FI72452C - RAMSAOG. - Google Patents

Description

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Patent 03 CG 1337 (51) Kv.lk.4 / lnt.CI.4 B 27 B 3/12 FINLAND —FINLAND (21) Patent application - Patentansökning 772008 (22) Application date - Ansökningsdag 28.06.77 (23) Starting date - Giltighetsdag 28.06 .77 (41) Made public - Blivit offentlig 1 4.1 1.78

National Board of Patents and Registration Date of publication and publication - 27 02 87

Patent and registration authorities '' Ansökan utlagd och utl.skriften publicerad '' (86) Kv. application - Int. ansökan (32) (33) (31) Privilege claimed - Begärd priority 13-05.77

Germany 1i i ttotasavalta-Förbundsrepubliken Tyskland (DE) P 2721842.4 (71) Maschinenfabrik Esterer Aktiengesel1schaft, Postfach 100, Altötting / -Obb. Förbundsrepubliken Tyskland (DE) (74) Leitzinger Oy (5 * 0 Circular saw - Ramsig

The invention relates to a circular saw having a sawtooth moving up and down in a circumferential frame, driven by at least one rotary rod which at its upper end is guided in a controlled manner to a saw frame pin and at its lower end to a crankshaft palm pin or the like. a device for balancing oscillating circumferential masses, the device consisting of first compensating weights arranged directly on the crankshaft at both ends thereof and second compensating weights rotating about axes of rotation parallel to the crankshaft at the same average speed as the crankshaft and in opposite directions to the first the product of the orbital diameter of the first compensating weights is approximately of the same order of magnitude as the corresponding product of the second compensating weights and the first and second compensating weights are so large and arranged with respect to each other such that the resulting mass forces they produce are approximately equal to the first order mass forces of the oscillating circumferential portions of the saw frame in the direction of the cutting impact 2 72452, but in opposite directions.

In known circular saws of the type described above, the mass compensating device is made as a separate structural group from the crank drive, which is mounted on the circumferential side, primarily on both sides, on the circumferential base and driven by a crank mechanism, for example by means of a crankshaft transmission with a crank actuator.

Known structures in which a flexible coupling is primarily used in the coupling between the crank drive and the mass equalization device are ideally suited for retrofitting and in-use circular saws that stress their environment with excessive base vibrations without being able to eliminate them from cadres. In these, a barrier line of forces passes between the vibration-generating mass forces, which mostly travel from the crank mechanism to the circumferential frame and from there to the base, and between the compensating forces of the mass equalizer acting against these mass forces via the base, which is therefore considerably stressed.

Until now, the newly installed rings have also been equipped with a mass equalizer according to the structure described above. However, due to the cooperation between the circumference and the mass equalizer via the circumferential base, in such a case the latter had to be constructed relatively strong, respectively.

A pre-publication of a printed product (Holzzentralblatt Vol. 1971, Booklet 1, page 1581) has already proposed to perform force equalization directly in the actual circumference and precisely by arranging a single second compensating weight In this case, the oscillating forces of the oscillating circumferential portions and the forces exiting the mass equalizer act directly through the crankshaft 3 72452 against each other and thus cannot reach the stand.

The proposal described above is not at all feasible at a reasonable cost because of the high forces that would have to be controlled by a single rotating shaft, namely the crankshaft, which would guarantee the necessary service life and the required safety for the mass equalizer.

The object of the invention is to provide a circular saw of the type mentioned in the introduction, in which the compensating mass forces are transmitted in the saw itself, i.e. without involving the base in the force circuit, without the need for unprofitable construction costs in relation to known circumferences of tried and tested there is a certainty that the synchronized flow of the mass equalizer and the compensating circumferential forces remains unchanged.

According to the invention, the object is solved in such a way that the crankshaft is mounted in a manner known per se on the lower part of the saw, which forms a movable structural unit and can be mounted on a flat horizontal base surface and is torsionally rigid which, viewed in the direction of the wood feed, are at the front and rear of the crankshaft and arranged at approximately the same height and substantially symmetrically with it at the bottom and each supporting a second compensating weight in the same direction as the direction of rotation of the opposite crankshaft, and that the product of weight and diameter in the individual first and second sa compensating weights correspond approximately to a fourth of the result of the estimated weight of the circumferential portions oscillating in the direction of the cutting impact of the saw ring and the circumferential diameter of the palm, and that the crankshaft and main compensating shafts are mounted on common lower side wall portions.

4,72452

In the circumferential sawing machine according to the invention, vibrating mass-generating mass forces and their compensating mass equalization forces are applied against each other in a massive base structure, these forces being applied to a total of three axes, namely a which are simply mounted on the substructure and can therefore, without difficulty, be placed against each other in such a way that these are only massive but structurally simple transmission elements.

In known circular saws of the structure described in the introduction, as well as in circular saws of the same type but without a mass equalizer, it is customary to bear a circumferential drive consisting of side-mounted flywheels and palm pins on a so-called washer through that it is cast on a substrate. Only after this can the circumferential drive be mounted on the base plate using halved bearing housings, in which case the crankshaft bearings can also be mounted on the shaft only at the installation site. Only when this installation has been completed can the sawmill, which is largely pre-assembled at the manufacturing plant, be mounted on the base plate on a perimeter drive. In this case, in addition, only the training of the guides on both sides of the perimeter pushers and the guide slides on the sawtooth, which can be carried out by thoroughly trained and experienced personnel, can be carried out. Installation at the sawmill site has so far taken a few weeks.

Also in relation to the above-mentioned, skill-intensive and time-consuming installation work of known circular sawing machines, which was supplemented by separate installations on both sides of the mass equalizers, the above-mentioned identification marks according to the invention offer considerable advantages. These are created in such a way that the Circular Saw according to the invention can be completely assembled at the factory and tested to verify the correct installation of all components, since no significant vibration-generating forces are generated from the assembled circular saw and can therefore only be started with a conventionally reinforced saw. the saw can be divided into two, better than a fully assembled Circular Saw, suitable transport groups of suitable length for transport, so that the adjustments made to the critical components remain essentially permanent. The two groups of structures are, firstly, the lower part with its crankshafts, the main compensating axes and the first and second compensating weights pre-assembled and, secondly, the end-assembled machine part to be mounted on the lower part. In this case, even the circumferential beam to which the crank drive is connected by the pusher and the pusher in a fully assembled state can remain in the lower part, for which only the lateral circumferential body parts need to be made so that the circumferential beam integrated with the pushers can be removed from the lateral body parts. It takes only a few days to install both assembly groups on which the Circular Saw according to the invention has been dismantled for transport to the installation site. This is a considerable advantage, as the long installation time or only the replacement of an exhausted circular saw with a new one results in significant losses due to production losses due to either delayed commissioning or long downtime, which are now avoidable in the circular saws according to the invention.

In a further development of the invention, it is assumed that the main compensating shafts at the same height are arranged slightly lower than the crankshaft in the substructure, the height difference between the crankshaft and the main compensating shafts being selected so that the dripping moment generated compensates as much as possible. Namely, the difference in height creates a tilting moment in the lower part, which acts against the dripping moment caused by each mass part of the pusher in the lower part and which can be taken purely horizontally oscillating (approximately equal part of the working mass can be taken purely rotating).

6 72452

In one structure of the invention, it is required that the second-order mass forces generated by the circumferential parts oscillating in the cutting direction of the saw ring are compensated in the lower part. This is done by means of two additional compensating shafts which are mounted at the bottom parallel to the crankshaft as well as symmetrically about a vertical plane passing through its center line and which are operated at twice the crankshaft in the opposite direction and support input GD, producing that the third-order compensating weights compensate for these second-order mass forces. The reason for the second-order mass forces is known to be that the sawtooth stroke lengths associated with the upper crankcase half on the one hand and the lower crankcase half on the other hand are different, with this difference increasing as the length of the pusher decreases. This difference manifests itself in a sinusoidal oscillation associated with the fundamental oscillation of the saw ring and having a double frequency in this respect.

The further development of the invention finally relates to a basic superstructure according to the invention in circular saws provided with a pendulum frame, wherein the additional horizontal oscillating movement of the saw ring is selected so that the local curve of the individual saw teeth coincides approximately parallel to Such pendulum frames, by means of frame guides, cause horizontal mass forces at a predetermined distance above the lower part of the circumferential frame, which, as well as the above-mentioned second-order mass forces, manifest as oscillations a weight 90 ° ahead of the respective third of the two additional compensating axes and 90 ° behind the second additional compensating axis. These fourth compensating weights produce not only a linear compensating vibration in the horizontal direction, but also a horizontal tilting moment of 7 72452 due to the distance of the additional compensating axes, which can be advantageously exploited of the fourth compensating weights can be applied at least in part.

Understandably, the third compensating weights and the fourth compensating * weights can in each case be combined into a single compensating weight, which in practice occurs so that the positions through which the opposite weights rotate simultaneously on the second or second additional compensating axis no longer correspond to 6 o'clock or 12 o'clock or 3 or 9 o'clock stations.

If the above-mentioned tipping moment generated at the bottom of the fourth compensating weights in individual cases were not desirable, it could easily be avoided so that only one of the two additional compensating axes is used for the fourth compensating weight and the second fourth compensating weight is placed on the additional compensating shaft running parallel to it. In this case, the fourth compensating weights produce a purely linear, horizontal compensating oscillation.

Both of the above modifications are described in more detail in the claims for the fourth compensating weights.

The drawing shows a structural model of the invention. It presents:

Figure 1 shows the lower part - very schematically - of the lower part of the circumferential frame with its pusher seen from the side, i.e. in a direction perpendicular to the direction of feeding of the wood;

Figure 2 is a cross-sectional view of the saw machine of Figure 1 taken along section line II-II in Figure 1; 8 72452

Fig. 3 shows the view according to Fig. 2, in which, however, the drive elements for transferring the driving force from the drive crank pins to the individual compensating shafts and the compensating weights are also shown;

Figure 4 is a cross-sectional view of the machine of Figure 3 taken along section line IV-IV in Figure 3.

The circular sawing machines shown in Figures 1-4 show an upper circumferential frame 1 (only the lower part is shown in Figures 1 and 2), in which the saw frame 2 is guided up and down in a known manner by means of guides and guide slides not shown. The saw machine structures according to Figures 1-4 have two pushers (rotating rods) 3 for moving the saw frame up and down, one of which grips the lower circumference on one side of the beam 2a and the other on the other side, which beam is provided with side circumferential pins 4 for this purpose. is mounted by means of rolling bearings 5. The lower circumferential beam 2a is bonded with the upper circumferential beam (not shown) to a rigid whole, to which the saw blades are tensioned by means of circumferential columns 2b running parallel to the saw blades also not shown.

The arrow 6 in Figures 1 and 2 show the saw frame 2 and the cutting blow direction of the arrow 7 in Figure 1 showing the feed direction of the wood.

Figures 1 and 2 are also displayed in the lower delivery rolls 8, which together with the upper feed rollers unrecited move the wood to be cut through in the direction of the arrow 7 the sawing machine.

The saw platform is marked with the number 9 in Figure 1.

The upper circumferential frame 1 is placed on a rigid lower part and fixed by means of screws with adapter surfaces or the like to a defined relative position. The lower part 10 rests on a flat washer 11, the strength of which should be substantially only as high as the static load caused by the circular saw machine with its lower parts requires.

The lower part consists of front-facing, vertical vertical columns 12 in each of two parallel horizontal longitudinal 13, parallel to each other, parallel to each other, parallel to each other, parallel to each other, parallel to each other, parallel to each other, parallel to each other, parallel to each other. two rear vertical pillars 15 corresponding to the two front upright pillars 12 »an upper front cross member 16 connecting the longitudinal beams 13 and the upright pillars 12; 18, which interconnects the lower longitudinal beams 14 and the front uprights 12 and the rear lower cross member 19, which interconnects the lower the longitudinal beams 14 and the lower vertical columns 15. The lower part 10 further comprises longitudinal, lateral mounting walls forming vertical steel plates 200, which are in each case mounted between the front vertical column 12 and the rearmost column 15 on the same side of the machine. The steel plates 20 do not extend the full height between the upper edge of the lower longitudinal beam 14 and the lower edge of the upper longitudinal beam n 13.

The vertical columns 12, 15, the longitudinal beams 13, 14, the cross beams 16, 17, 18, 19 and the steel plates 20 are welded to each other and also form a self-rigid base loaded by a relatively heavy circumferential frame 1 and other associated machine parts.

The circular sawing machine according to Figures 1 to 4 shows a vertical plane E 1 which is vertical, longitudinally running and thus parallel to the drawing plane of Figure 1, and a vertical plane Eq which is transverse and accordingly parallel to the image plane of Figure 2. These levels arise approximately in the basic superstructure of the perimeter chipper - with the exception of the gearbox, which will be described later and shown in Figures 3 and 4, to provide a drive connection from the crank to the compensating stacks still to be described,

In the polar plane, the central plane Eq has bores 21 in both steel plates 20 in the same horizontal direction, which are surrounded by housing rings 22 welded to the plates, the inner diameter of which corresponds to the diameter of the bores 21. In this way, the housings are constructed to receive main bearings 23 in which the crankshaft 24 is rotatably mounted.

The front uprights 12 and the rear uprights 15 as well as the lower longitudinal beams 14 are displaced inwardly in the plane direction relative to the upper longitudinal beams 13 mounted at a distance from the lateral circumferential body parts so that there is space on the side outside the steel plates 20 in each case. which in each case extends outwards to an even height with the longitudinal beam 13 above it.

Each flywheel 25 is provided with a laterally outwardly pointing crank pin 26, the center line of which extends exactly parallel to the center line of the crankshaft 24. Both flywheels 25 are arranged on the crankshaft 24 at such a relative angular position that the center lines of the pins 26 are exactly the same line.

The pushers 3 are in each case connected to these pins 26 by means of rolling bearings 27.

Mounted on the lower part 10 is a motor 28 mounted on an approximately vertical clamping frame 29 which, relative to the lower part 10, is pivotally mounted on the crankshaft about an approximately parallel pivot shaft 30 and is adjustable from above by means of a lower part 10 articulated screw 31 and nut 32. Thus, the drive belt 33 can be given the correct tension which travels on the motor pulley and the circumferential belt surface 34 of the left flywheel 25 of the viewer of Figure 2 and thus transfer the drive force from the motor to the crank drive of the circular saw machine.

Symmetrically with respect to the polar plane Eg, there are in each case two additional bores 35 at the same height as in the same straight horizontal direction in the steel plates 20 at the front and rear of the crankshaft. by means of rolling bearings are rotatably mounted. These compensating shafts 36 are hereinafter referred to as the main compensating shafts, because the crankshaft 24 also forms a compensating shaft, because the flywheels 25 are provided with first compensating weights 25a which act together . The impact motion of the saw ring and the above-mentioned linear oscillation contrast in their phases. For this purpose, the second compensating weights 36a and the first compensating weights 25a are arranged according to Fig. 1 so that the others pass through their upper dead center if the others are at their lower dead center and vice versa, rotating in pairs in parallel but in pairs with respect to 11 72452 11 in opposite directions. The individual compensating weights 25p and 36a are dimensioned so that in each of them the input GD of their weight and the diameter D of the path of rotation on which its center of gravity Sj and Sjj move is approximately equal and corresponds approximately to a quarter of the crankcase diameter Dg (see Fig. 3) the result of the assumed weight of the circumferential portions oscillating in the direction of the cutting impact.

The circumferential oscillating parts of the saw blade mainly include the saw blade with guide slides, saw blades with grips, saw blade holders with snacks, upper pusher heads and half the weight of the pusher shank. The other half of the weight of the pusher arm can be considered to be a mass rotating around the crankshaft, performing a clean rotational movement, and just like the lower pusher head, from which no linear vibration component is emitted either.

In the lower part 10, two additional compensating shafts 37 are mounted symmetrically across the plane as well as parallel to it at a relatively high distance at the same height, on which the third compensating weights 37a are located outside the longitudinal beams 13. These are operated relative to the crankshaft 24 at twice the rotational speed and have a phase ratio relative to the cutting oscillation oscillation of the sawtooth and such a GD relative to the circumferential oscillating circumferential parts that the second-order mass forces produced by the latter are compensated.

The compensating shafts 37 can further be provided with fourth compensating weights (not shown in the drawing), one of which the third compensating weight on its axis rotates about 90 ° forward, while the other travels 90 ° behind the third compensating weight on its axis. The mass forces produced by these four compensating weights are able to at least partially compensate for the oscillation from the circumference via the circumferential body 1 to the ground forces transmitted to the lower part 10, which are caused by the horizontal oscillating movements of the saw frame. In describing the structural example, it is left open whether the circumferential pushers use 3 pendulum rings, i.e. a saw frame with a cutting stroke movement accompanied by a horizontal deflection movement for the lower and upper dead center, or a normal saw stroke in the cutting direction direction; for this reason, this fourth compensatory weight is not shown in the drawing.

Figures 3 and 4 show some details of the use of various compensating shafts and compensating weights derived from the crankshaft pin 26 n * »_____ .. TT ___ 12 72452.

A crank 38 is non-rotatably mounted on the outermost end of the viewer of Figures 1 and 3 and on the left palm pin 26 in Figures 2 and 4. The pusher head is located between the flywheel 25 and this crank 38, with the second end of the crank 38 articulated to the free end of the crank 38 so as to flush With the 25 planes, it would be rotatable about an articulated axis that draws the same path of rotation as the palm pin if it did not sit on your non-rotating crankshaft on a parallel axis 40 whose centerline coincides as closely as possible with the centerline of the crankshaft. Dividing the crankcase into two interlocking parts 38 and 39 allows certain inaccuracies to exist in the aforementioned coaxiality.

The shaft 40 goes into a gearbox in which a drive gear 41 is rigidly attached to it. From this gear 41 two identical gear connections lead to the main compensation shafts 36. via a gearbox via a gear 41 driven by cranks 38, 39 in the same direction relative to the crankshaft 24, but in the opposite direction of rotation, the gears being dimensioned relative to each other so that the speed of the crankshaft and the speed of the compensating shafts correspond exactly to each other.

The additional compensating shafts for the third and possibly fourth compensating weights are actuated counterclockwise and with respect to the main compensating shafts 36 by means of toothed belts 42 at respective speeds. , that in the toothed belt drive connection to the right of the viewer of Fig. 3 from the main compensation shaft 36 to the auxiliary compensation shaft 37, no reversing switch is used, while in the drive connection on the left, such a reversing is used.

Figure 4 also shows details of the bearing of the main compensating shafts 36, which are not so clear from Figure 2. These details are understandable with the aid of the drawing, so they do not skip the broader description.

13 72452

The second counterweights 36a are shaped as discs with wedge-shaped cavities to provide a higher torque relative to the simple counterweight, resulting in a deeper self-resonance.

The beams and columns of the rigid lower part consist of steel perforated profiles.

The rigid lower part is assembled primarily at the factory as a transport unit with crankshafts, compensating shafts, compensating weights and flywheels, when installing a bearing-equipped crankshaft with an intermediate tube not shown in the drawing, then the combination of crankshaft 24 rolling bearings 23 and split tube is pushed externally into one of the two bearing plates adhering to the outer circumference of the rolling bearing 23, not shown, first through the second bearing housing and then into the second bearing housing 23 The 20 placed bearing housings settle into their final positions, after which the split tube is removed. In this connection, the press plate can be tightened against the steel plate 20 by means of a screw-adjustable tension anchor, from which the above-mentioned combination is pushed into the lower part. For this purpose, the plates around the crankshaft 24 are further supported against each other by a few tubes 44 which bind the plates together and are welded to their opposite sides. The hole spaces surrounded by the tubes are accessible through bores 45 in the steel plates so that the aforementioned pull anchor can be pushed through these tubes 44 and then provided with a pull nut on the parts of the threaded end projecting from the other side. The tubes 44 provide the steel plates 20 with a significant additional stiffness against bending during the insertion of the bearing shafts under considerable compression and are located outside the path of rotation of the other compensating weights. In addition, the increased stiffness of the steel plates 20 will benefit from the stiffness of the entire lower part 10.

Claims (5)

14 72452 A circular saw having an up and down movable saw ring (2) in the circumferential frame (1), driven by at least one rotary rod (3) connected at its upper end to the saw frame pin (4) at its upper end and to the palm pin (26) of the crankshaft (24) at its lower end, or a crankshaft (24) in a horizontal position and perpendicular to the cutting direction of the machine, and a device driven by the crankshaft (24) for balancing the oscillating circumferential masses, the first compensating weights (25a) arranged directly on the crankshaft (24) at both ends and the second compensating weights (36a) rotating about axes of rotation (36) parallel to the crankshaft (24) at the same average speed as the crankshaft and in opposite directions to the first compensating weights (25a), and in which the rotation of the weight (G) and center of gravity of the first compensating weights (25a) (D) the product (GD) is of the same order of magnitude as the other compensating weights ( 36a) the corresponding input and the first and second compensating weights (25a, 36a) are so large and arranged relative to each other that the resulting mass forces they produce are approximately equal to, but opposite to, the first order mass forces of the oscillating circumferential portions of the saw frame (2) , characterized in that the crankshaft (24) is mounted in a manner known per se on the lower part (10) of the saw, which forms a movable structural unit and which can be mounted on a flat horizontal base surface (11) and which is torsionally rigid even when loaded on circumferential parts the compensating weights (36a) are arranged on two main compensating shafts (36) parallel to the crankshaft (24), which in front of and behind the crankshaft (24) and arranged approximately at the same height and substantially symmetrically with the lower part (10) and each supporting another balance (36a) non-rotatably arranged on a central plane (E1) perpendicular to the crankshaft and intersecting between the first compensating weights (25a) of the crankshaft, , and that the product of weight and diameter at the individual first and second compensating weights (25a or 36a) corresponds approximately to one-fourth the result of the estimated weight and circumferential diameter (Dr) of the circumferential oscillating parts of the saw ring (2), and that the crankshaft (24) and main axis is mounted on common side wall portions of the lower part (10). Circular saw according to Claim 1, characterized in that the first compensating weights (25a) are each mounted on their own integrated flywheel (25) on the built-in crankshaft (24) and in that the motor-driven transmission belt (33) is mounted on a second belt pulley ( 34) equipped with a flywheel (25). Circular saw according to Claim 1 or 2, characterized in that the main compensating shafts (36) at approximately the same height are arranged slightly lower than the crankshaft (24), the height difference between the crankshaft (24) and the main compensating shafts (36) being selected so that the height difference the tilting moment compensates as much as possible for the mass forces of the connecting rod or connecting rods (3). Circular saw according to one of the preceding claims, characterized in that two additional compensating shafts (37) are mounted on the lower part (10) parallel to the crankshaft (24) and symmetrically with respect to the vertical plane (Eq) passing through its center line, which is used with respect to the crankshaft (24). at twice the speed and in the opposite direction and each having at least one third compensating weight (37a) symmetrical about the center plane (E1) of the shafts, having a weight (G) and a diameter (D) input (GD) and in such an angular position with respect to the other that the effect of the third compensating weights (37a) is to compensate for the second-order mass forces of the circumferential oscillating parts of the saw ring (2). A circular saw according to claim 4, provided with a pendulum ring, wherein the additional horizontal oscillating motion of the saw ring (2) ________ - ΤΓΖ ----- ιβ 72452 is selected such that the local curve of the individual saw teeth corresponds approximately parallel to the saw frame that in order to at least partially compensate for the mass forces generated by the extra horizontal oscillation movement, applied horizontally to the circumferential frame (1) by the saw frame (2) and transmitted to the lower part (10), a fourth equalizing weight is provided on each of the two additional compensating shafts (37); about 90 ° above the compensating weight (37a) and about 90 ° behind the second additional compensating shaft (37). 72452 17