GB1598395A

GB1598395A - Feed apparatus for the infeed of material to machines or apparatus

Info

Publication number: GB1598395A
Application number: GB587778A
Authority: GB
Original assignee: Individual
Current assignee: Individual
Priority date: 1977-09-13
Filing date: 1978-02-14
Publication date: 1981-09-16
Also published as: BR7805947A; DE2741149A1; DE2741149C2

Description

(54) FEED APPARATUS FOR THE INFEED OF MATERIAL TO MACHINES OR APPARATUS (71) I, OTTO BIHLER of 2 Schleiferweg, D-8959 Halblech/Fussen, Federal Republic of Germany, a citizen of the Federal Republic of Germany, do hereby declare the invention, for which I pray that a patent may be granted to me, and the method by which it is to be performed, to be particularly described in and by the following statement: This invention relates to a feed apparatus for the infeed of material in machines or apparatus, comprising a driving shaft rotatable about a drive axis, a first eccentric part which rotates with said driving shaft and has a first eccentric part axis which is displaced parallel relative to said drive axis and a second eccentric part which follows the movement of the first eccentric part about said drive axis, with a second eccentric part axis which is displaced parallel relative to the first eccentric part axis, this second eccentric part being rotatable about a second eccentric part turning axis parallel to said second eccentric part axis and receiving, by way of a train of gear wheels stepped-up movement derived from the rotation of said driving shaft the drive movement of the feed apparatus being taken from the second eccentric part.

Such feed apparatus has been disclosed in German Offenlegungsschrift 24 50 970.

In the feed apparatus as disclosed in said German Offenlegungsschrift the second eccentric part is provided with a first gear, which first gear meshes with a second gear mounted on the driving shaft, said second gear meshing with a stationary internally toothed gear rim. In this apparatus it is not easily possible to vary the eccentricity of the first eccentric part with respect to the driving axis of the driving shaft.

It is the object of this invention to provide a feed apparatus as stated above, in which the eccentricity of the first eccentric part with respect to the drive axis of the driving shaft is easily variable.

In view of this object it is proposed that the apparatus further comprises a gear wheel carrier following the movement of the first eccentric part about the drive axis, the spatial orientation of said carrier being substantially constant and said carrier carrying a gear wheel which lies in the train of gear wheels.

An example of the invention will now be described with reference to the accompanying drawings, in which: Figure 1 is a schematic view of a known feed apparatus.

Figure 2a shows travel path diagrams for explaining a way of shortening the infeed angle in the feed apparatus of Figure 1; Figure 2b shows speed diagrams corresponding to the travel path diagrams shown in Figure 2a; Figure 3 illustrates in a diagrammatical way a possibility of overcoming the disadvantages of the apparatus of Figure 1; Figure 4 represents the travel path curve resulting from the apparatus of Figure 3, which travel path curve is also true for the embodiment of this invention which is illustrated in Figure 5.

Figure 5 is a side elevational view, with partial cross-sectioning of the embodiment of the invention; Figure 6 is a plan view of the embodiment shown in Figure 5; and Figure 7 is a view given for explaining a periodically variable rotational speed, which may be possibly realized in the case of the embodiment of Figures 5 and 6, of a first eccentric Din.

In Figure 1, 1 designated a disc which is driven, by the machine drive designated M, for rotating about a driving shaft axis 0. During one working cycle of the machine disc 1 executes a complete revolution. An eccentric slide 3 is slidable, along a guide 2, in or on the disc 1. The position of the eccentric slide 3 is adjustable by means of a spindle 4 and nuts 5.

An eccentric pin 6 is arranged on the eccentric slide 3 and the connecting rod head 7 of a connecting or pull rod 8 is mounted on this pin 6. The boss of the connecting rod 8 acts on a lever 9 by way of spring 10. Lever 9 is mounted so as to be pivotable about a pin 11 spatially arranged, in some suitable way, on the machine frame. The end of the lever 9 remote from the pin 11 is connected to an infeed slide 13 by way of a strap 12. The infeed slide 13 is rectilinearly slidable between -two stops 14. The working stroke h of the infeed slide 13 depends on its length 1 and on the distance between the two stops 14.

When disc 1 rotates the eccentric pin 6 moves about the fulcrum 0 on a circular path of movement. The connecting rod 8 is shifted both in its axial direction and also, relative to the lever 9, about the centre point of its boss. The extent of movement in the axial direction depends on the adjustable eccentricity E of the eccentric pin 6, whereas the extent of pivotal movement of rod 8 decreases with increasing length of connecting rod 8 relative to the eccentricity E.

For purposes of simplification it will be assumed, for the following explanations of Figures 2a, 2b and 4, that the length of the connecting rod 8 is so great, relative to the eccentricity E of the eccentric pin 6, that the pivotal motion of the connecting rod 8 can be ignored, that is to say that the connecting rod 8 moves almost parallel to itself. It is to be emphasised that the practical value of the invention is in no way restricted by this simplification, which is made purely for explanation of the principles involved. Thus, the invention described below is susceptible of use for any feasible ratio of connecting rod length to eccentricity and, naturally, is not restricted to the use of a connecting rod as coupling member between the eccentric pin and the infeed slide. For example, coupling may be effected, particularly in the case of small lengths of infeed movement, by arranging for the eccentric pin to directly drive a slide block which is guided, in a groove of the infeed slide, transversely of the direction of infeed. The translatory movement of the connecting rod 8 in Figure 1 results in a rotation of lever 9 about pin 11. In turn this rotation of lever 9 shifts, through the intermediary of strap 12, the infeed slide 13. Connecting rod 8 could also act directly on the infeed slide 13, that is to say without the motion-transmitting lever 9.

The feed apparatus shown in Figure 1 is intended to draw the strip of wire like material 15 from a storage roll (not shown) or the like into the machine in the direction indicated by arrow A, this infeed movement taking place by separate increments of infeed movement of identical path lengths. As is readily apparent from Figure 1, the lengths of these increments of infeed movement equals the working stroke h of the infeed slide. This length of infeed movement can be adjusted to the desired value by altering the distance between the two stops 14. During the infeed movement of the slide 13 - in Figure 1 this infeed movement is arbitrarily assumed to be the movement from the right-hand stop 14 to the left-hand stop 14 - a tong mechanism, schematically indicated by arrow 16a, secured the material 15 against the infeed slide, so that this material is moved, together with the slide, in the left-hand direction (Figure 1). When, in the course of this infeed movement, the slide 13 strikes against the left-hand (Figure 1) stop 14, this movement is stopped, while the eccentric pin 6 continues to rotate at a constant speed, and one of the springs 10 absorbs the continued movement of the connecting rod 8 until the eccentric pin 6 has passed the left-hand (Figure 1) dead-centre point, i.e. the 90" point. During this period of standstill a retaining device, which is in the form of a tong mechanism schematically designated by arrows 16b, comes into engagement with the material 15 and secured it on a stationary frame portion 16c. In this way it is ensured that the material 15 will not be completely or partially pulled back out of the machine in the course of the ensuing return or backward movement of the infeed slide 13, e.g. through frictional contact with the infeed slide. At the end of the standstill period the infeed slide 13 is pulled back to the right-hand (Figure 1) stop 14 and remains in abutment against this stop for a specified standstill period. During this second standstill phase the tong mechanism 16b is caused to discontinue clamping the material against the stationary frame part 16c although, naturally, this only takes place after the tong mechanism 16a has again assumed a position in which it secures the material against the infeed slide 13. Thus. the interchange of functions of the tong mechanisms 16a and 16b always takes place with mutual overlap.

Schematically represented on the left-hand side of Figure 1 is a material treating or processing unit in the form of a bending tool, which is intended to treat the material 15. The bending tool comprises a die 150 and a punch 153 which is rectilinearly shiftable between two stationary guides 151 and 152. The die 150 is formed with a recess. which corresponds to the desired bend to be formed in the material, while the lower end of the punch 153 has a shape complementary to that of the recess in die 150. At its opposite end punch 153 carries a cam follower roller 154 which is in engagement with a cam disc 155. A common machine drive M drives both disc 1 and also cam disc 155 synchronously and at the same speed. The above-described control of the tong mechanism 16a and of the retaining device 16b can also be derived from the drive M, this being indicated by the respective dashed lines leading to the drive M. The punch 153 is upwardly (Figure 1) biased by means of a spring 156. Spring 156 is accommodated in a recess 157 of punch 153 and engages at its lower end with a stationary part and at its upper end with punch 153.

As long as the eccentric pin 6 is in the vicinity of its infeed angle ae the cam follower roller 154 engages with a part of cam disc 155 having the smallest radius. Accordingly, the punch 153 is retracted, during the infeed movement of the slide 13, a sufficient distance from the die 150 to ensure that the next portion or section of the material 15 can be pushed into position between die 150 and punch 153. Depending on the particular shape of die and punch it may also be necessary, for ensuring an unobstructed feed of the material 15, that the die 150 be retracted, from its working position, into a rest position during the inward (infeed) movement of the slide. This movement of the die 150 may be effected in exactly the same way as that of the punch 153, that is to say by means of a cam plate and a motion-restoring spring. One revolution of the cam plate 155 represents a working cycle of the machine, which comprises infeed of the material and also the movement of the punch 153, and possibly also of die 150, into the working position from the rest position and, thence, back into the rest position. It is to be noted that, naturally, the number of other processing or treating units can also act, within this working cycle, on the previously introduced length of material, such additional treatments of the material taking place either simultaneously or successively; this is the case when more complicated bending and/or punching work is to be carried out.

Figure 2a shows two different path diagrams for the feed apparatus of Figure 1, that is to say diagrams of the path of motion s described by the infeed slide 13 potted against the angle a of rotation of the eccentric pin 6. An infeed angle ae, standstill angle aS and a return motion angle ar (see Figure 1) correspond, with respect to the eccentric pin 6, to the above defined terms infeed time, standstill time, and return motion time, these terms referring to the movement of the infeed slide 13. So long as the angular speed of the eccentric pin 6 is constant, these angles are proportional to the corresponding times. For purposes of clear explanation the condition in which the infeed slide 13 lies exactly centrally between two stops 14 is arbitrarily selected as s = 0. The path between the centre and the left-hand stop (Figure 1) is arbitrarily selected as positive, and the path between the centre and the right-hand stop (Figure 1) is, consequently, referred to as negative.

If the above explained simplification is adopted that the inclination of the connecting rod 8 can be ignored during the complete rotation of the eccentric pin 6, then the inward (infeed) movement of slide 13 follows, after this slide 13 has moved from the right-hand stop 14 (Figure 1), the curve E1 sina in one instance E = El of eccentricity of the eccentric pin 6, and follows the curve Eosine in the other case E = E2 of eccentricity. a designates the angle of rotation of the eccentric pin 6 about the fulcrum 0. When the infeed slide has come into abutment against the left-hand stop 14 (Figure 1), the eccentric pin 6 has just passed through the infeed angle ae = aei or ae = e2 (see also Figure 1). As only the range 0 to 1800 of the range of angular rotation of the eccentric pin 6 is represented in Figure 2a, only half the infeed angle (a01)/2 and (aye)12 appears in this Figure 2a. So long as the eccentric pin 6 is subsequently passing through the standstill angle aS = aSl or aS = Q2 (left-hand side in Figure 1), the infeed slide 13 abuts against the left-hand stop 14 and is stationary. The corresponding portion of the paths of movement (1) and (2) in Figure 2a extend rectilinearly parallel to the abscissa at this time. After eccentric pin 6 has passed through the standstill angle aS. the infeed slide 13 is retracted, during the return angle ar, to the right-hand stop 14. In the case of the generally symmetrical conditions obtaining, the infeed angle ae equals the return motion angle ar. Again, the curves (1) and (2) of the paths of executed movements follow the function s = El sina and s = E-sina respectively.

The material is only moving so long as the infeed slide 13 is in movement whilst at the same time the tong mechanism 16a secured the material 15 against the slide 13, so that the material cannot be processed or treated. This is the situation so long as eccentric pin 6 is passing through pin feed angle ae. Therefore the working angle aa available for treating or processing the material introduced is: Qi = ar + 2 aS cr, = 3600 as ar + ae + 2 aS = 360".

Comparison of the curves (1) and (2) of the paths of movement, shown in Figure 2a, shows one way of shortening the infeed angle ae and, hence, of increasing the working angle aa in the case of the feed apparatus illustrated in Figure 1. If the eccentricity of the eccentric pin 6 is increased from E = El to E = E2, the pattern of movement of the infeed slide 13 outside the standstill angle or standstill phases corresponds to the function s = E2-sina. As is clear from Figure 2a, the infeed angle aye2, through which the eccentric pin 6 must pass for moving the infeed slide 13 from the right-hand stop 14 to the left-hand stop 14 (Figure 1), is smaller in the case of the greater eccentricity E2 than in the case of the eccentricity El. It should be clear that this smaller infeed angle ae2 results in a correspondingly greater working angle aa. However, it is also clear from Figure 2a that the overrun 2 of the connecting rod 8, which must be taken up or absorbed by the spring 10 after the infeed slide 13 has come into contact with the stop 14, is very much greater, in the case of curve (2), than the comparable overrun U1 in the case of curve (1). The path of resilient movement of springs 10 must therefore be correspondingly greater, which results in the above mentioned drawbacks insofar as the more rapid wear and tear and the higher energy consumption are concerned.

In Figure 2b the speed v of the infeed slide is plotted, for the two curves (1) and (2) of the paths of movement in Figure 2a, as a function of the angle of rotation a of the eccentric pin 6. It should be apparent that the speed of the infeed slide should have a cosine-like pattern so long as it is not brought to a halt by a stop. The speed of the infeed slide 13 at the end of the infeed angle aei and ae2 is the speed VAl and VA2 respectively at which the infeed slide comes into abutment with its stops 14. It is clear from Figure 2b that the speed VAl of impact is appreciably lower than the speed VA2 of impact. One reason for this is the cosine-like pattern of speed of the infeed slide, which causes the impact speed to progressively approach the maximum speed with decreasing infeed angle. The second reason for the fact that VA2 is greater than VAl resides in the increased eccentricity E2 which, for one and the same speed of rotation of the disc 1, results in a higher speed of rotation of the eccentric pin 6 and, hence, a higher maximum speed V2 of the infeed slide 13.

It is clear that, in the case of the known feed apparatus illustrated in Figure 1, the infeed angle ae can be reduced by altering the eccentricity E of the eccentric pin 6 and by corresponding alteration of the springs 10. However, this reduction in the infeed angle ae is associated with a pronounced increase in the overrun and in the speed of impact. As both a greater overrun and also a greater speed of impact. As both a greater overrun and also a greater speed of impact are disadvantageous, shortening of the infeed angle is subject to narrow limits insofar as the known feed apparatus is concerned.

Figure 3 diagrammatically illustrates apparatus which can be used to overcome these difficulties. In this figure, 51 indicates a disc which rotates synchronously with the drive of the machine (not shown), which is intended to process or treat the material introduced.

One revolution of the disc 51 corresponds to a complete working cycle of the machine. The disc 51 carries an eccentric pin 52 which is arranged at a distance of the eccentricity E from the centre point or from the axis of rotation A of the disc 51. The eccentric pin 52 engages, for example by way of a coupling member constituted as a connecting rod 53. with an infeed slide which is not shown but which corresponds for example to the infeed slide illustrated in Figure 1, this infeed slide being guided for sliding movement along the axis X-X. The eccentric pin 52 could, by way of contrast. equally well engage in a guide groove formed in the infeed slide and extending perpendicularly of the direction of movement of the slide. As shown in Figure 1, the eccentricity E of the eccentric pin 52 can be adjusted for altering the working stroke of the infeed slide. The disc 51, and also a spur wheel 54 which is connected to the disc 51 or is integral therewith, are freely rotatably mounted at the free end of a rocker arm 55. The other end of the rocker arm 55 is mounted in a stationary joint 56; mounted concentrically with the joint 56 is a further spur gear wheel 57 which, in some suitable way, is so driven that, taking into account the motion transmission ratio of the spur gears 54 and 57, the disc 51 rotates, in the above mentioned manner, synchronously with the machine drive, and executes one revolution per working cycle. A push bar 58 is articulated at the free end of the rocker arm 55. However, the point at which the push bar 58 engages the rocker arm 55 does not necessarily have to coincide with the mounting point of disc 51 and spur gear 54, but may lie at any point between the joint 56 and the free end. A second disc 59 is mounted for rotation about an axis B, and is driven, in some suitable way, synchronously with the disc 51 although it rotates at three times (n7 = 3nl) the speed of the disc 51. The second disc 59 carries a second eccentric pin 60 at the distance of the eccentricity Z, the other end of the push bar 58 being rotatably mounted on this pin 60; the eccentricity of the eccentric pin 60 can be adjustable in a similar way to the eccentric pin 52.

When, in the arrangement shown in Figure 3, the disc 59 rotates about axis B, the axis of rotation A of the disc 51 will move back and forth on an arc lying concentrically of the joint 56. If, further, the disc 51 rotates about the axis of rotation A, connecting rod 53 will move the infeed slide (not shown) back and forth and rectilinearly on the axis X-X between two end positions. If it is again assumed, for purposes of simplicity, that the length of the connecting rod 53 is great relative to the eccentricity E of the first eccentric pin 52, then, if the disc 59 is stationary, a rotation of the disc 51 will result in the travel path curve s(a) = E sino, shown in Figure 4, for the infeed slide, s standing for the path of travel executed by the infeed slide from the centre position and a representing the instantaneous angle of rotation of the disc 51 in accordance with the definition in Figure 3. In Figure 4 the travel path curve is only represented for the angular range 0 S a S 1800. It is clear that when this simplification is assumed the maximum stroke of the infeed slide will equal twice the amplitude of the travel path curve s(a), that is to say 2E.

Subject to the further simplification that the length of the rocker arm 55, and also that of the push bar 58, are large relative to the eccentricity Z of the second eccentric pin 60, there will substantially be obtained - in the course of one revolution of the disc 59 and for. a movement of the axis A of rotation of the disc 51 along the axis X-X - the travel path curve sl ((p) = z sin (p, which is shown in Figure 4 and in which sl represents the path of travel executed by the axis of rotation A in the direction of the axis X-X from a central position and (p stands for the angle of rotation of the disc 59 defined- in Figure 3.

The travel path curve s2(a) actually resulting for the infeed slide from the action of the supplementary drive 59, 60 is arrived at by superimposition, i.e. addition, of the travel path curves s(a) and si((p) = s1(3.a), and is also shown in Figure 4.

By reason of the threefold speed of the disc 59 ( = 3a) the second eccentric pin 60 produces, in conjunction with the rocker arm 55 and the push rod 58, an additional periodic component of movement for the infeed slide, the frequency of which additional movement is three times that of the also periodic main component of movement deriving from the eccentric pin 52. In Figure 3 the same direction of rotation of the discs 51 and 59 and of their eccentric pins 52, 60 is assumed. It is clear that, in the case of the opposite direction of rotation, the same travel path curves will be obtained are as shown in Figure 4, insofar as the zero position, shown in Figure 3, of the second eccentric pin 60 is turned through (p = 1800.

Without the above assumptions concerning the ratio of the length of the connecting rod to the eccentricity E, or concerning the ratio of the length of the rocker arm and of the push bar to the eccentricity Z, the travel path curves obtained differ to a greater or lesser degree from the sinusoidal curves shown in Figure 4 without any basic alteration in the superimposition of the components of movement al d in the resultant travel path curve.

Thus, the invention as later to be described is in no way restricted to the assumptions, which were only made for purposes of simplified explanation. The movement of the axis A of rotation on an arc about the swivel axis of joint 56 results, for the spur gear wheel 54 (and, hence, also for the eccentric pin 52), in an angular speed which fluctuates periodically above a centre value but which can in practice be ignored.

As has been explained with reference to Figure 1, the movement of the infeed slide is limited, by means of stops, to the working stroke h. By reason of the superimposition according to the invention of a main component of movement and of a supplementary component of movement with three times the frequency there is only required, for the working stroke h of the infeed slide, the relatively small infeed angle ae shown in Figures 3 and 4 and the return movement angle ar, which is of the same size, as angles or rotation of the first eccentric pin 52. Again Figure 4 shows only half the infeed angle (aye)/2 and of the return movement angle (ar)12, as the travel path curves are only represented in the range 0 < a ffi 1800. The connecting rod 53 is coupled to the infeed slide, in the Way described with reference to Figure 1, by way of springs so as to enable the overrun U1 - apparent from Figure 10 - that is to say the continued movement of the connecting rod 53 after the infeed slide has come into contact with a stop - to be taken up or absorbed.

A comparison of the travel path curves s(a) and s2(a) in Figure 4 makes clear the effect of the supplementary component of movement on the magnitude of the infeed angle and of the overrun. Without the additional component of movement there would be, for a constant working stroke h of the infeed slide, the appreciably greater overrun U2 and an appreciably greater infeed angle. The result of the greater infeed angle would be a smaller standstill angle a'S and, hence, a smaller working angle for each machine cycle. Through suitably selecting the ratio of eccentricity E to eccentricity Z it can be ensured that the speed of impact of the infeed slide on to its slopes is at least not greater than on the occasion of a movement exclusively executed by the first eccentric pin with the same eccentricity E.

This means that, for an infeed angle of constant magnitude, the supplementary component of movement reduces both the overrrun and also the speed of impact.

As is clear from Figure 4, the greatest possible infeed length, that is to say the greatest possible slide stroke hmaX = 2 (E-Z), occurs in the resulting travel path curve s2(a). If the working stroke of the infeed slide were set, by means of the stops, to an even greater value, the infeed slide would move away from the stop at a = 900, which is of course undesirable.

The maximum infeed length corresponds to a maximum infeed angle amax = 2 arcsin (1/2) (ff/Z-1). Thus, the maximum possible infeed angle depends on the ratio of the eccentricities of the first and second eccentric pins. If this ratio E/Z lies between 4 and 9 the resulting travel path curve will, if the maximum possible infeed angle is used, result relative to the pure sinusoidal curve of the amplitude E and for a constant working stroke of the infeed slide h - in a reduction in the overrun, a reduction in the infeed angle and also a reduction in the speed with which the infeed slide comes into contact with the stops. The ratio E/Z = 9 represents a limit value at which the resulting travel path curve s2(a) still has only one maximum at a = 90".

The explanation given above of the invention assumed a speed ratio of the disc 51 and of the disc 59 of n1:n2 = 1:3. In principle, it is also possible to use a speed ratio n1:n2 = 1:5, at which the additional component of movement has 5 times the frequency of the main component of movement based on the eccentric pin 52. For a constant infeed angle this state of affairs does not result, relative to a movement solely based on the main component of movement, in a reduction in the overrun, but does result in a quite considerable reduction of the speed at which the infeed slide strikes against its stop. Further, it is possible, through a second eccentric pin, which rotates with three times the speed, and with a third eccentric pin, which rotates with five times the speed, to obtain a travel path curve for the infeed slide which is composed of three components of movement and in which, in spite of the very small infeed angle, the overrun can be further reduced relative to the arrangement shown in Figure 4. Such a superimposition of three components of movement could be realized simply by a cascade arrangement of the embodiment shown in Figure 3. In such a cascade arrangement the disc 59 would be mounted in a rocker arm comparable to rocker arm 55, and this rocker arm (i.e. a rocker arm comparable to rocker arm 55) would be moved back and forth, by way of a further push rod, by a third disc with the third eccentric pin.

It was stated at the outset that the transfer of movement from the first eccentric pin 52 to the infeed slide (not shown) does not necessarily have to take place by way of

comprising a radial extension 126 and a pin 127, which is rotatable about an axis lying parallel, in the extension 126, to the axes F, G and K. The head of the pin 127 is constituted as a sleeve 128, in which the connecting rod 111 is slidably guided, so that the spatial orientation of the carrier 123 is substantially constant.

Figure 6 is a schematic plan view of the embodiment shown in Figure 5. If it is first of all assumed, that the length of the connecting rod 111 is great relative to the eccentricity E of the eccentric pin 104, it can be further assumed, as a first approximation, that the connecting rod 111 will be shifted continuously parallel to itself during one revolution of the eccentric pin 104 about the driving axis A and during the rotation of the second eccentric part 108, 109 about the second eccentric part turning axis F. This means, that the position of the gear wheel carrier 123 with the internal toothed rim 123' remains unaltered, relative to the axis F of the eccentric pin 104, while this pin is rotating about drive axis A, as relative rotation between the connecting rod 119 and the gear wheel carrier 123 is impossible. If disc 100 rotates synchronously with the machine, the axes F of the eccentric pin 104 and K of the intermediate gear wheel 125 move on concentric circles about the drive axis A. As, in accordance with the above stated assumption, the gear wheel carrier 123 does not turn about axis F, the intermediate gear wheel 125 rolls along the internally toothed rim 123', and thus executes a further rotation about its axis K. Rotation of the intermediate gear wheel 125 is transmitted to the driving gear wheel 107 and leads to second eccentric part 108,109 rotating about axis G. Through suitably selecting the motion transmission ratio of the internally toothed rim 123' and the gear wheels 125 and 107 the desired speed ratio between the second eccentric part 108, 109 and disc 100 of 3:1 for example can be set.

For a finite length of the connecting rod 111 the latter rocks about its point of articulation on the infeed slide (not shown), and this is accompanied with a corresponding rocking movement of the gear wheel carrier 123 about the axis F. In Figure 7 circle 129 indicates the path of the eccentric pin 104 about the drive axis A. The straight lines 130 and 130' represent the extreme positions of the connecting rod, which rocks about the point of articulation 131 on the infeed slide. If the path of travel 129 of the eccentric pin 104 is in clockwise direction the rotary movement of the second eccentric part 108, 109 will, in consequence of the rocking motion of the connecting rod 111, be accelerated, relative to the mean value corresponding to the infinite length of the connecting rod, in the first and second quadrants I and II, whereas this rotary movement of the second eccentric part 108, 109 will be decelerated relative to this mean value, in the third and fourth quadrants III and IV. Accordingly, the rotation of the second eccentric part takes place with a periodically altering angular speed which can, however, be neglected in view of the length conditions and eccentricity conditions which occur in practice.

WHAT I CLAIM IS: 1. Feed apparatus for the infeed of material in machines or apparatus, comprising a driving shaft rotatable about a drive axis, a first eccentric part which rotates with said driving shaft and has a first eccentric part axis which is displaced parallel relative to said drive axis and a second eccentric part which follows the movement of the first eccentric part about said drive axis, with a second eccentric part axis which is displaced parallel relative to the first eccentric part axis, this second eccentric part being rotatable about a second-eccentric-part-turning-axis parallel to said second-eccentric-part-axis and receiving, by way of a train of gear wheels, stepped-up rotary movement derived from the rotation of said driving shaft, the drive movement for the feed apparatus being taken from the second eccentric part, the apparatus further comprising a gear wheel carrier following the movement of the first eccentric part about the drive axis, the spatial orientation of said carrier being substantially constant and said carrier carrying a gear wheel which lies in the train of gear wheels.

2. Apparatus as claimed in claim 1, wherein the second eccentric part is rotatable about its second eccentric-part-turning-axis at a speed which corresponds to an odd integral multiple of the speed of the driving shaft.

3. Apparatus as claimed in claim 2, wherein the odd integral multiple is 3.

4. Apparatus as claimed in any one of claims 1 to 3, wherein the eccentricity of the first eccentric part relative to the drive axis is variable.

5. Apparatus as claimed in claim 4 wherein the first eccentric part is arranged on a first eccentric part carrier which is shiftable relative to the drive axis.

6. Apparatus as claimed in any one of claims 1 to 5, wherein the first eccentric part is an eccentric pin, which constitutes an axially parallel continuation of the driving shaft.

7. Apparatus as claimed in any one of claims 1 to 5, wherein the eccentricity of the second eccentric part relative to its second-eccentric-part -turning-axis is variable.

8. Apparatus as claimed in claim 7, wherein the second eccentric part comprises an eccentric base member and of an eccentric structure member, which can be rotated relative to the eccentric base member and locked in the position arrived at after rotation.

**WARNING** end of DESC field may overlap start of CLMS **.

Claims

**WARNING** start of CLMS field may overlap end of DESC **. comprising a radial extension 126 and a pin 127, which is rotatable about an axis lying parallel, in the extension 126, to the axes F, G and K. The head of the pin 127 is constituted as a sleeve 128, in which the connecting rod 111 is slidably guided, so that the spatial orientation of the carrier 123 is substantially constant. Figure 6 is a schematic plan view of the embodiment shown in Figure 5. If it is first of all assumed, that the length of the connecting rod 111 is great relative to the eccentricity E of the eccentric pin 104, it can be further assumed, as a first approximation, that the connecting rod 111 will be shifted continuously parallel to itself during one revolution of the eccentric pin 104 about the driving axis A and during the rotation of the second eccentric part 108, 109 about the second eccentric part turning axis F. This means, that the position of the gear wheel carrier 123 with the internal toothed rim 123' remains unaltered, relative to the axis F of the eccentric pin 104, while this pin is rotating about drive axis A, as relative rotation between the connecting rod 119 and the gear wheel carrier 123 is impossible. If disc 100 rotates synchronously with the machine, the axes F of the eccentric pin 104 and K of the intermediate gear wheel 125 move on concentric circles about the drive axis A. As, in accordance with the above stated assumption, the gear wheel carrier 123 does not turn about axis F, the intermediate gear wheel 125 rolls along the internally toothed rim 123', and thus executes a further rotation about its axis K. Rotation of the intermediate gear wheel 125 is transmitted to the driving gear wheel 107 and leads to second eccentric part 108,109 rotating about axis G. Through suitably selecting the motion transmission ratio of the internally toothed rim 123' and the gear wheels 125 and 107 the desired speed ratio between the second eccentric part 108, 109 and disc 100 of 3:1 for example can be set. For a finite length of the connecting rod 111 the latter rocks about its point of articulation on the infeed slide (not shown), and this is accompanied with a corresponding rocking movement of the gear wheel carrier 123 about the axis F. In Figure 7 circle 129 indicates the path of the eccentric pin 104 about the drive axis A. The straight lines 130 and 130' represent the extreme positions of the connecting rod, which rocks about the point of articulation 131 on the infeed slide. If the path of travel 129 of the eccentric pin 104 is in clockwise direction the rotary movement of the second eccentric part 108, 109 will, in consequence of the rocking motion of the connecting rod 111, be accelerated, relative to the mean value corresponding to the infinite length of the connecting rod, in the first and second quadrants I and II, whereas this rotary movement of the second eccentric part 108, 109 will be decelerated relative to this mean value, in the third and fourth quadrants III and IV. Accordingly, the rotation of the second eccentric part takes place with a periodically altering angular speed which can, however, be neglected in view of the length conditions and eccentricity conditions which occur in practice. WHAT I CLAIM IS:

1. Feed apparatus for the infeed of material in machines or apparatus, comprising a driving shaft rotatable about a drive axis, a first eccentric part which rotates with said driving shaft and has a first eccentric part axis which is displaced parallel relative to said drive axis and a second eccentric part which follows the movement of the first eccentric part about said drive axis, with a second eccentric part axis which is displaced parallel relative to the first eccentric part axis, this second eccentric part being rotatable about a second-eccentric-part-turning-axis parallel to said second-eccentric-part-axis and receiving, by way of a train of gear wheels, stepped-up rotary movement derived from the rotation of said driving shaft, the drive movement for the feed apparatus being taken from the second eccentric part, the apparatus further comprising a gear wheel carrier following the movement of the first eccentric part about the drive axis, the spatial orientation of said carrier being substantially constant and said carrier carrying a gear wheel which lies in the train of gear wheels.

3. Apparatus as claimed in claim 2, wherein the odd integral multiple is 3.

9. Apparatus as claimed in claim 8, wherein said eccentric base member is rotatable

about a driving gear wheel, which is concentric with the second-eccentric-part-turning-axis and can be locked in the position arrived at after rotation.

10. Apparatus as claimed in any one of claims 1 to 9, wherein the spatial orientation of the gear wheel carrier is substantially constant through support on a connecting rod which serves as drive organ is rotatably mounted on the second eccentric part.

11. Apparatus as claimed in claim 10, wherein the gear wheel carrier is supported on the connecting rod by a supporting device which permits a sliding-and rotary-movement.

12. Apparatus as claimed in any one of claims 1 to 11, wherein the second eccentric part is rotatably mounted on the first eccentric part about the first eccentric part axis of said first eccentric part; and a gear wheel which is attached to and for rotation with the second eccentric part, and is located concentrically of the first eccentric part axis of the first eccentric part, is in rolling engagement with an internally toothed rim secured to the gear wheel carrier, the gear wheel carrier being rotatably mounted on the second eccentric part.

13. Apparatus as claimed in claim 12, wherein the driving gear wheel which is rotatable with the second eccentric part is in engagement, by way of an intermediate gear wheel, with the internally toothed rim of the gear wheel carrier, this intermediate gear wheel being mounted about an intermediate gear wheel axis which is stationary relative to the first eccentric part axis.

14. Feed apparatus for the infeed of material in machines or apparatus substantially as hereinbefore described with reference to and as illustrated in Figures 5 and 6 of the accompanying drawings.