CA2076660A1 - Milling machine - Google Patents
Milling machineInfo
- Publication number
- CA2076660A1 CA2076660A1 CA 2076660 CA2076660A CA2076660A1 CA 2076660 A1 CA2076660 A1 CA 2076660A1 CA 2076660 CA2076660 CA 2076660 CA 2076660 A CA2076660 A CA 2076660A CA 2076660 A1 CA2076660 A1 CA 2076660A1
- Authority
- CA
- Canada
- Prior art keywords
- platform
- working table
- relative
- eccentrics
- worm
- 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.)
- Abandoned
Links
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B27—WORKING OR PRESERVING WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES IN GENERAL
- B27C—PLANING, DRILLING, MILLING, TURNING OR UNIVERSAL MACHINES FOR WOOD OR SIMILAR MATERIAL
- B27C5/00—Machines designed for producing special profiles or shaped work, e.g. by rotary cutters; Equipment therefor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q27/00—Geometrical mechanisms for the production of work of particular shapes, not fully provided for in another subclass
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B44—DECORATIVE ARTS
- B44B—MACHINES, APPARATUS OR TOOLS FOR ARTISTIC WORK, e.g. FOR SCULPTURING, GUILLOCHING, CARVING, BRANDING, INLAYING
- B44B3/00—Artist's machines or apparatus equipped with tools or work holders moving or able to be controlled substantially two- dimensionally for carving, engraving, or guilloching shallow ornamenting or markings
- B44B3/06—Accessories, e.g. tool or work holders
- B44B3/061—Tool heads
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B44—DECORATIVE ARTS
- B44B—MACHINES, APPARATUS OR TOOLS FOR ARTISTIC WORK, e.g. FOR SCULPTURING, GUILLOCHING, CARVING, BRANDING, INLAYING
- B44B3/00—Artist's machines or apparatus equipped with tools or work holders moving or able to be controlled substantially two- dimensionally for carving, engraving, or guilloching shallow ornamenting or markings
- B44B3/06—Accessories, e.g. tool or work holders
- B44B3/065—Work holders
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Wood Science & Technology (AREA)
- Forests & Forestry (AREA)
- Nitrogen And Oxygen Or Sulfur-Condensed Heterocyclic Ring Systems (AREA)
- Machine Tool Units (AREA)
Abstract
A milling machine is provided with a mechanism (7) intended for mutual movement of the working table (3) and a platform (5) and consisting of at least two pairs of eccentrics (8, 10; 9, 11) located on both sides of a trajectory (O-O) of movement of the working table (3). The internal eccentric (8, 10) of each pair is mounted inside the other, external eccentric (9, 11) mounted in the platform (5) carrying the spindle head (6), has the possibility of rotation and fixing its position in relation to the external eccentric (9, 11) and is kinematically connected to the drive (2) for movement of the working table (3) in relation to the stand (1).
Description
207 666~ 1 MILLING MACHINE
Field of the Art The present invention relates to mechanical engineering and more Particu1ar1y to mi11ing machines.
Background of the Invention Well known in the art are milling machines adapted for milling contoured slots and producing intricate and repeat-ing patterns and relie~s. UsuallY each working motion of the table and of the working spindle in such machines is effect-effected with the help o~ an individual comPuter-controlled drive. Such a system re~uires that the machine should be provided with a large number of electric drives and with a sophisticated electronic control system comprising a central ~ processor, -a sensor, and other elements of the automatic control system. This involves an increase in the power con-sumption and weight of the machine, makes the machine serv-- icing more complicated, and adds to the cost of the machine.
~nown in the art is a milling machine comprising a bed, a working table for clamping workpieces thereto, mounted on the bed with the possibility of travel and provided ~ith a drive ensuring its movement relative to the bed; a platform mounted with the possibility of movement relative to the bed and carrying at least one spindle head intended for securing a working tool; and a mechanism for ensuring relative move-ment of the working table and the platform (SU, A, 1511124~.
This machine is noted for a simple desi~n, its working motions are ensured by purely mechanical means from one ' drive. The mechanism for ensuring relative movement of the working table and the platform comprises a pair of eccen-trics, horizontal plates and vertical plates, arranged in ~uides of said horizontal Plates and transmittin~ motion to the platform carrying the spindle heads. This milling ma-' chine is disadvantageous in that it cannot provide curvi-linear Patterns and intricate reliefs, because the working platform and the spindle heads can perform onlY a limited number of working motions. Furthermore, the machine is pro-.
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vided with a cumbersome mechanism for ensuring relative movement of tne working table and the platform. This mech-anism is a source of losses of the drive nechanical energy because of friction experienced by the vertical plates in the guides. This makes the machine inefficient and un-reliable in operation.
Disclosure of the Invention The present invention is directed to the provision of a milling machine, in which a mechanism for ensuring relative movement of its working table and platform is designed so as to secure by purely mechanical means a plurality of differ-ent combinations of the working motions of the machine mem-bers.
- Said object-is accomplished by that in a milling ma-chine comprising a bed, a working table for clanping work-pieces, mounted on the bed with the possibility of travel and provided with a drive ensuring its movement relative to the bed; a platform mounted with the possibility of travel relative to the bed and carrying at least one spindle head intended for securing a working tool; and a mechanism for ensuring relative movement of the working table and the platfor~, according to the invention, the mechanism for en-suring relative movement of the working table and the plat-form is made in the form of at least two pairs of eccentrics .
disPosed on both sides in relation to the path of travel of the working table, one of the eccentrics of each pair, name-ly, the inner eccentric, being disposed inside the other, outer eccentric, which is mounted on the platform carrying the spindle head with the possibilitY of rotation and fixing its Position relative to the outer eccentric and is kinema-tically linked with the drive ensuring the motion of the working table relative to the bed. The spindle head is mounted with the possibility of travel relative to the plat-form and is provided with a drive for ensuring its movement relative to the platform, said mechanism being kinematically linked with one of the eccentrics.
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Such an arrangement ensures an infinite variety of com-binations of the eccentricities of the two eccentrics; this - feature allows anY versions of a repeating ~eometrical pat-tern to be produced on the surface being worked. In com-bination with the movement of the spindle head, provided by the same drive, an additional infinite variety of pattern versions is ensured; ail the working motions of the machine are effected from one drive with the help of purely mechan-ical means.
The outer eccentrics are Preferably mounted on the platform rotatably and with the possibility of fixing their position relative to the platform. In this case the adjust-ment for varying the co~bination by the eccentricity of the ---- - eccentrics is simplified. --The drive for moving the spindle head relative to the platform preferably comprises a carrier installed on the inner eccentric rotatably and with the possibility of fixing its position relative to the inner eccentric. This provides adjustment of the phase of the spindle head travel.
The outer eccentrics are preferably kinematicallY in-terlinked. This ensures precise adjustment of the eccentri-: city.
Each outer eccentric is Preferably made with an extern-al cam surface having a elevation in the direction perpendi-:- ~5 cular to the plane of the working table, and the platform is provided with a carrier for interacting with said cam sur-face.
~ This ensures additional motion of the platform with the ; spindle heads, effected by the same drive, ~or producing in-tricate surface reliefs.
'~ Each outer eccentric preferably has a worm wheel in-stalled for movin~ together with the platform and rotatably .~ relative to the platform, the carrier being fixed rigidly in : said worm wheel; a shaft is mounted rotatablY in the plat-~orm and has worms fixed rigidly thereon, said worms meshing with said worm wheels. This ensures precise and simultaneous 2076~60 4 adjustment of the phase of the vertical travel of the plat-~orm.
The drive for moving the working table is preferabl-~made as a rack-and-pinion mechanism, comprising at least one rack attached to the workin~ table, the pinion of the rack-and-pinion mechanism is linked kinematically with a pair of shafts, and each inner eccentric is rigidly fixed on one of these shafts. This simplifies the design of the drive mech-anism, minimi~es the consumption of power, and ensures high accuracy of the relative working movements of the machine.
The outer and inner eccentrics of each pair of the ec-centrics are preferably interlinked by means of a uorm-and-worm gear, the worm of each worm-and-worm gear being dispos-ed on the extsrnal eccentric. This ensures simple and pre-cise adjustment of the mutual position of the eccentrics andreliable fixing of the eccentrics after the adiustment.
The spindle head is linked with the carrier by means of an oscillating crank gear with a variable radius of the crank. This provides additional versions of the working movements of the spindle head along with the movements of the platform carrying the spindle head.
Brief Description of Drawings Given hereinbelow is a detailed description of the pre-sent invention, illustrated by the accompanying drawings, in - 25 which:
Fig. 1 is a general view of a milling machine according to the invention, longitudinal section;
Fig. 2 is view A in Fig~. 1 (some units and parts of the machine are conventionally not shown);
Fig. 3 is a section along III-III in Fig. l;
Fig. 4 is a version of the structure of a part of the mechanism for ensurin~ relative travel of the working mecha-nism and the platform, shown in Fig. l;
Figs. 5-20 show different adjustments of the mechanism for ensuring relative travel of the working table and the platform, and the corresponding patterns produced on ma-.
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207666~ s chined workpieces; in Figs. 6, 8, 10, 12, 14, 16 and 18 in the upper part of each drawing a pattern is shown with the working table being stationary, whereas in the lower part of the drawing a pattern is shown with the working table in motion.
Preferred Embodi~ents The machine of the invention comprises a bed 1, in the lower part of which a reversing driv~, 2 is installe~, kine-~atically linked with a wor'~ing table 3, ~ounted on the bed l with the possibility of ~oving along a path lengthwise of the longitudinal axis 0-0 of the ~achine ~Fig. 3) and pro-vided with units (not shown) for clamping a workpiece 4. The bed 1 mounts a ~ovable platfor~ 5. The Platform 5 is mounted ~ movably relative to the bed l-and-carries two spindle heads - 15 6. The machine is provided with a mechanism 7 for ensuring relative movement of the working table 3 and the platform 5.
The mechanism 7 has two pairs of eccentrics 8, 9 and 10, 11 ; ~Figs. 1, 3) disposed on both sides of the path of travel ; 0-0 of the working table 3. The inner eccentrics 8 and 10 - 20 are mounted rigidly on vertical shafts 12, 13 which carry on ; their free ends conical gears 14, 15 that are in ~esh with ~ .~
conical gears 16, 17 mounted on a horizontal shaft 18 linked with the drive 2 through a r,eduction gear 19 (which can be a gearbox or a variator).
~ 25 The outer eccentrics 9, 10 are mounted rotatably on the ,; inner eccentrics 8, 10. The outer eccentrics 9, 10 are in-. terlinked with the inner eccentrics 8, 10 through worm-and-worn gears, comPrising worm screws 20, 21 installed rotatab-~: ly in the outer eccentrics 9, 11 and meshing with worm wheels 22, 23 cut on the inner eccentrics 8, 10. With such an arrangement the outer eccentrics 9, 11 can be rotated re-lative to the inner eccentrics 8, 10 for adjustment, and their mutual position after the adjustment can be reliably ~; fixed. It is obvious that other embodiments of the mechanism ; .
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' - ' ' 2 ~7 ~ 6 for adjusting the mutual position of the outer eccentrics 9, 11 and inner eccentrics 8, 10 are also possible, but the structural embodi~ent describçd hereinabove should ~e pre-~erred. The described structure ensures an~ combinations of the eccentricities of the outer eccentric and the inner ec-centric of each pair, ranging from their alignment, when the total eccentricity is equal to the sum of the eccentricities of the t~o eccentrics, to such a position, ~hen the total eccentricity will be equal to the difference of the eccen-tricities of the two eccentrics (for instance, to zero,when the t~o eccentricities are equal~. In this case the value of the total eccentricitY defines the amplitude of travel of the platform 5.
The spindle heads 6 are movably mounted on the''~platfor'm 15 5 on links 25, 26 disposed in guide openings 27, 28 of the platform 5, and each spindle head 6 is provided with a mech-anism for moving it relative to the platform 5. This mecha-nism is a carrier 29 (30) mounted rotatably on the inner ec-' centric 8 (10) with the possibility of fixing the position of the carrier relative to the inner eccentric. For this to be done, the carrier 29 (30) is provided with a worm screw 31, arran~ed rotatably in the inner eccentric 8 ~10) and meshing with a worm wheel 32 cut in the inner eccentric 8 (10). With such an arrangement the carrier 29 (30) can be rotated relative to the inner eccentric 8 (10) for adjust-ment and their mutual position after the adjustment can be reliably fixed. It is obvious that other embodiments of the mechanism for adjusting the'mutual position of the carrier 29 (30) and the inner eccentric 8 (lO) are also possible, but the structural embodiment described hereinabove should ~; be preferred. With suoh a structure of the mechanism for moving the spindle head 6, the phase of travel of the spin-dle head 6 relative to the platfor~ 5 varies, depending on the angular position of the carrier 29 (30) with respect to the inner eccentric 8 (10), as will be shown hereinbelow.
, - ' . . , , ' ~: ~' - , ,: , ~ ~ , 2076~6~ 7 In the ~iven e~bodi~ent one of the spindle heads 6 is provided with a mechanism for moving it in relation with the platform 5 with a crank 33, installed on the carrier 29 and articulated with the link 25. The crank 33 is ~ounted on the carrier 29 with the aid of an adjusting screw 34 that inter-acts with the internal thread ~not shown) of the crank 33.
The adiusting screw 34 is arranged in the carrier ~9 rota-tably and, in combination with the carrier 29, the crank 33 and the link 25, it makes up an oscillatin~ crank gear with a variable radius of the crank. With such an arrangement the inclination of the elements of the pattern produced on the workpiece 4 can be adjusted, as will be shown hereinbelow.
It is obvious that the second spindle head can also be pro-vided with a si~ilar mechanism.
As shown in Fig. 1, the outer eccentrics 9, 11 have cam surfaces 35, 36 on the external surface, having an elevation in the direction perpendicular to the plane of the working " table 3. The platform 5 has carriers 37, 38 (39~ secured .i thereon for interacting with the cam surfaces 35, 36 (Fi~s.
. 20 1, 4). In the particular case (Fig. 4), instead of the cam` surface in the outer eccentric 9, 11 an annular slot 40 can be made without the cam elevation, interacting with a carri-er 39 arranged in a threaded openin~ 41 provided in the platform 5. As shown in Fig. 4, the outer eccentrics 9, 11 may have simultaneously both the cam surfaces 35, 36 and the annular slots 40. With the provision of the cam surfaces 35, 36, rotation of the outer eccentrics 9, 11 leads to vertical displacenents of the carriers 37, 38 and to vertical move-ments of the platform S.
As shown in Figs. 1, 3, thc carriers 37, .,8 are ri~idly ; fixed in wor~ wheels 1~, 43, mounted for joint novement with the platform and rotatably with respect to it. A shaft 44 is mounted rotatably in the platform 5. On said shaft 44 worms 45, 46 are rigidly secured (or cut). These worms 45, 46 are in engagement with the worm wheels 42, 43. Rotation of the shaft 44 brings about rotation of the worm wheels 42, 43 re-lative to the outer eccentrics ~, 11 and leads to a ch~nge in the position oE the carriers 37, 38 r~-lative to th~ cam surfaces 35, 36, for changin~ the ph~se ef vertica' traiel of the platform 5 relative to the r~orking table 3. In the ~ 5 embodiment shown in Fig. 4 resetting of the carri r into - openings 41a, 41b ensures a change in th~ phase of vertical travel of the platform 5 in relation of the working table 3.
The result of such change in the Phase of vertical t~ravel of the Platform 5 ~ill be shown hereinbelow.
As shown in Fig. 1, the working table 3 is driven by a rack-and-pinion mechanism, comprising two toothed racks 47, 48 attached to the idle surface of the working table 3 and disposed parallel to the path of travel of the table 3 or to the axis 0-0 (Fig. 3). The toothed racks are in engagement with pinions ~9, 50 mounted on the hori~ontal shaft 18 link-ed uith the drive 2 of the machine, as described herein-above. The working table 3 is mounted on the bed l with the help of guide rollers 51, 52. With such a design of the .' drive the working table performs rectilinear motion with resPect to the bed 1. Thereby, a recurring pattern is pro-duced on the workpiece 4, Rith a period ~repeat) depending ; on the rate of rectilinear motion of the working table 3.
The spindle head 6 (Fig. 1) is provided with a device for adjusting its position with respect to the link (25, 26), this device being, for example, a carria~e 53 with stops 54. Furthermore, the spindle head 6 is provided with a chuck 55 for securing a working tool 56, for example, a mil-ling cutter for machining tHe workpiece 4.
: The above-described milling machine operates in the following manner.
; Before the machine operation is started, the milling cutter S6 is set on a required height and the spindle head 6 is brought to the required position by resetting the car-riage 53 on the link 25 and by fixing it with the stops 54.
Once the drive 2 is switched on, the table 3 executes a lon--: :: .
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gitudinal translation or reciprocating ~otion through the rack-and-pinion mechanism 47-S0 ~clefined by the design of the reduction gear 13 or b~ the drive control s-~stem, which is not shownj. The wor~piece 4 sxecutes a longitudinal motion.
Rotation of the shaft 18 causes rotation of the inner eccentrics 8, 10, which transmit rotation to the outer ec-centrics 9, 11 through the worm-and-worm gears 20, 22 and 21, 23. The platfor~ 5 executes a oircular motion relative to the table 3, if the sums of the eccentricities of the eccentrics 8, 9 and 10, 11 are not e~ual to zero. It is clear that the working tool 56 of each spindle head 6 also performs similar circular motions.
- The carrier 29 linked with the inner eccentric 9 by the worm-and-worm gear 31, 3~, brings the crank 33 in rotation.
The latter causes reciprocation of the link 25 and, together therewith, reciprocation of the spindle head 6 in relation to the platform 5. Thus, in the general case the spindle head 6 executes a circular ~otion with respect to the work-ing table 3 together with the platform 5 and a reciprocating motion with respect to the platform 5 and the working table 3.
If the outer eccentrics are provided with the annular slot 40 (Fig. 4), the platform 5 does not perform vertical motions. If the outer eccentrics are Provided wïth the cam surface 35, 36 and the carrier 39 is set in one of the openings 41a, 41b (Fig. 4) or if the carriers 37, 38 interact with the cam surfaces 35, 36, the platform 5 recip-rocates vertically with respect to the working table 3 together with the spindle heads 6. This brings about changes in the depth of the pattern relief produced bY the milling cutter 56 in the workpiece 4.
From the above description it is apparent that the platform 5 carrying the spindle heads 6 performs circular 3S and reciProcating motions relative to the working table 3 and that the spindle head 6 Performs reciprocating motion 2~7~G60 lO
relative to the platform 5 and the aorking ta~!e 3. It is obvious that both spin,ile heads ~ can be provided with ~
mechanis~ for reciprocating motion. All said motions are realized purely mechanically owin~ to the mechanisms 7.
For a better understanding of the operation of the mechanism 7 and for illustrating the potentialities of the milling machine of the invention, a description of some ad-justments in setting said machine is given hereinbeloa.
As shoun in Fig. 5, the total eccentricity of the ec-centrics 8, 10, adiusted by the worm-and-worm gear 20, 22, is equal to zero, the radius of the crank 33, adjusted bY
the screa 34, is equal to zero, and the phase of the crank 33, adjusted by the worm-and-worm gear 31, 32, is equal to zero. In this case, as shown in Fig. 6,-a~dot 57 is produced on the workpiece 4, if the aorking table 3 is stationary, and/or a longitudinal straight line 58 is produced .-,n the; aorkpiece ', if the wori;ing table 3 is in motion.
As shown in Fig. 7, the total eccentricity of the ec-centrics 8, 10, adjusted by the worm-and-worm gear 20, 22, is equal to zero, the radius of the crank 33, adjusted by the screw 34, is maximum, the phase of the crank 33, adiust-ed by the aorm-and-worm gear 31, 32, is equal to zero. In this case, as shown in Fig. 8, a transverse straight line 59 ~ . is produced on the workpiece 4, if the uorking table 3 is : 25 stationary, whereas a sinusoid 60 is produced on the work-piece 4, if the working table 3 is in motion.
As shoan in Fig. 9, the total eccentricity of the ec-centrics 8, 10, adiusted by`the worm-and-worm gear 20, 22, is maximu~, the radius of the crank 33, adjusted by the screu 34, is equal to zero, and the Phase of the crank 33, : adjusted by the worm-and-worm gear 31, 32, is equal to zero.
- In this case, as shown in Fig. 10, a circumference 61 is - produced on the workpiece 4, if the working table 3 is sta-tionary, whereas a longitudinal cycloid-like line 62 is pro-duced on the workpiece 4, if the working table 3 is in motion.
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' As shown in Fig. 11, the total eccentricity of the ec-centrics 8, 10, adjusted by the ~orm-and-worm gear 20, 22, is maximum, the radius of the crank 33, adjusted by the screw 34, is equal to zero, and the phase of the crank 33, S adjusted by the worm-and-worm gear 31, 32, is egual to zero.
In this case, as showr. in Fig. 12, an ellipse 63 with the transversely disposed major diameter is Produced on the aorkpiece 4, if the working table 3 is stationary, whereas a longitudinal periodic parabola 64 is produced on the work-piece 4, if the working table 3 is in motion.
As shown in Fig. 13, the total eccentricity of the ec-centrics 8, 10, adjusted by the ~orm-and-~orm gear 20, 22, is maximum, the radius of the crank 33, adjusted by the screw 34,-is equal to zero, and the phase of the crank 33, adjusted by the worm-and-worm gear 31, 32, is equal to 180~.
In this case, as sho~n in Fig. 14, an ellipse 85 ~ith the longitudinally disposed major diameter is produced on the workpiece 4, if the working table 3 is stationary, whereas a longitudinal cycloid-like line 66 is produced on the work-` 20 piece 4, if the working table 3 is in motion.
As shown in Fig. 15, the total eccentricity of the ec-centrics 8, 10, adjusted by the worm-and-worm gear 20, 22, is maximum, the radius of the crank 33, adjusted by the screw 34, is maximum, and the phase of the crank 33, adiusted by the worm-and-worm gear 31, 32, is equal to 270. In this case, as shown in Fig. 16, an ellipse 67 with inclined maior diameter is produced on the workpiece 4, if the working table 3 is stationary, whereas a longitudinal periodic para-bola 68 with the pattern element inclined in the same direc-tion is produced on the workpiece 4, if the working table 3 is in motion.
-~ As shown in Fig. 17, the total eccentricity of the ec-centrics 8, 10, adjusted by the worm-and-worm gear 20, 22, : 35 is maximum, the radius of the crank 33, adiusted by the screw 3~, is maximum, and the phase of the crank 33, adjust-' ' ' 20766~0 12 ed by the worm-and-worm gear 31, 32, is equal to 90. In this case, as shown in Fig. 18, an ellipse 69 with inclined major diameter is produced on the r~orkpiece 4, iE the work-ing table 3 is stationary, whereas a longitudinal Periodic parabola 70 with the pattern elements inclined in the same direction is produced on the workpiece 4, if the working table 3 is in motion. The inclination of the ellipse and of the elements of the periodic parabola in the present case is opposite to that shown in Fig. 16.
; 10 As shown in Fig. 19, adiustments of the mechanism 7 correspond to those shown in Fig. 7, and, with the working table 3 in motion, a sinusoid 71 is produced (Fig. 20). In this version the cam surfaces 35, 36 and the carriers 37, 38 - -- participate in the work, as a-result of which the depth of the pattern varies and a relief is formed. Version (a) in Eig. 20 is obtained when the phase of setting the carrier 37 (38) is 0 (Fie. 19); version (b) is obtained when the phase of -~etting the carrier 37 (38) is 90 (Fig. 19).
Described hereinabove are versions of the adjustments with the parts of the mechanism 7 in extreme Positions. It is obvious that the possibility of smooth variation of the ~utual positions of these parts in combination with the con-ventional continuous or stepwise control of the speed of the : drive 2 and also in combination with the conventional conti-nuous or stepwise control of feeding the spindle heads pro-vides a possibility of obtaining an infinite variety of pat-terns on the workpiece 4.
From the description given .hereinabove it is obvious that the milling machine according to the invention enables the obtaining o~ most diverse combinations of the working movements of the platform and the spindle heads, whereby an infinite variety of patterns and reliefs can be produced in a purely mechanical way.
Industrial Applicability The present invention may find application in mechanic-al engineerin~ in woodworking, and in other industries for - ,, ' ! .
207666~ 13 producing various slots, gtJoves, reliefs, patt;c!rls, and the like. ~he nain applic~tion of the ~iiling ma hin~ ef the present invention is the producin~ of re~uiari~ repeating - pattern-. .
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Field of the Art The present invention relates to mechanical engineering and more Particu1ar1y to mi11ing machines.
Background of the Invention Well known in the art are milling machines adapted for milling contoured slots and producing intricate and repeat-ing patterns and relie~s. UsuallY each working motion of the table and of the working spindle in such machines is effect-effected with the help o~ an individual comPuter-controlled drive. Such a system re~uires that the machine should be provided with a large number of electric drives and with a sophisticated electronic control system comprising a central ~ processor, -a sensor, and other elements of the automatic control system. This involves an increase in the power con-sumption and weight of the machine, makes the machine serv-- icing more complicated, and adds to the cost of the machine.
~nown in the art is a milling machine comprising a bed, a working table for clamping workpieces thereto, mounted on the bed with the possibility of travel and provided ~ith a drive ensuring its movement relative to the bed; a platform mounted with the possibility of movement relative to the bed and carrying at least one spindle head intended for securing a working tool; and a mechanism for ensuring relative move-ment of the working table and the platform (SU, A, 1511124~.
This machine is noted for a simple desi~n, its working motions are ensured by purely mechanical means from one ' drive. The mechanism for ensuring relative movement of the working table and the platform comprises a pair of eccen-trics, horizontal plates and vertical plates, arranged in ~uides of said horizontal Plates and transmittin~ motion to the platform carrying the spindle heads. This milling ma-' chine is disadvantageous in that it cannot provide curvi-linear Patterns and intricate reliefs, because the working platform and the spindle heads can perform onlY a limited number of working motions. Furthermore, the machine is pro-.
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vided with a cumbersome mechanism for ensuring relative movement of tne working table and the platform. This mech-anism is a source of losses of the drive nechanical energy because of friction experienced by the vertical plates in the guides. This makes the machine inefficient and un-reliable in operation.
Disclosure of the Invention The present invention is directed to the provision of a milling machine, in which a mechanism for ensuring relative movement of its working table and platform is designed so as to secure by purely mechanical means a plurality of differ-ent combinations of the working motions of the machine mem-bers.
- Said object-is accomplished by that in a milling ma-chine comprising a bed, a working table for clanping work-pieces, mounted on the bed with the possibility of travel and provided with a drive ensuring its movement relative to the bed; a platform mounted with the possibility of travel relative to the bed and carrying at least one spindle head intended for securing a working tool; and a mechanism for ensuring relative movement of the working table and the platfor~, according to the invention, the mechanism for en-suring relative movement of the working table and the plat-form is made in the form of at least two pairs of eccentrics .
disPosed on both sides in relation to the path of travel of the working table, one of the eccentrics of each pair, name-ly, the inner eccentric, being disposed inside the other, outer eccentric, which is mounted on the platform carrying the spindle head with the possibilitY of rotation and fixing its Position relative to the outer eccentric and is kinema-tically linked with the drive ensuring the motion of the working table relative to the bed. The spindle head is mounted with the possibility of travel relative to the plat-form and is provided with a drive for ensuring its movement relative to the platform, said mechanism being kinematically linked with one of the eccentrics.
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207~6~
Such an arrangement ensures an infinite variety of com-binations of the eccentricities of the two eccentrics; this - feature allows anY versions of a repeating ~eometrical pat-tern to be produced on the surface being worked. In com-bination with the movement of the spindle head, provided by the same drive, an additional infinite variety of pattern versions is ensured; ail the working motions of the machine are effected from one drive with the help of purely mechan-ical means.
The outer eccentrics are Preferably mounted on the platform rotatably and with the possibility of fixing their position relative to the platform. In this case the adjust-ment for varying the co~bination by the eccentricity of the ---- - eccentrics is simplified. --The drive for moving the spindle head relative to the platform preferably comprises a carrier installed on the inner eccentric rotatably and with the possibility of fixing its position relative to the inner eccentric. This provides adjustment of the phase of the spindle head travel.
The outer eccentrics are preferably kinematicallY in-terlinked. This ensures precise adjustment of the eccentri-: city.
Each outer eccentric is Preferably made with an extern-al cam surface having a elevation in the direction perpendi-:- ~5 cular to the plane of the working table, and the platform is provided with a carrier for interacting with said cam sur-face.
~ This ensures additional motion of the platform with the ; spindle heads, effected by the same drive, ~or producing in-tricate surface reliefs.
'~ Each outer eccentric preferably has a worm wheel in-stalled for movin~ together with the platform and rotatably .~ relative to the platform, the carrier being fixed rigidly in : said worm wheel; a shaft is mounted rotatablY in the plat-~orm and has worms fixed rigidly thereon, said worms meshing with said worm wheels. This ensures precise and simultaneous 2076~60 4 adjustment of the phase of the vertical travel of the plat-~orm.
The drive for moving the working table is preferabl-~made as a rack-and-pinion mechanism, comprising at least one rack attached to the workin~ table, the pinion of the rack-and-pinion mechanism is linked kinematically with a pair of shafts, and each inner eccentric is rigidly fixed on one of these shafts. This simplifies the design of the drive mech-anism, minimi~es the consumption of power, and ensures high accuracy of the relative working movements of the machine.
The outer and inner eccentrics of each pair of the ec-centrics are preferably interlinked by means of a uorm-and-worm gear, the worm of each worm-and-worm gear being dispos-ed on the extsrnal eccentric. This ensures simple and pre-cise adjustment of the mutual position of the eccentrics andreliable fixing of the eccentrics after the adiustment.
The spindle head is linked with the carrier by means of an oscillating crank gear with a variable radius of the crank. This provides additional versions of the working movements of the spindle head along with the movements of the platform carrying the spindle head.
Brief Description of Drawings Given hereinbelow is a detailed description of the pre-sent invention, illustrated by the accompanying drawings, in - 25 which:
Fig. 1 is a general view of a milling machine according to the invention, longitudinal section;
Fig. 2 is view A in Fig~. 1 (some units and parts of the machine are conventionally not shown);
Fig. 3 is a section along III-III in Fig. l;
Fig. 4 is a version of the structure of a part of the mechanism for ensurin~ relative travel of the working mecha-nism and the platform, shown in Fig. l;
Figs. 5-20 show different adjustments of the mechanism for ensuring relative travel of the working table and the platform, and the corresponding patterns produced on ma-.
. . : : . - , , :
.
207666~ s chined workpieces; in Figs. 6, 8, 10, 12, 14, 16 and 18 in the upper part of each drawing a pattern is shown with the working table being stationary, whereas in the lower part of the drawing a pattern is shown with the working table in motion.
Preferred Embodi~ents The machine of the invention comprises a bed 1, in the lower part of which a reversing driv~, 2 is installe~, kine-~atically linked with a wor'~ing table 3, ~ounted on the bed l with the possibility of ~oving along a path lengthwise of the longitudinal axis 0-0 of the ~achine ~Fig. 3) and pro-vided with units (not shown) for clamping a workpiece 4. The bed 1 mounts a ~ovable platfor~ 5. The Platform 5 is mounted ~ movably relative to the bed l-and-carries two spindle heads - 15 6. The machine is provided with a mechanism 7 for ensuring relative movement of the working table 3 and the platform 5.
The mechanism 7 has two pairs of eccentrics 8, 9 and 10, 11 ; ~Figs. 1, 3) disposed on both sides of the path of travel ; 0-0 of the working table 3. The inner eccentrics 8 and 10 - 20 are mounted rigidly on vertical shafts 12, 13 which carry on ; their free ends conical gears 14, 15 that are in ~esh with ~ .~
conical gears 16, 17 mounted on a horizontal shaft 18 linked with the drive 2 through a r,eduction gear 19 (which can be a gearbox or a variator).
~ 25 The outer eccentrics 9, 10 are mounted rotatably on the ,; inner eccentrics 8, 10. The outer eccentrics 9, 10 are in-. terlinked with the inner eccentrics 8, 10 through worm-and-worn gears, comPrising worm screws 20, 21 installed rotatab-~: ly in the outer eccentrics 9, 11 and meshing with worm wheels 22, 23 cut on the inner eccentrics 8, 10. With such an arrangement the outer eccentrics 9, 11 can be rotated re-lative to the inner eccentrics 8, 10 for adjustment, and their mutual position after the adjustment can be reliably ~; fixed. It is obvious that other embodiments of the mechanism ; .
''' , .
' - ' ' 2 ~7 ~ 6 for adjusting the mutual position of the outer eccentrics 9, 11 and inner eccentrics 8, 10 are also possible, but the structural embodi~ent describçd hereinabove should ~e pre-~erred. The described structure ensures an~ combinations of the eccentricities of the outer eccentric and the inner ec-centric of each pair, ranging from their alignment, when the total eccentricity is equal to the sum of the eccentricities of the t~o eccentrics, to such a position, ~hen the total eccentricity will be equal to the difference of the eccen-tricities of the two eccentrics (for instance, to zero,when the t~o eccentricities are equal~. In this case the value of the total eccentricitY defines the amplitude of travel of the platform 5.
The spindle heads 6 are movably mounted on the''~platfor'm 15 5 on links 25, 26 disposed in guide openings 27, 28 of the platform 5, and each spindle head 6 is provided with a mech-anism for moving it relative to the platform 5. This mecha-nism is a carrier 29 (30) mounted rotatably on the inner ec-' centric 8 (10) with the possibility of fixing the position of the carrier relative to the inner eccentric. For this to be done, the carrier 29 (30) is provided with a worm screw 31, arran~ed rotatably in the inner eccentric 8 ~10) and meshing with a worm wheel 32 cut in the inner eccentric 8 (10). With such an arrangement the carrier 29 (30) can be rotated relative to the inner eccentric 8 (10) for adjust-ment and their mutual position after the adjustment can be reliably fixed. It is obvious that other embodiments of the mechanism for adjusting the'mutual position of the carrier 29 (30) and the inner eccentric 8 (lO) are also possible, but the structural embodiment described hereinabove should ~; be preferred. With suoh a structure of the mechanism for moving the spindle head 6, the phase of travel of the spin-dle head 6 relative to the platfor~ 5 varies, depending on the angular position of the carrier 29 (30) with respect to the inner eccentric 8 (10), as will be shown hereinbelow.
, - ' . . , , ' ~: ~' - , ,: , ~ ~ , 2076~6~ 7 In the ~iven e~bodi~ent one of the spindle heads 6 is provided with a mechanism for moving it in relation with the platform 5 with a crank 33, installed on the carrier 29 and articulated with the link 25. The crank 33 is ~ounted on the carrier 29 with the aid of an adjusting screw 34 that inter-acts with the internal thread ~not shown) of the crank 33.
The adiusting screw 34 is arranged in the carrier ~9 rota-tably and, in combination with the carrier 29, the crank 33 and the link 25, it makes up an oscillatin~ crank gear with a variable radius of the crank. With such an arrangement the inclination of the elements of the pattern produced on the workpiece 4 can be adjusted, as will be shown hereinbelow.
It is obvious that the second spindle head can also be pro-vided with a si~ilar mechanism.
As shown in Fig. 1, the outer eccentrics 9, 11 have cam surfaces 35, 36 on the external surface, having an elevation in the direction perpendicular to the plane of the working " table 3. The platform 5 has carriers 37, 38 (39~ secured .i thereon for interacting with the cam surfaces 35, 36 (Fi~s.
. 20 1, 4). In the particular case (Fig. 4), instead of the cam` surface in the outer eccentric 9, 11 an annular slot 40 can be made without the cam elevation, interacting with a carri-er 39 arranged in a threaded openin~ 41 provided in the platform 5. As shown in Fig. 4, the outer eccentrics 9, 11 may have simultaneously both the cam surfaces 35, 36 and the annular slots 40. With the provision of the cam surfaces 35, 36, rotation of the outer eccentrics 9, 11 leads to vertical displacenents of the carriers 37, 38 and to vertical move-ments of the platform S.
As shown in Figs. 1, 3, thc carriers 37, .,8 are ri~idly ; fixed in wor~ wheels 1~, 43, mounted for joint novement with the platform and rotatably with respect to it. A shaft 44 is mounted rotatably in the platform 5. On said shaft 44 worms 45, 46 are rigidly secured (or cut). These worms 45, 46 are in engagement with the worm wheels 42, 43. Rotation of the shaft 44 brings about rotation of the worm wheels 42, 43 re-lative to the outer eccentrics ~, 11 and leads to a ch~nge in the position oE the carriers 37, 38 r~-lative to th~ cam surfaces 35, 36, for changin~ the ph~se ef vertica' traiel of the platform 5 relative to the r~orking table 3. In the ~ 5 embodiment shown in Fig. 4 resetting of the carri r into - openings 41a, 41b ensures a change in th~ phase of vertical travel of the platform 5 in relation of the working table 3.
The result of such change in the Phase of vertical t~ravel of the Platform 5 ~ill be shown hereinbelow.
As shown in Fig. 1, the working table 3 is driven by a rack-and-pinion mechanism, comprising two toothed racks 47, 48 attached to the idle surface of the working table 3 and disposed parallel to the path of travel of the table 3 or to the axis 0-0 (Fig. 3). The toothed racks are in engagement with pinions ~9, 50 mounted on the hori~ontal shaft 18 link-ed uith the drive 2 of the machine, as described herein-above. The working table 3 is mounted on the bed l with the help of guide rollers 51, 52. With such a design of the .' drive the working table performs rectilinear motion with resPect to the bed 1. Thereby, a recurring pattern is pro-duced on the workpiece 4, Rith a period ~repeat) depending ; on the rate of rectilinear motion of the working table 3.
The spindle head 6 (Fig. 1) is provided with a device for adjusting its position with respect to the link (25, 26), this device being, for example, a carria~e 53 with stops 54. Furthermore, the spindle head 6 is provided with a chuck 55 for securing a working tool 56, for example, a mil-ling cutter for machining tHe workpiece 4.
: The above-described milling machine operates in the following manner.
; Before the machine operation is started, the milling cutter S6 is set on a required height and the spindle head 6 is brought to the required position by resetting the car-riage 53 on the link 25 and by fixing it with the stops 54.
Once the drive 2 is switched on, the table 3 executes a lon--: :: .
. , ' ' .
207666~
gitudinal translation or reciprocating ~otion through the rack-and-pinion mechanism 47-S0 ~clefined by the design of the reduction gear 13 or b~ the drive control s-~stem, which is not shownj. The wor~piece 4 sxecutes a longitudinal motion.
Rotation of the shaft 18 causes rotation of the inner eccentrics 8, 10, which transmit rotation to the outer ec-centrics 9, 11 through the worm-and-worm gears 20, 22 and 21, 23. The platfor~ 5 executes a oircular motion relative to the table 3, if the sums of the eccentricities of the eccentrics 8, 9 and 10, 11 are not e~ual to zero. It is clear that the working tool 56 of each spindle head 6 also performs similar circular motions.
- The carrier 29 linked with the inner eccentric 9 by the worm-and-worm gear 31, 3~, brings the crank 33 in rotation.
The latter causes reciprocation of the link 25 and, together therewith, reciprocation of the spindle head 6 in relation to the platform 5. Thus, in the general case the spindle head 6 executes a circular ~otion with respect to the work-ing table 3 together with the platform 5 and a reciprocating motion with respect to the platform 5 and the working table 3.
If the outer eccentrics are provided with the annular slot 40 (Fig. 4), the platform 5 does not perform vertical motions. If the outer eccentrics are Provided wïth the cam surface 35, 36 and the carrier 39 is set in one of the openings 41a, 41b (Fig. 4) or if the carriers 37, 38 interact with the cam surfaces 35, 36, the platform 5 recip-rocates vertically with respect to the working table 3 together with the spindle heads 6. This brings about changes in the depth of the pattern relief produced bY the milling cutter 56 in the workpiece 4.
From the above description it is apparent that the platform 5 carrying the spindle heads 6 performs circular 3S and reciProcating motions relative to the working table 3 and that the spindle head 6 Performs reciprocating motion 2~7~G60 lO
relative to the platform 5 and the aorking ta~!e 3. It is obvious that both spin,ile heads ~ can be provided with ~
mechanis~ for reciprocating motion. All said motions are realized purely mechanically owin~ to the mechanisms 7.
For a better understanding of the operation of the mechanism 7 and for illustrating the potentialities of the milling machine of the invention, a description of some ad-justments in setting said machine is given hereinbeloa.
As shoun in Fig. 5, the total eccentricity of the ec-centrics 8, 10, adiusted by the worm-and-worm gear 20, 22, is equal to zero, the radius of the crank 33, adjusted bY
the screa 34, is equal to zero, and the phase of the crank 33, adjusted by the worm-and-worm gear 31, 32, is equal to zero. In this case, as shown in Fig. 6,-a~dot 57 is produced on the workpiece 4, if the aorking table 3 is stationary, and/or a longitudinal straight line 58 is produced .-,n the; aorkpiece ', if the wori;ing table 3 is in motion.
As shown in Fig. 7, the total eccentricity of the ec-centrics 8, 10, adjusted by the worm-and-worm gear 20, 22, is equal to zero, the radius of the crank 33, adjusted by the screw 34, is maximum, the phase of the crank 33, adiust-ed by the aorm-and-worm gear 31, 32, is equal to zero. In this case, as shown in Fig. 8, a transverse straight line 59 ~ . is produced on the workpiece 4, if the uorking table 3 is : 25 stationary, whereas a sinusoid 60 is produced on the work-piece 4, if the working table 3 is in motion.
As shoan in Fig. 9, the total eccentricity of the ec-centrics 8, 10, adiusted by`the worm-and-worm gear 20, 22, is maximu~, the radius of the crank 33, adjusted by the screu 34, is equal to zero, and the Phase of the crank 33, : adjusted by the worm-and-worm gear 31, 32, is equal to zero.
- In this case, as shown in Fig. 10, a circumference 61 is - produced on the workpiece 4, if the working table 3 is sta-tionary, whereas a longitudinal cycloid-like line 62 is pro-duced on the workpiece 4, if the working table 3 is in motion.
.
- ~
., ~ ,.
' As shown in Fig. 11, the total eccentricity of the ec-centrics 8, 10, adjusted by the ~orm-and-worm gear 20, 22, is maximum, the radius of the crank 33, adjusted by the screw 34, is equal to zero, and the phase of the crank 33, S adjusted by the worm-and-worm gear 31, 32, is egual to zero.
In this case, as showr. in Fig. 12, an ellipse 63 with the transversely disposed major diameter is Produced on the aorkpiece 4, if the working table 3 is stationary, whereas a longitudinal periodic parabola 64 is produced on the work-piece 4, if the working table 3 is in motion.
As shown in Fig. 13, the total eccentricity of the ec-centrics 8, 10, adjusted by the ~orm-and-~orm gear 20, 22, is maximum, the radius of the crank 33, adjusted by the screw 34,-is equal to zero, and the phase of the crank 33, adjusted by the worm-and-worm gear 31, 32, is equal to 180~.
In this case, as sho~n in Fig. 14, an ellipse 85 ~ith the longitudinally disposed major diameter is produced on the workpiece 4, if the working table 3 is stationary, whereas a longitudinal cycloid-like line 66 is produced on the work-` 20 piece 4, if the working table 3 is in motion.
As shown in Fig. 15, the total eccentricity of the ec-centrics 8, 10, adjusted by the worm-and-worm gear 20, 22, is maximum, the radius of the crank 33, adjusted by the screw 34, is maximum, and the phase of the crank 33, adiusted by the worm-and-worm gear 31, 32, is equal to 270. In this case, as shown in Fig. 16, an ellipse 67 with inclined maior diameter is produced on the workpiece 4, if the working table 3 is stationary, whereas a longitudinal periodic para-bola 68 with the pattern element inclined in the same direc-tion is produced on the workpiece 4, if the working table 3 is in motion.
-~ As shown in Fig. 17, the total eccentricity of the ec-centrics 8, 10, adjusted by the worm-and-worm gear 20, 22, : 35 is maximum, the radius of the crank 33, adiusted by the screw 3~, is maximum, and the phase of the crank 33, adjust-' ' ' 20766~0 12 ed by the worm-and-worm gear 31, 32, is equal to 90. In this case, as shown in Fig. 18, an ellipse 69 with inclined major diameter is produced on the r~orkpiece 4, iE the work-ing table 3 is stationary, whereas a longitudinal Periodic parabola 70 with the pattern elements inclined in the same direction is produced on the workpiece 4, if the working table 3 is in motion. The inclination of the ellipse and of the elements of the periodic parabola in the present case is opposite to that shown in Fig. 16.
; 10 As shown in Fig. 19, adiustments of the mechanism 7 correspond to those shown in Fig. 7, and, with the working table 3 in motion, a sinusoid 71 is produced (Fig. 20). In this version the cam surfaces 35, 36 and the carriers 37, 38 - -- participate in the work, as a-result of which the depth of the pattern varies and a relief is formed. Version (a) in Eig. 20 is obtained when the phase of setting the carrier 37 (38) is 0 (Fie. 19); version (b) is obtained when the phase of -~etting the carrier 37 (38) is 90 (Fig. 19).
Described hereinabove are versions of the adjustments with the parts of the mechanism 7 in extreme Positions. It is obvious that the possibility of smooth variation of the ~utual positions of these parts in combination with the con-ventional continuous or stepwise control of the speed of the : drive 2 and also in combination with the conventional conti-nuous or stepwise control of feeding the spindle heads pro-vides a possibility of obtaining an infinite variety of pat-terns on the workpiece 4.
From the description given .hereinabove it is obvious that the milling machine according to the invention enables the obtaining o~ most diverse combinations of the working movements of the platform and the spindle heads, whereby an infinite variety of patterns and reliefs can be produced in a purely mechanical way.
Industrial Applicability The present invention may find application in mechanic-al engineerin~ in woodworking, and in other industries for - ,, ' ! .
207666~ 13 producing various slots, gtJoves, reliefs, patt;c!rls, and the like. ~he nain applic~tion of the ~iiling ma hin~ ef the present invention is the producin~ of re~uiari~ repeating - pattern-. .
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Claims (10)
1. A milling machine comprising a bed (1), a working table (3) for clamping workpieces (4) thereto, movably mounted on the bed and provided with a drive (2) for moving said table relative to the bed (1); a platform (5) mounted movably relative to the bed (1) and carrying at least one spindle head (6) intended for fixing a working tool (56);
and a mechanism (7) for ensuring relative travel of the working table (3) and the platform (5), c h a r a c t e r -i z e d in that the mechanism (7) for ensuring relative travel of the working table (3) and the platform (5) com-prises at least two pairs of eccentrics (8, 10; 8, 11) dis-posed on both sides relative to the path (0-0) of travel of the working table (3), one of the eccentrics, the inner ec-centric (8, 10) of each pair being disposed inside the other, outer eccentric (8, 11), mounted in the platform (5) carrying the spindle head (6), with the possibility of rota-tion and fixing the position of said inner eccentric relat-ive to the outer eccentric (8, 11) and kinematically linked with the drive (2) for moving the working table (3) relative to the bed (1).
and a mechanism (7) for ensuring relative travel of the working table (3) and the platform (5), c h a r a c t e r -i z e d in that the mechanism (7) for ensuring relative travel of the working table (3) and the platform (5) com-prises at least two pairs of eccentrics (8, 10; 8, 11) dis-posed on both sides relative to the path (0-0) of travel of the working table (3), one of the eccentrics, the inner ec-centric (8, 10) of each pair being disposed inside the other, outer eccentric (8, 11), mounted in the platform (5) carrying the spindle head (6), with the possibility of rota-tion and fixing the position of said inner eccentric relat-ive to the outer eccentric (8, 11) and kinematically linked with the drive (2) for moving the working table (3) relative to the bed (1).
2. A machine according to Claim 1, c h a r a c t e r -i z e d in that the outer eccentrics (8, 11) are mounted in the platform (5) with the possibility of rotation and fixing their position relative to the platform (5).
3. A machine according to Claims 1,2, c h a r a c -t e r i z e d in that the outer eccentrics (9, 11) are ki-nematically interlinked.
4. A machine according to Claims 1-3, c h a r a c -t e r i z e d in that each outer eccentric (9, 11) is pro-vided with an external cam surface (35, 36) having an eleva-tion in the direction perpendicular to the plane of the working table (3) and in that the platform (5) is provided with a carrier (37, 38) secured thereon, serving for inter-action with said cam surface (35, 36).
5. A machine according to claims 1-4, c h a r a c -t e r i z e d in that each outer eccentric (9, 11) is pro-vided with a worm wheel (42, 43), mounted for moving toge-ther with the platform (5) and rotatably with respect to the platform (5) and in that the carrier (37, 38) is rigidly se-cured in said worm wheel (42, 43), a shaft (44) being rota-tably mounted in the platform (5), said shaft carrying worms (45, 46) rigidly secured thereon, said worms meshing with said worm wheels (42, 43).
6. A machine according to Claims 1-5, c h a r a c -t e r i z e d in that the drive (4) for moving the working table is made as a rack-and-pinion mechanism comprising at least one rack (47, 48) attached to the working table (3), pinion (49, 50) of the rack-and-pinion mechanism being kine-matically linked with a pair of shafts (12, 13), and each inner eccentric (8, 10) is rigidly secured on one of these shafts (12, 13).
7. A machine according to Claims 1-6, c h a r a c -t e r i z e d in that the outer and inner eccentrics (8, 9;
10, 11) of each pair of eccentrics are interlinked by means of a worm-and-worm gear (20, 22; 21, 23), the worm (20, 21) of each worm-and-worm gear being disposed in the outer eccentric (9, 11).
10, 11) of each pair of eccentrics are interlinked by means of a worm-and-worm gear (20, 22; 21, 23), the worm (20, 21) of each worm-and-worm gear being disposed in the outer eccentric (9, 11).
8. A machine according to Claims 1-7, c h a r a c -t e r i z e d in that the spindle head (6) is mounted with a possibility of travel relative to the platform (5) in the direction perpendicular to the path (0-0) of travel of the working table and is provided with a mechanism (29, 33, 25) for moving thereof with respect to the platform (5), said mechanism being kinematically linked with one of the eccen-trics (8).
9. A machine according to Claim 8, c h a r a c t e r -i z e d in that the mechanism for moving the spindle head (6) relative to the platform (5) comprises a carrier (29) installed on the inner eccentric (8) with the possibility of rotation and fixing its position with respect to the inner eccentric (8).
10. A machine according to Claim 9, c h a r a c t e r -i z e d in that the carrier (29) is linked with the spindle head (6) by means of an oscillating crank gear (33, 25), with a variable radius of the crank (33).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SU4891694 | 1990-12-27 | ||
| SU4891694 | 1990-12-27 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2076660A1 true CA2076660A1 (en) | 1992-06-28 |
Family
ID=21550468
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2076660 Abandoned CA2076660A1 (en) | 1990-12-27 | 1991-11-26 | Milling machine |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP0516865A4 (en) |
| CA (1) | CA2076660A1 (en) |
| WO (1) | WO1992011965A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| NL9202257A (en) * | 1992-12-24 | 1994-07-18 | Cederroth Bv | Apparatus and method for cutting a strip of plaster material. |
| CN101791810B (en) * | 2010-03-31 | 2012-06-13 | 深圳华中数控有限公司 | Polar coordinate numerical control woodworking basket milling machine |
| CN105774356B (en) * | 2016-04-27 | 2017-11-14 | 湖州南浔双林振森实木加工厂 | The engraving machine of stair pin |
| CN111532067A (en) * | 2020-06-06 | 2020-08-14 | 刘立超 | Portable on-site carving device |
| CN111572255A (en) * | 2020-06-06 | 2020-08-25 | 刘立超 | Decorative pattern engraving device |
| CN111605345A (en) * | 2020-06-06 | 2020-09-01 | 刘立超 | Building materials edge carving device |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE135918C (en) * | ||||
| US3946774A (en) * | 1974-10-17 | 1976-03-30 | Vermont American Corporation | Device for employing a motorized hand tool to cut a spiralled groove in a workpiece |
| SU1013129A1 (en) * | 1982-01-27 | 1983-04-23 | Херсонский Индустриальный Институт | Machine for milling curvilinear surfaces |
| IT1192902B (en) * | 1982-09-20 | 1988-05-26 | Vacom Srl | MACHINE FOR SHAPING (MODANARE) PIECES OF WOOD ARCHED SHAPE |
| IT8354060V0 (en) * | 1983-12-20 | 1983-12-20 | Nuova Scolpitrice | MULTIPLE WOOD CARVING MACHINE |
| US4787430A (en) * | 1987-02-23 | 1988-11-29 | Ryobi Ltd. | Duplicating router |
| DE8912970U1 (en) * | 1989-11-02 | 1991-02-28 | Ley, Hans, 5203 Much | Cage ring for guiding the rolling elements in the rolling bearing |
-
1991
- 1991-11-26 CA CA 2076660 patent/CA2076660A1/en not_active Abandoned
- 1991-11-26 EP EP19920903355 patent/EP0516865A4/en not_active Ceased
- 1991-11-26 WO PCT/SU1991/000249 patent/WO1992011965A1/en not_active Application Discontinuation
Also Published As
| Publication number | Publication date |
|---|---|
| EP0516865A1 (en) | 1992-12-09 |
| EP0516865A4 (en) | 1993-06-30 |
| WO1992011965A1 (en) | 1992-07-23 |
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