated toothed members 180 and 280. Also, the connection between the spindles 142 and 242 and the lever arms 140 and 240 must not necessarily be of the spherical type 64 shown in Figure 1, it being possible to use in their place other joints well known to persons skilled in the art.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Grinding And Polishing Of Tertiary Curved Surfaces And Surfaces With Complex Shapes (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)

Claims (6)

  1. Tête rotative de polissage et de rodage pour des pierres de granit et similaires, comportant un disque incliné (146, 246) tournant autour d'un axe de rotation (48) de la tête, une pluralité de pattes oscillantes (134a à 134f ; 234a à 234f) agencées circonférentiellement autour du disque, munies de segments de meulage et pouvant tourner autour de directions radiales respectives en référence à l'axe de la tête, une pluralité de broches (142b, 142d, 142f ; 242c, 242f) faisant saillie vers l'extérieur à partir de la périphérie du disque incliné, s'étendant entre deux pattes adjacentes et reliées à l'une de celles-ci de manière à la faire osciller à la suite de la mise en rotation du disque incliné, caractérisée en ce que :
    entre deux broches consécutives sont agencées au moins deux pattes ;
    chaque patte oscillante est munie d'un élément denté respectif (140, 240 ; 180, 280 ; 260) et les éléments dentés des pattes situées entre deux broches consécutives engrènent l'un avec l'autre en mettant ainsi en rotation contraire leurs pattes respectives ;
    chaque broche est agencée sur l'élément denté de la patte adjacente à laquelle elle est reliée, de sorte que cette dernière oscille par suite du fonctionnement de cet élément denté lorsque le disque incliné tourne, alors que les autres pattes agencées entre les broches consécutives sont mises en rotation contraire par les éléments dentés engrenant les uns avec les autres, de sorte que les éléments dentés engrenant ne forment pas une chaíne fermée.
  2. Tête rotative selon la revendication 1, dans laquelle il existe trois broches (142b, 142d, 142f ; 242c, 242f) qui font saillie à 120° à partir du disque incliné (146, 246) et dans laquelle deux pattes oscillantes (134a à 134f ; 234a à 234f) sont agencées entre chaque paire de broches consécutives.
  3. Tête rotative selon la revendication 1, dans laquelle il existe deux broches (142b, 142d, 142f ; 242c, 242f) qui font saillie à partir de parties opposées du disque incliné (146, 246) le long d'une même direction diamétrale en référence à l'axe (48) de la tête, et dans laquelle le nombre de pattes oscillantes (134a à 134f ; 234a à 234f) agencées entre ces broches de chaque côté par rapport à la direction mentionnée ci-dessus est un nombre impair.
  4. Tête rotative selon la revendication 3, dans laquelle le nombre impair est trois.
  5. Tête rotative selon la revendication 3, dans laquelle le nombre impair est cinq.
  6. Tête rotative selon la revendication 3, dans laquelle le nombre impair est sept.
EP94202683A 1993-09-22 1994-09-17 Tête à faire le lapping et le polissage pour granit et des roches semblables Expired - Lifetime EP0649706B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITPD930186 1993-09-22
ITPD930186A IT1263400B (it) 1993-09-22 1993-09-22 Perfezionamenti a testa levigatrice e lucidatrice per graniti e pietresimili

Publications (2)

Publication Number Publication Date
EP0649706A1 EP0649706A1 (fr) 1995-04-26
EP0649706B1 true EP0649706B1 (fr) 1999-01-20

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EP94202683A Expired - Lifetime EP0649706B1 (fr) 1993-09-22 1994-09-17 Tête à faire le lapping et le polissage pour granit et des roches semblables

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EP (1) EP0649706B1 (fr)
DE (1) DE69416076T2 (fr)
IT (1) IT1263400B (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1293124B1 (it) * 1997-06-18 1999-02-11 Giani & Grazzi Meccanica S R L Testa levigatrice e lucidatrice per lastre lapidee
ITMI20040311U1 (it) * 2004-06-24 2004-09-24 Dario Toncelli Testa di le igatura per materiali lapidei duri
IT1404573B1 (it) * 2011-02-24 2013-11-22 Toncelli Macchina e mandrino per la levigatura o lucidatura di lastre di materiale lapideo o litoide.
ITFI20120227A1 (it) * 2012-10-25 2014-04-26 Comes Srl Carter di contenimento per teste portautensili
CN103331679A (zh) * 2013-06-17 2013-10-02 廖季锋 一种固定式抛光机
CN111761504B (zh) * 2020-07-07 2022-03-18 温州职业技术学院 一种家具生产用环保型表面处理装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2105634A (en) * 1936-04-10 1938-01-18 Marbriere De Paris Sa Soc Machine for facing the surfaces of hard substances by pressure
DE800112C (de) * 1949-07-15 1950-09-01 Karl Dipl-Ing Fickert Flaechenschleif- und Poliermaschine
DE2607804A1 (de) * 1976-02-26 1977-09-01 Heinrich Fickert Vorrichtung zum flaechenschleifen von hartgestein und aehnlichen materialien mit diamantwerkzeugen
IT1175191B (it) * 1983-03-14 1987-07-01 Marcello Toncelli Testa rotante con mole a settori oscillanti, con meccanismo di comando a disco inclinato, per levigatura di marmi, graniti e pietre dure
IT1247256B (it) * 1991-04-23 1994-12-12 Simec Spa Testa per la lucidatura di marmo, granito e materiali lapidei in genere con mole oscillanti.

Also Published As

Publication number Publication date
IT1263400B (it) 1996-08-05
ITPD930186A0 (it) 1993-09-22
DE69416076T2 (de) 1999-06-02
EP0649706A1 (fr) 1995-04-26
DE69416076D1 (de) 1999-03-04
ITPD930186A1 (it) 1995-03-22

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