US3092159A

US3092159A - Cyclically operating machine having at least one element to be automatically positioned during each of the consecutive cycles of operation of the machine

Info

Publication number: US3092159A
Application number: US815989A
Authority: US
Inventors: Ebser Willi
Original assignee: Individual
Current assignee: Individual
Priority date: 1958-05-27
Filing date: 1959-05-26
Publication date: 1963-06-04
Anticipated expiration: 1980-06-04

Description

June 4, 1963 w, 5555 3,092,159

CYCLICALLY OPERATING MACHINE HAVING AT LEAST ONE ELEMENT TO BE AUTOMATICALLY POSITIONED DURING EACH OF THE CONSECUTIVE CYCLES OF OPERATION OF THE MACHINE Filed May 26, 1959 10 Sheets-Sheet 1 lNVENTOR W/LL/ 5555;?

BY /CHAEL 3. aye R ATTORNEY 3,092, 1 59 ELEMENT W. EBSER CYCLICALLY OPERATING MACHINE HAVING AT LEAST ONE TO BE AUTOMATICALLY POSITIONED DURING EACH OF THE CONSECUTIVE CYCLES OF OPERATION OF THE MACHINE Filed May 26, 1959 10 Sheets-Sheet 2 DHVI E. H 8 ME M m M B June 4, 1963 w. EBSER 3,092,159

CYCLICALLY OPERATING MACHINE HAVING AT LEAST ONE ELEMENT TO BE AUTOMATICALLY POSITIONED DURING EACH OF THE CONSECUTIVE CYCLES OF OPERATION OF THE MACHINE 1959 10 Sheets-Sheet 3 Filed May 26.

m K C m S m5 N 5 E L V M N Y M ATTOR Y June 4, 1963 w. EBSER 3,

CYCLICALLY OPERATING MACHINE HAVING AT LEAST ONE ELEMENT TO BE AUTOMATICALLY POSITIONED DURING EACH OF THE CONSECUTIVE CYCLES OF OPERATION OF THE MACHINE Filed May 26, 1959 10 Sheets-Sheet 4 Fig. 5

//Vl/E/VTOR W/LL/ 5685 Y H/IEL S. STRIKE/Q ATTORNEY 3,092,159 CYCLICALLY OPERATING MACHINE HAVING AT LEAST ONE ELEMENT June 4, 1963 w. EBsER TO BE AUTOMATICALLY POSITIONED DURING EACH OF THE CONSECUTIVE CYCLES OF OPERATION OF THE MACHINE Filed May 26, 1959 10 Sheets-Sheet 5 Q mm i" INVENTOR WILL! EBSER MICHAEL s. STR/KER Nay ATTORNEY June 4, 1963 w. EBSER 3,092,159

CYCLICALLY OPERATING MACHINE HAVING AT LEAST ONE ELEMENT TO BE AUTOMATICALLY POSITIONED DURING EACH OF THE CONSECUTIVE CYCLES OF OPERATION OF THE MACHINE Filed Nay-26, 1959 10 Sheets-Sheet 6 //vvE/vroa W/LL/ 5555/2 BXWICHAEL SIR/KER,

A TTOR/VE Y June 4, 1963 w. EBSER 3, 5

CYCLICALLY OPERATING MACHINE HAVING AT LEAST ONE ELEMENT TO BE AUTOMATICALLY POSITIONED DURING EACH OF THE CONSECUTIVE CYCLES OF OPERATION OF THE MACHINE Filed May 26, 1959 10 Sheets-Sheet 7 //v VEN 70 W/LL/ 13 55;

MICHAEL S. STRIKE i ATTURNEY June 4, 1963 w. EBSER 3,092,159 cm-Emmy OPERATING MACH NE HAVING AT LEAST ONE ELEMENT TO BE AUTOMATICALLY POSITIONED DURING EACH OF THE 10 Sheets-Sheet 9 CONSECUTIVE CYCLES OF OPERATION OF THE MACHINE Filed May 26, 1959 /NVENTOR W/LL! 51355 R BYM/CHAEL s. STR/KER ATTORN Y June 4, 1963 W EBSER CYCLICALLY OPERATING MACH ENE HAVING AT LEAST ONE ELEMENT TO BE AUTOMATICALLY POSITIONED DURING EACH OF THE CONSECUTIVE CYCLES OF OPERATION OF THE MACHINE Filed May 26, 1959 10 Sheets-Sheet 10 //V VENTOR W/Z 1/ EB 85/? Y M! CHAEL s. STE/KER A 770R NE Y United States Patent 3,092,159 CYCLICALLY OPERATING MACHINE HAVHJG AT LEAST ONE ELEMENT TO BE AUTOMATI- CALLY POSITIONED DURING EACH OF THE CONSECUTIVE CYCLES OF OPERATION OF THE MACI-HNE Willi Ebser, 30 Schonauerstrasse, Todtnau, Black Forest, Germany Filed May 26, 1959, Ser. No. 815,989 Claims priority, application Germany May 27, 1958 11 Claims. (Cl. 144-94) This invention relates to a cyclically operating machine in which one or more mechanical elements are to be cyclically displaced in a predetermined manner.

In the case of automatic machines of different types, irrespectively of whether they are textile machines, woodworking machines, machine tools, brush-making machines or the like, there are practically without exception mechanical elements effecting a feed which have to be adjusted or moved on in steps according to a predetermined working program and in synchronism with the operation of the machine. This moving on or displacement must in most cases take place alternately in both directions of movement and in steps which can differ very considerably in size. If several such mechanical elements are present to which feed movements have to be imparted and which must then also be brought back quickly into their retracted positions, many constructional difiiculties are encountered in the building of such a machine, if it is to meet the present day requirements as to working speed, accuracy of work and easy adjustability. This is especially the case if such a machine should be easily adaptable to frequently occurring changes in its working program and in which case it will be necessary to provide possibilities of control differing considerably from one another for the different working operations in each individual case.

The object of the invention is to devise a machine which renders it possible to meet the above-mentioned conditions with a constructional outlay which is inexpensive and nevertheless ensures maximum precision without causing any worry. At the same time it must be possible to adjust the controlling steps effecting the forward and backward movement not only in stages but also continuously. Similarly it must be capable of taking care of switching displacements of maximum length in both directions for one or more mechanical elements simultaneously.

With these objects in view, the cyclically operated machine according to the present invention mainly comprises an element whose position is to be determined during each of the consecutive cycles of operation of the machine, support means supporting the element for movement so that it can occupy different positions during the consecutive cycles of operation, swing frame means supported for turning movement by the support means, an elongated support member supported for axial movement by the swing frame means and carried by the same for turning movements therewith, drive means operatively connected to the swing frame means for turning the latter during each cycle from a first plane along a working stroke to a second plane and from said second plane along a return stroke to said first plane, linkage means connecting the elongated member to the element so that the extent to which the latter is moved by the linkage means is determined by the axial position of the elongated member with respect to the swing frame, and second linkage means located in said first plane and operatively connected to the elongated member to be moved thereby in one direction in said first plane, when the swing frame means turns along said working stroke thereof and in opposite direction in 3,092,159 Patented June 4, 1963 said first plane when the swing frame means moves along said return stroke thereof. The machine includes further a plurality of spacers located next to each other, and guide means guiding the spacers for movement perpendicularly to said first plane into the path of movement of the aforementioned second linkage means during the return stroke of the swing frame means while the second linkage means moves in said opposite direction so that the spacers will limit the movement of the second linkage means and will thus determine the axial position of the elongated member with respect to the swing frame means, so as to determine the extent to which the element is moved during the next working stroke of the swing frame means. selecting means are also provided which are driven by the drive means of the machine and which cooperate with the spacers for automatically selecting a plurality of spacers to be moved into the path of movement of the second linkage means so as to automatically determine the position of the aforementioned element during the next cycle.

The swing frame means are supported on the support means for turning movement about a predetermined axis and the first mentioned linkage means includes a link pivotally connected to the elongated member and depending on the number of spacers moved into the path of the second linkage means, the elongated member will be located at an axial position where the turning axis of the link of the first linkage means will coincide with the turning axis of the swing frame means or be located on one or the other side of the turning axis of the swing frame means. When the turning axis of the link of the first linkage means coincides with the turning axis of the swing frame means, the elongated member will be placed in an axial position where the first linkage means will transmit no movement to the element during the next working stroke of the swing frame means, while when the turning axis of the link with respect to the elongated member will be located on one side of the turning axis of the swing frame means with respect to the support means, the element will be moved in one direction, and when the turning axis of the link will be moved to the opposite side of the turning axis of the swing frame means, the element will be moved in opposite direction during each work ng stroke from the position it occupied during the immediately preceding cycle.

The automatic selecting means preferably include a perforated band operatively connected to the drive means of the machine to be advanced thereby and to be moved thereby toward the path of movement of the second linkage means, and a plurality of rod portions respectively fixed to and extending from the spacers into engagement with the band so that non-perforated portions thereof will engage rod portions which are not aligned with any perforations of the band to move automatically selected spacers into the path of movement of the above mentioned second linkage means.

The invention is hereinafter described in detail in connection with an embodiment in the form of a brushmaking machine, reference being made to the accompanying drawings, in which:

FIG. 1 is a perspective view of a brush-making machine seen from the front;

FIG. 2 is another perspective view of the machine;

FIG. 3 is still another perspective view of the machine;

FIG. 4 is a vertical section through the machine on line IVlV of FIG. 6;

FIG. 5 is a vertical section through the machine on line VV of FIG. 6;

FIG. 6 is a top plan view of the machine;

FIG. 7 is a side elevation viewed from the side on which the perforated band effecting the control is ar- Automatic 'three axially

displaceable control shafts

1, 2 and 3, Wheretive coupling elements 22 whereas a pin projectingsub- 3 ranged, "but which is omitted from the drawing for the sake of clearness;

FIG. 8 is a vertical section, on a larger scale, through the actual controlling elements on line Vlll-Vlil of FIG. 10; 5

FIG. 9 is a view showing these elements from the perforated band;

FIG. is a horizontal section taken on line X-X of FIG. 8, and

FIG. 11 is across section, on a larger scale, through the hydraulic holding device for the control shafts.

' If the invention is incorporated in a brush-making machine operating with a stationary drilling spindle, only carrying out forward and backward drilling movements, and a bristle inserting device, a brush wood carrier must be provided which is capable of three-dimensional displacement in relation to the drilling spindle and the bristle inserting device. The carrier must be movable in axial direction towards and away from the drilling spindle so as to attain the same depth of bore on the entire surface of the brush wood in spite of this wood being turned during the drilling of the holes. Then the brush wood carrier must also be movable in horizontal direction but at right angles to the direction mentioned above in order to enable the brush wood to be displaced in relation to the drilling spindle so far laterally that the point of the brush wood adjacent to the hole already drilled, is brought opposite the drilling spindle for drilling the next hole. The third dimension of displacement is then necessary in vertical direction so as to adjust the brush 30 wood in vertical direction in relation to the drilling spindle. V

The displacement of the brush wood carrier is, 1n the machine according to the present invention attained by by the control shaft 1 effects the shifting of a brush Wood carrier 7 in the direction of the drilling spindle (not shown in the drawings) with the aid of a bolt 8 (FIG. 6) arranged in an inclined slot 4 in a control member 5 and in a bracket 6. The control shaft 2 in being-shifted axially operates by means of a link 9 an elbow lever 10 carrying the brush wood carrier 7, which lever shifts the brush wood carrier 7 perpendicularly to carrier also perpendicularly to the drilling spindle but also in the plane of the drawing containing FIG. 6. Thus, the shafts 1-3 each form an element whose position is to be determined during each of the consecutive cycles of operation of the machine.

The three

control shafts

1, 2 and 3 are mounted axially shiftable' in a support means which includes two crossbeams 14 and .15 connecting two

side walls

12 and 13 of the machine, the bearings for each of the control shafts in the cross-beam 14 being each provided with a hydraulically actuated clamping shoe 16'so as to enable the

control shafts

1, 2 and 3 to be fixed in their new positions after adjustment. The actually required displacemtnt of each of the control shafits is effected by a connecting rod 17 which is connected at one end to an elongated member 19, and at the other end to a swing disk 21; .The three elongated members for the control shafts 1-3 are mounted in a common swing frame 18, each separately adjustable, and three disks 21 being mounted on a common axle 20.-

The swing discs 21 are respectively linked by curved connecting members 23 to coupling elements 22 which are respectively slidably arranged on the

control shafts

1, 2, 3, and which can be fixed in any adjusted position to the latter. The curved connecting members 23 are respectively hingedly connected at one end to the respecstantially normal from the other end of each connecting member 23, engages in a slot 24 of the respective swing disc. By adjusting the position of the coupling element 22 on the respective control shaft, the pin on the other end of the connecting member 23 will be moved in the slot 24 toward or away from the common axle 20 about which the swing discs 21 may pivot, so that depending on the position at which the coupling element 22 is fixed to the respective control shaft, a larger or smaller axial displacement of the respective control shaft will be obtained during pivoting of the respective swing disc 21 about the common axle 20 by means of the connecting rods 17 connected thereto.

The swing frame 18 is pivoted on the two side walls 12 V the intermediary of a lever 28 carrying a roller 27 and a link 29 connected to this lever 28, whereas a tension spring 31 shifts the swing frame 18 back into its initial position in the opposite direction to the arrow. In carrying out this turning movement through an angle of about the swing frame 18 entrains a bearing bolt 32 of the connecting rod 17 and thus imparts to the connecting rod 17 either a thrust moving it forward in the direction of its longitudinal axis or a corresponding pull towards the rear, according to whether its bearing bolt 32 is adjusted above or below an axis 33 about which the swing frame 18 turns. If the axis of the bearing bolt 32 coincides with the axis 33, the connecting rod 17 is not shifted at all in the direction of its longitudinal axis.

In order to obtain the desired or necessary thrust or rod 17 at each swing of the framewith the elongated member 19 into horizontal position the bearing pin 35 is raised through the intermediary of the link 34. In this position one or several plates of laminations 38 can be shifted in the direction of arrow 42 under the bearing pin 35, forming a support therefor, so that these laminations 38 then limit the downward movement of the bearing pin 35 eflfected by a lever 37. 7

It will be seen, from the above description, that the shaft 25 forms a drive means which acts through a transmission means on the elements 1-3. This transmission means'includes the cam 26 as Well as the. levers 28 and 29 and the swing frame means 18, as well as the elongated member 19 which is axially adjustable with respect to the swing frame means 18 and the linkage means formed by

elements

17, 21, 23 and 22 and interconnecting the elongated member 19 with the element whose plane shown in FIG. 8 to the horizontal plane shown also in FIG. 8 where the swing frame means is illustrated in dot-dash lines in this horizontal'plane and then along a return stroke during the same cycle back to the vertical plane where the swing frame means 18 is shown in solid lines in FIG. 8. The

elements

34 and 35 form a second linkage means movable in the vertical plane in response to turn-ing of the elongated member 19 with the swing frame means 18 first upwardly While the swing frame means 18 turns along its working stroke into the horizontal plane and then downwardly during the return stroke of the swing frame means 18. The plates or laminations 38 form a plurality of spacers located next to each other and guided for movement into the path of movement of the second linkage means 34, 35 during the return stroke of the swing frame means so that the spacers 38 will intercept and limit the movement of the second linkage means 34, 35 and will thus determine the axial position of the elongated member 19 with respect to the swing frame means .18. The perforated band 41 is advanced by the drive means in a manner described below and is bodily moved to the right and left, as viewed in FIG. 8. The band 41 cooperates with rod portions 40 of the spacers 38 to move only those rod portions which are aligned with non-perforated portions of the band, so that the band '41 together with the rod portions 41 form an automatic selecting means driven by the drive means for automatically selecting the number of spacers 38 to be moved in the path of the linkage means 34, 35. This selecting means and the spacers together form an automatic adjusting means for automatically adjusting the transmission means which transmits movement of the drive means 25 to the

element

1, 2, or 3 so that in this way the extent and direction of movement of the

element

1, 2 or 3 is determined.

The spacers or laminations 38 are slidable in a bed 39 which forms a guide means for the spacers 38 which are of different thicknesses, from 0.1 to 6.0 mm., at their front ends engaging under the bearing pins 35, so that by a suitable combination of several suitably chosen spacers 38 or of only one spacer it is possible to lift the bearing pin 35 and with it also the elongated member 19 by 0.1 to 24.0 mm. in any desired stages which only differ by 0.1 mm. By placing spacers with a thickness of O to 11.9 mm. beneath the bearing pins 35, a thrust, and by placing spacers with a total thickness of 12.1 to 24 mm. beneath the pins 35, a pull is exerted by the connecting rods 17 on the swing disks 21 and consequently on the

control shaft

1, 2 or 3. If the spacers 38 introduced have a thickness of 12.0 mm. the connecting rods 17 will not be displaced at all in their longitudinal direction. In this case the bearing bolt 32 of the connecting rod 17 will coincide with the axis 33 of the swing frame 18.

The appropriate operation of the spacers 38 so as to bring them alternately into the required working positions is effected by an endless perforated band 41. For this purpose the spacers 38 are each provided on their outwardly directed end with a rod 40. These rods 40 rest with their free ends against the endless perforated band 41. This perforated band 41 is moved to and fro transversely to its surface in working rhythm with the machine after being moved on one perforation each time. In so doing the band 41 shifts all the rods 40 of the spacers 38 in the direction of the arrow 42 in inward direction under the bearing pin 35 which are not opposite a hole in the perforated band. As the guide 43 carrying the perforated band 41 moves back, a comb 44 connected with the perforated band guide 43 brings the spacers 38 once more into their inoperative or initial position with the aid of collars 45 provided on the rods 40. Thin stationary plates are arranged between the individual movable spacers which plates keep the spacers apart and prevent the same from being unintentionally shifted by friction. These thin interposed plates are not shown in the drawings to render them more clear.

If, for example, as shown in FIG. 8, no spacer 38 is pushed under the bearing pin 35, the bearing bolt 32 of the connecting rod 17 is moved in the direction indicated by arrow 46 into the position 32' shown in dot-dash lines, after the simultaneous clamping of the elongated member 19, which is effected by a clamping shoe 48 arranged in the swing frame 18, and also by the operation of a clamping shoe 49 provided in the coupling element 22, at the same time releasing the clamping shoe or holding means 16 arranged in the cross-beam 14 for the control shaft 2 as the swing flame means 18 swings into its operative position 18'. The connecting rod 17 now assumes position 17', the swing disk 21 position 21' and the coupling element 22 position 22. This produces at the same time an axial displacement of the control shaft 2 by a distance b in the direction of arrow 47.

After this operation the clamping shoe 16 arranged in the cross-beam 14 is tightly clamped whereas the clamping shoes 48 and 49 are slackened and the return movement of the swing frame 18 into its initial position is initiated. Hereby the bearing bolt 32 of the connecting rod 17 also moves out of its position 32' back into its initial position 32, which causes a displacement of the coupling element 22 on the control shaft 2 by the distance b, but in this case in the opposite direction to the arrow 47.

If, however, during the lifting of the bearing pin 35, spacers 38 are slid thereunder as indicated in dotted lines in FIG. 8, both the bearing pin 35 and also the elongated member 19 can descend a lesser distance n. Thus the elongated member 19 with the bearing bolt 32 now comes into position 32" indicated in dotted lines, the connecting rod 17 into position 17", the swing disk 21 into position 21" and a bearing bolt 50 for the connecting piece 23 on the coupling element 22 into position 50. As the control shaft 2 has been previously clamped by the clamping shoe 16 provided in the cross-beam 14, the coupling element 22 is shifted on the control shaft 2 a distance a towards the right, without entraining the control shaft 2. The coupling element 22 as well as the elongated member 19 in the swing frame 18 are now hydraulically clamped by the clamping

shoes

49 and 48. Thereafter the clamping in the cross-beam 14 is released by loosening the clamping shoe 16. During the working movement of the swing frarne 18 out of its inoperative position into the position 18' which is now reached, the bear-ing bolt 32 for the connecting rod 17 moves out of the position 32" into position 32' indicated in dash lines, the connecting rod out of the position 17 into position 17" also indicated in dash lines, the swing disk 21 out of the position 21" into position 21' and the bearing bolt 50 on the coupling element 22 out of the position 50 into position 50", which results in an axial displacement of the control shaft 2 a distance b towards the left in the direction indicated by the arrow. So as to fix the control shaft 2 in its new position the clamping shoe 16 in the cross-beam 14 is then pressed on again. Thereupon the clamping shoe 49 in the coupling element 22 and the clamping shoe 48 in the swing frame 18 are also released. During the subsequent return movement of the swing frame 18 the bearing bolt 32 of the connecting rod passes out of the position 32" back into the position 32" and the bearing bolt 50 of the coupling element 22 out of the position 511" into the position 50'. At the same time the coupling element 22 is shifted on the control shaft 2 a distance b towards the right in the opposite direction to the arrow.

The clamping shoes are hydraulically operated for all three

control shafts

1, 2 and 3 together. This is effected positively by means of the driving shaft 25 which carries two

eccentrics

51 and 52 for this purpose (FIGS. 6 and 7). These eccentrics operate two pistons 53 and 54 mounted in

cylinders

55 and 56 filled with oil. The cylinder 55 is connected on the one hand by a pressure pipe 57 with three clamping shoes 49 in the coupling elements 22 through the intermediary of a distributor 58 and flexible pressure pipe 59 and on the other hand by a pipe 68 with the clamping shoes 48 for the bearing pistons 19 in the swing frame 18 through the intermediary of a bore 61 provided in the swing frame 18. The second cylinder 56, the piston 54 of which is actuated at a different time, is connected by a third pressure pipe 62 to the three clamping shoes 16 arranged in the cross-beam 14 for the

control shafts

1, 2 and 3. Adjustable overload safety devices of known construction can be fitted in the

pressure pipes

57, 59 and 62.

A clamping device is illustrated on a larger scale in FIG. 11 and hereinafter described in detail. For this purpose a clamping shoe such as that fitted in the cou- 7 pling elements 22 is chosen by way of example. In principle all the clamping shoes of these arrangements are alike. As can be seen from FIG. 11 the coupling element 22- has in addition to the bore for receiving the control shaft 2 a second bore 63 at right angles thereto and leading therein. In [this second bore 63 the'clamping shoe or connecting means 49 is mounted in such a manner that its ;concave bottom surface almost touches the control shaft 2. It is held in this position by a mushroom-shaped attachment 64 fixed to the connecting means 49 and resting on an annular flat spring 65 which in turn rests ona spring ring 66 inserted in a groove in the second bore 63.' The clamping shoe 49 is provided with an annular groove 67 above its concave clamping surface, and an O-Shaped ring 68 is placed in this groove as packing. The head of the mushroom-shaped attachment 64 has apertures 69 to allow oil to how in through a bore 70 in a screw plug 71.

The above-described clamping device operates in the following manner:

As the pipe is filled with oil from the

pressure cylinder

55 or 56 to the surface of the clamping shoe, the pressure produced b ythe piston 53 or 54 is transmitted to the upper surface of the clamping shoe 49. The latter is pressed thereby on to the control shaft 2 and holds it tight. When the pressure decreases the annular flat spring 65 assists in releasing the clamping shoe 49 from the control shaft 2. Owing to friction in the pipe, a relatively great delay might occur in removing the oil pressure and consequently the clamping effect.

As is apparent from the above description, the element 48 forms a connecting means for releasably connecting the elongated member 19 to the swing frame means 18 while the element 49 together with element 22 forms a connecting means for releasably connecting the linkage means 17, 21, 23 to the element 2, as shown in FIG. 8,

; means 16, and the drive means acts through the out-ofphase

cams

51 and 52 respectively on the pistons 53 and 54of the pair of hydraulic actuating means for simultaneously actuating the pair of connecting

means

48 and 49 and releasing the holding means 16 during the working stroke of the swing frame means 18 and for simultaneously disconnecting the pair of connecting

means

48 and 49 and operating .the holding means 16 during the return stroke of p the swing frame means 18.

To ensure quick and accurate working of the machine, additional measures are provided according to the invention. Thus for example, the levers 37 which effect the downward movement of the bearing pins 35 and also of the elongated members 19 through the intermediary i of the links 34 are mounted on a common axle 72 (FIGS.

4 and Their free end engage inthe spaces formed by the bearing pins 35 and the links establishing the connection with the respective elongated members 19. Below'the levers 37 but oscillatable on the same ax le 72 is a tensioning lever 73 which is actuated by an eccentric '74 arranged on the driving shaft 25 (FIGSQS, 6 and 7) through the intermediary of a lever 90 carrying a roller 83 and rotatably mounted at 89, the lever 90 being rendered operative through the intermediary of a connectingbar 75 and a transmission arm 76 provided on the tensioning lever 73; Between the tensioning lever 73 and the lever 37 an elastic connection is provided which consists of two pressure springs 78 and 79 mounted on a guide rod 77. These springs serve to attain a compensation in the possibility of movement of the levers 73 wand 37 accordingto whether a large or small number of spacers or even no spacer have been slipped under the bearing pin 35. The rod 77 is pivotally connected with the lever 37. The rod 77 can move in relation to the lever 73 in its longitudinal direction and thereby compress the spring 79 more or less according to how far the lever 37 can swing downwards. The object of the 'lever 37 is to causethe bearing pin 35 to accurately and quickly find the total height of the spacers slipped under it.

In order to prevent any blocking orjamming of the connecting rods 17 during the return movement of the swing frame 18 out of its operating position 18', especially when the bearing bolt 32 is located below the pivot axis 33 of the swing frame 1 8, a return stirrup 80 (FIG. 4) pivotable in the

side walls

12 and 13 is provided which, at the moment the elongated members 19 are released by the clamping devices, moves the connecting rods 17 by means of the projections 81 thereon through a swinging movement towards the left in the direction of arrow 82 and consequently into a position in which they are not blocked or jammed. The return stirrup 80 is also driven by an eccentric 83 on the driving shaft 25 which imparts the swinging movement to a lever 87 mounted on the return stirrup 80 through the intermediary of a two-armed lever 86 carrying a roller 84 and a set screw 85 The perforated band 41 is operated by the means hereinafter described-with reference to FIG. 5 of the drawings. The arrangement carryingthe perforated band 41 consists of a guide 43 which, for the purpose of adjusting the spacers 38, always carries out a movement in the direction of the arrow 42 and back again. is effected by another eccentric 91 mounted on the driving shaft 25 and which through the intermediary of a roller 92 controls a two-armed operating lever 94 pivoted at 93. One of the ends of a connecting bar or link 95 is con nected to the lower end of this operating lever 94 whereas the opposite end is hinged to a clamping clutch 96. This clamping clutch 96 is fixed and easily adjustable on a shaft 99 axially shiftable in

bearings

97 and 98. Shaft 99 carries at its outer end the guide 43 for the perforated band 41. A second shorter shaft 100 fixed to a bottom portion of the guide 43 and substantially equally spaced from the side edges thereof and slidable in a bearing 101, effects a parallel movement of the guide 43.

So as to move the perforated band 41 on after each working operation, a stub axle 102 (FIG. 6) is provided parallel to the driving shaft 25 and carries a gear wheel 103 meshing with a gear :wheel 104 on the driving shaft 25. On the inwardly directed end of the stub axle 102 an indexing disk 105 (FlG. 5) is arranged which carries a tripping pin 106. Below this indexing disk 105 a toothed wheel 107 is mounted on the guide 43 of the perforated band, which toothedwheel is turned one tooth at the end of each working cycle by the tripping pin 106. A locking pawl 108 then holds the toothed wheel 107 in the position it has actually assumed. Two feed wheels 110 are provided on an axle 109 carrying the toothed wheel 107 each feed wheel engages in a row of perforai of the rods 40, gives the perforated band 41 the necestions provided on the two sides of the perforated band 41 thereby moving the band on for the next working operation. A guide bar 111 screwedon to the guide 43 (FIG. 4) and provided with holes 112 for the passage sary guiding. V

The entire drive of the controlling arrangement for the brush wood carrier 7 is derived from the driving shaft 25 by means of six

eccentrics

26, 83, 74, 51 and 52 (FIGS. 4 and 5) mounted thereon and appropriately displaced in relation to each other, a working operation being completed at each revolution. of this driving'shaft 25, that is during this period a hole is drilled in a clamped brush wood and the corresponding hole in a second brush wood controlled in parallel to the first, is at the same time plugged with bristles.

The machine described above operates in the following manner:

The swing frame 18 is brought into its operative position 18' by the eccentric 26 (FIG. 8) through the intermediary of the lever 28 with its roller 27 and the link 29 and at the same time, by means of the eccentric 51 (FIG. 6) and the

pipes

60 and 57, both the clamping shoes 48 in the swing frame 18 clamp the elongated members 19 in position and the clamping shoes 49 in the coupling elements 22 clamp the

control shafts

1, 2 and 3 in their positions. Thus the connecting rods 17, through the intermediary of the swing disks 21 and the curved connecting pieces 23, impart to the

control shafts

1, 2 and 3 a corresponding axial displacement which effects the desired setting of the brush WOOd carrier 7, whereby the bearing pin 35 is raised at the same time so far by the link 34 that its underside is flush with the underside of the bearing block 36. At this point the eccentric 91 releases the lever 94 (FIG. 5 so that it is brought by a spring 113 into position 94 shown in dotted lines. As a result, the shaft 99 carrying the guide 43 for the perforated band 41 is moved in the direction of the arrow 42 through the intermediary of the link 95 and the clamping clutch 96. Thereby the perforated band 41 pushes in this direction all those rods 40 (FIGS. 8 to 10) opposite the ends of which there is no hole in the perforated band and thus brings the spacers 38 connected to these rods with their free ends of different thicknesses under the raised bearing pin 35-. This is the preparation for a fresh adjustment of the bearing bolt 32 of the connecting rod 17. The new adjustment serves for the next displacement of the respective control shafts 1, =2 and 3. This displacement takes place during the next working stroke, which occurs when the swing frame 18 swings out of its vertical into its horizontal position. The insertion of the spacers 38 takes place during the last portion of the working stroke. The feeling of the spacers is carried out while the frame 18 swings out of its horizontal back into its vertical position. It is terminated when the frame 18 has reached its vertical position. The feeling therefore takes place during the return or idle stroke. By utilizing the return or idle stroke of the frame 18 for the feeling the machine attains a high Working speed.

At the termination of the working stroke of the swing frame 18 (position 18) the eccentric 51 (FIG. 6) liberates the piston 53 which effects the release of the clamping devices in the swing frame 18 and in the coupling elements 22. Previously the eccentric 52 has brought into operation the clamping shoes 16 in the cross-beam 14 by actuat ing the pistons 54 through the pipe 62-. Consequently the

control shafts

1, 2 and 3 are fixed in the working positions they have assumed. During the subsequent return movement of the swing frame 18 into its initial position the arm 76, actuated by the eccentric 74 through the intermediary of the lever 90 and the link 75, presses the spring 79 as well as the rod 77 with the lever 37, and the bearing pin 35 with the elongated member 19 on to the inserted spacers 38. The number and the thickness of the spacers 38 pushed in by the perforated band 41 determine the magnitude of the downward movement of the elongated member 19 and consequently also the position of the bearing bolts 32 for the connecting rods 17 in relation to the pivot .axis of the swing frame 18, which is the determining factor for the axial forward movement of the

control shafts

1, 2 and 3 during the next Working stroke of the swing frame 18, because the clamping elements 22 are shifted on the control shafts accordingly by the connecting rods 17. At the end of the return movement of the swing frame 18 the feeling operation is likewise terminated. The clamping shoes 49 and 48 in the coupling element 22 and the swing frame 18 are then pressed on and the clamping shoe 16 in the cross-beam 14 is Subsequently released. Thereupon the next working stroke of the swing frame 18 commences and is enacted in a similar manner.

The feeding mechanism according to the invention can be incorporated in an analogous manner to that described above for a brush-making machine, in any other machines in which it is a question of adjusting one or several mechanical elements simultaneously or successively according to a predetermined working program, either continuously or in steps at relatively long or even minutely short intervals.

Of course, various changes may be made in the details disclosed in the foregoing specification without departing from the invention and the claims annexed hereto.

I claim:

1. In a cyclically operating machine which, during operation, carries out consecutive cycles of operation, in combination, an element whose position is to be determined during each of the consecutive cycles of operation of the machine; support means supporting said element for movement so that it can occupy different positions during the consecutive cycles of operation; drive means; adjustable transmission means operatively connected to said drive means and to said element for transmitting movement of the drive means to said element to move the latter from one position which it occupies during at least part of one cycle to another position which it occupies during at least part of the next cycle, said transmission means being adjustable to difierent extents for determining the extent to which said transmission moves said element, and said transmission means being driven by said drive means during each cycle along a working stroke and a return stroke; automatic connecting means automatically connecting said transmission means to said element during said working stroke of said transmission means and disconnecting said transmission means from said element during said return stroke of said transmission means so that said element can be moved by said transmission means only during said working stroke thereof at each cycle; automatic holding means cooperating with said element for holding the same stationary during said return stroke of said transmission means during each cycle; and automatic adjusting means driven by said drive means and cooperating with said transmission means for adjusting the latter during said return stroke thereof at each cycle of operation according to a predetermined program; so that the adjustment of said transmission means during one cycle determines the position to which said transmission means moves said element during the Working stroke of said transmission means at the next following cycle.

2. ha machine as recited in claim 1, said holding means cooperating with said drive. means to be driven thereby.

3. In a cyclically operating machine which, during operation, carries out consecutive cycles of operation, in combination, an element whose position is to be determined during each of the consecutive cycles of operation of the machine; support means supporting said element for movement so that it can occupy different positions during the consecutive cycles of-operation; drive means; adjustable transmission means operatively connected to said drive means and to said element for transmitting movement of said drive means to said element to move the latter from one position which it occupies during at least part of one cycle to another position which it occupies during at least part of the next cycle, said transmission means being adjustable to different extents for determining the extent to which said transmission means moves said element, and said transmission means being driven by said drive means during each cycle along a working stroke and a return stroke, said transmission means including a pair of members one of which is adjustable with respect to the other; automatic adjusting means driven by said drive means and cooperating with said transmission means for adjusting said one member with respect to said other member during said return stroke of said transmission means at each cycle of operation according to a predetermined program, so that the adjustment of said transmission means during its return 1 l stroke in one cycle determines the position to which said transmission means moves said element during the working stroke of said transmission means in the next followting cycle; first connecting means cooperating with said transmission means and said element for connecting said transmission means to said element and for disconnecting said transmission means-from said element; second connecting means cooperating with said pair of members of said transmission means for connecting said members to each other for movement together and for disconnecting said one member from said other member; and actuating means driven by said drive means and cooperating with both of said connecting means for simultaneously actuating the same to connect said transmission means to said element and said pair of members to each other during the working stroke of said transmission means at each cycle and for simultaneously actuating both of said connecting means to disconnect said transmission means from said element and said one member from said other member during the return stroke of said transmission means at each cycle.

4. In a machine as recited in claim 3, said actuating means operating with a fluid under pressure on both of said connecting means to actuate the same.

5. In a machine as recited in claim 3, releasable holding means cooperating with said element for holding the same stationary during said return stroke of said trans mission means at each cycle and releasing said element for movement during the working stroke of said trans missionmeans at each cycle.

6. In a machine as recited in claim 5, second actuating means driven by said drive means and cooperating with said holding means for actuating the same to hold said element stationary and to release said element for movement.

7. In a machine as recited in claim 6, both of said actuating means operating with a fluid under pressure and being driven in out-of-phase relation with respect to each other by said drive means.

8. In a'cyclically operating machine which, during operation, carries out consecutive cycles of operation, in

combination, an element whose position is to'be determinedduring each of the consecutive cycles of operation of the machine; support means supporting said element .for movement so that it can occupy difierent positions during the consecutive cycles of operation; swing frame means. supported for turning movement by said support means; an elongated member supported for axial movement by said swing frame means and carried by said swing. frame means for turning movement therewith; drive .means' operatively connected to said swing frame means for turningthe latter during each cycle from a first plane along a working stroke to a second plane and from said second plane along a return stroke to said first plane; linkage means connecting said elongated member to said element so that the extent towhich the latter is moved by said linkage means is determined by the axial position of said elongated member with respect to said swing frame; second linkage means located in said first plane I and .operatively connected to said elongated member to be moved thereby in one direction in said first plane when 'said swing frame means turns along said working stroke :thereof and in an opposite direction in said first plane when said swing frame means moves along said return stroke thereof; a plurality of spacers located next to each other; guide means guiding said spacers for movement perpendicularly to said first plane into the path of movement of said second linkage means during the return stroke of said swing frame means while said second linkage means" moves in said opposite direction so that said spacers will limit themovement of said second linkage means and will thus determine the axial position of said elongated member with respect to. said swing frame means so as to determine the extent to which said element is moved during the next working stroke of said swing frame means; and automatic selecting means driven by'said drive means and cooperating with said spacers for automatically selecting the number of spacers to be moved into said path so as to automatically determine the position of said element during the next cycle.

9. In a machine as recited in claim 8, said support means supporting said swing frame means for turning movement about a predetermined axis and said first-mentioned linkage means including a link pivotally connected to said elongated member, a' given number of said' spacers cooperating with said second linkage means to locate said elongated member at an axial position where the turning axis of said link with respect to said elongated member coincides with the turning axis of said swing frame means with respect to said support means, so that when said automatic selecting means selects said given number of spacers for movement into the path of movement of said second linkage means said elongated member will be placed in an axial position where said first-mentioned linkage means will transmit no movement to said element during the next working stroke of said swing frame 7 means.

10. In a machine as recited in claim 9, said plurality of spacers having a total number greater than said given number so that when said automatic selecting means selects a number of spacers greater than said given number the turning axis of said link with respect to said elongated member will be located on one side of the turning axis of said swing frame means with respect to said support means while when said automatic selecting means selects a number of spacers less than said given number the turning axis of said link with respect to said elongated member will be on the opposite side of said turning axis of said swing frame means with respect to said support means, so that in accordance with the selection made by said automatic selecting means said element will remain in the position it occupied during the immediately precedingcycle or Will be moved in one of a pair of opposed directions from the position it occupied during the immediately preceding cycle.

11. In a machine as recited in claim 8, said automatic selecting means including a perforated band operatively connected to said drive means to be advanced thereby and to be bodily moved thereby toward said path of movement of said second linkage means, and a plurality of rod portions respectively fixed to and extending from said spacers into engagement with said band so that nonperforated portions thereof will engage rod portions which are not aligned with any perforations of said band to move automatically selected spacers into said path.

References Cited in the file of this'patent UNITED STATES PATENTS 787,875 Creed Apr. 18, 1905 1,059,880 Kobler Apr. 22, 1913 1,139,506 Eggart May 18, 1915 2,034,598 Scheibel Mar. 17, 1936 2,548,738 Orlich et al Apr. 10, 1951

Claims

1. IN A CYCLICALLY OPERATING MACHINE WHICH, DURING OPERATION, CARRIES OUT CONSECUTIVE CYCLES OF OPERATION, IN COMBINATION, AN ELEMENT WHOSE POSITION IS TO BE DETERMINED DURING EACH OF THE CONSECUTIVE CYCLES OF OPERATION OF THE MACHINE; SUPPORT MEANS SUPPORTING SAID ELEMENTS FOR MOVEMENT SO THAT IT CAN OCCUPY DIFFERENT POSITIONS DURING THE CONSECUTIVE CYCLES OF OPERATION; DRIVE MEANS; ADJUSTABLE TRANSMISSION MEANS OPERATIVELY CONNECTED TO SAID DRIVE MEANS AND TO SAID ELEMENT FOR TRANSMITTING MOVEMENT OF THE DRIVE MEANS TO SAID ELEMENT TO MOVE THE LATTER FROM ONE POSITION WHICH IT OCCUPIES DURING AT LEAST PART OF ONE CYCLE TO ANOTHER POSITION WHICH IT OCCUPIES DURING AT LEAST PART OF THE NEXT CYCLE, SAID TRANSMISSION MEANS BEING ADJUSTABLE TO DIFFERENT EXTENTS FOR DETERMINING THE EXTENT TO WHICH SAID TRANSMISSION MOVES SAID ELEMENT, AND SAID TRANSMISSION MEANS BEING DRIVEN BY SAID DRIVE MEANS DURING EACH CYCLE ALONG A WORKING STROKE AND A RETURN STROKE; AUTOMATIC CONNECTING MEANS AUTOMATICALLY CONNECTING SAID TRANSMISSION MEANS TO SAID ELEMENT DURING SAID WORKING STROKE OF SAID TRANSMISSION MEANS AND DISCONNECTING SAID TRANSMISSION MEANS FROM SAID ELEMENT DURING SAID RETURN STROKE OF SAID TRANSMISSION MEANS SO THAT SAID ELEMENT CAN BE MOVED BY SAID TRANSMISSION MEANS ONLY DURING SAID WORKING STROKE THEREOF AT EACH CYCLE; AUTOMATIC HOLDING MEANS COOPERATING WITH SAID ELEMENT FOR HOLDING THE SAME STATIONARY DURING SAID RETURN STROKE OF SAID TRANSMISSION MEANS DURING EACH CYCLE; AND AUTOMATIC ADJUSTING MEANS DRIVEN BY SAID DRIVE MEANS AND COOPERATING WITH SAID TRANSMISSION MEANS FOR ADJUSTING THE LATTER DURING SAID RETURN STROKE THEREOF AT EACH CYCLE OF OPERATION ACCORDING TO A PREDETERMINED PROGRAM, SO THAT THE ADJUSTMENT OF SAID TRANSMISSION MEANS DURING ONE CYCLE DETERMINES THE POSITION TO WHICH SAID TRANSMISSION MEANS MOVES SAID ELEMENT DURING THE WORKING STROKE OF SAID TRANSMISSION MEANS AT THE NEXT FOLLOWING CYCLE.