|Publication number||US3807460 A|
|Publication date||Apr 30, 1974|
|Filing date||Oct 12, 1972|
|Priority date||Oct 12, 1972|
|Publication number||US 3807460 A, US 3807460A, US-A-3807460, US3807460 A, US3807460A|
|Inventors||Alexandr A, Anatoly P|
|Original Assignee||Alexandr A, Anatoly P|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (4), Referenced by (12), Classifications (5)|
|External Links: USPTO, USPTO Assignment, Espacenet|
United States Patent [191 Alexandr et al. l
' Apr. 30, 1974 HEALD MOTION FOR LOOMS  Inventors: Alexandrovich Kazurov Alexandr, 3 Linia, l3, kv. 175; Petrovich Topilin Anatoly, ulitsa Jsjurupy, l2 korpus l, bothof Moscow, U.S.S.R.
22 Filed: Oct. 12, 1972 21 Appl. No.: 296,752
 US. Cl. 139/76  Int. Cl. D03c 1/12  Field of Search 139/55, 57, 66, 76, 77
 References Cited UNITED STATES PATENTS 3,101,745 8/l963 Pfarrwaller 139/66 3,228,427 l/l966 Honegger 139/66' 3,557,842 l/l97l Porter 139/55 FORElGN PATENTS OR APPLICATIONS 1,945,034 3/ l97l Germany 139/76 Primary Examinerl-lenry S. Jaudon Attorney, Agent, or Firm-Holman & Stem ABSTRACT In the heald motion of looms there are provided paired shedding cams, each pair being loosely mounted on a hollowshaft independent of others so as to be capable of periodically rotating about it with the aid of a clutch with rotary keys. One half-clutch is constantly associated with the main shaft of the loom, and the other one is associated with the paired cams and which periodically engages the main shaft through said keys which are turned from a program carrier through a control mechanism.
'6 Claims, 25 Drawing Figures Pmmmmmw 3.801.460
' sum 03 0-13 PATENTEDAPWWW 518073160 SHEET 070F13 I 9ATENTEDAPR30 1914 3.807 460 SHEET 08 [1F FIE. 12
msmsnm so new SHEET 11 0F l3 PATENTEDAPR 36 I974 SHEET PATENTED A R 3 0 I974 SEMI 13 1F 13 FIG, 25
HEALD MOTION FOR LOOMS The present invention relates to weaving machines, and more exactly to the heald motions utilized "in these machines.
The present invention may be most effectively employed in high-speed looms.
Heald motions are presently known which comprises shafts with healds for the passage therethrough of the warp threads forming the shed, each heald shaft being reciprocated alternately in the vertical plane and dwelt by a pair of profiled shedding cams mounted on a cam shaft which act through a system of levers and links with, the paired cams being rigidly connected to each other, and with the succession of the movement of the heald shafts depending on the profile of these cams. In these looms, the cams are made for four, five, six, seven, and eightpicks with, the weaving being repeated accordingly to four, five, six, seven and eight weft threads. Any further increase of the weaving repeat is impossible because of the so-called undercutting" of the cams, i.e. formation of cam profile sections having a very small radius of curvature which involves concentrations of contact stresses.
The repeat of pattern can be increased by extending the dwell diameter of the cams. But this results in the growth of the overall dimensions of the mechanism as a whole while the repeat is insignificantly widened thereby.
Also there are heald motions known in the art which have lift dobbies in the form of hooks and knives which enable the variety of manufactured fabrics to be considerably widened due to the unlimited weaving repeat. However, these mechanisms feature large impact loads in the dobby members because of the wide clearances which are necessary to change over the basic working elements of the dobby (knives-hooks and hooks-rests). Said clearances in these mechanisms may be smoothly taken up by a special means, but the latter complicates the design of the dobby and makes it costly.
The principal object of the present invention is to provide a high-speed heald motion wherein the drive of the shedding cams would be so improved as to enable this motion to produce fabrics with an unlimited pattern repitition and, at the same time eliminating any impact loadsin the motion thereof.
With this and other objects in view, a heald motion comprising shafts with healds for'the passage of the warp threads therethrough forming the shed, each heald shaft being alternately reciprocated in the vertical plane and dwelt by a pair of profiled cams mounted on a cam shaft which act through a system of levers and links and, according to the invention, each paired cam has a seating hole with segmental cutouts which is freely mounted on the shaft independently of the other cams, so that it is capable of periodically rotating about the shaft by means of a clutch with rotary keys, one half-clutch thereof being in constant driving connection with the main shaft of the loom, while the other half-clutch is engaged with the paired cam which periodically comes into driving connection with the main shaft by way of said keys which are turned by means of a program carrier through a control mechanism, and, according to the invention, each paired cam has a means with which to fix it on the shaft in a position corresponding to the dwell of the heald shaft. Such a design allows for the production of fabrics with an unlimited pattern repitition, since each shedding cam is kinematically associated with its respective heald shaft and has a separate drive.
Advantageously, the shaft of the shedding cams should be made hollow, and the means with which to fix them onto said shaft should comprise springed blocks located inside this shaft which carry rollers that contact the seating hole of the cam and fill the segmental cutouts of this cam, the shedding cams in their fixed position on said shaft being capable of oscillating within an angle of the cam profile which corresponds to the dwell of the heald shaft. The oscillation of the cams provides for improved dynamics of in their engagement and disengagement processes, i.e. for with the absense of impact loads within these time periods.
The oscillation of each of the shedding cams should advisably be effected through the medium of a pivoted rocker which interacts with the other cams and the arms whereof are attached to links whose free ends are hinged to a flange affixed on the end face of the hollow shaft of the shedding cams. Due to such an embodiment, the speeds of the half-clutches, the shedding cams and the fixing means are levelled off just before the changeover, and hence the impact loads are excluded in the operation of such a motion.
, In order to achieve a secure operation, it is expedient to use a clutch having rotary keys, wherein the halfclutch connected to the main shaft of the loom comprises a cylindrical body rotatably mounted on an axle and provided with shoulders and wells for the rotary keys fitted with toothings whereby these keys are kept in internal engagement with a changeover gear seated on one of said shoulders and having outer recesses to accommodate a roller for the control mechanism, while the other half-clutch is made as a gear with segmental cutouts formed in its seating hole, this gear being seated on the other shoulder of said body, and meshing with another gear which is placed between the shedding cams and is connected thereto through a flattened pm.
Said control mechanism comprises cams mounted on a drive shaft so as to interact with the rollers, and a frame carrying said rollers and also a bar to which a springed rod is hingedly secured carrying the roller that at some of the intervals enters the recesses of the changeover gear, and a three-arm lever through which a movable stop is associated with the program carrier.
Such an embodiment improves the operational dynamics of the program carrier and provides the appropriate force necessary to turn the keys of the clutch.
In order to reduce the size and weight of the movable parts, as well as to improve the operationaldynamics, the program carrier should advantageously comprise a drum mounted in guides so as to be capable of reciprocatory motion in a plane normal to that of the motion of the heald shafts, this drum being reciprocated from a double-track cam and having pins for drawing a punched tape whose holes accommodate readout needles, which needles are placed in a block, with their free ends abutting against bracket-mounted plates each carrying a lug that interacts with the respective threearm lever of the control mechanism, said drum being at its edges and provided with toothings one of which interacts with a toothed sector mounted on an axle so that it can be swung from said double-track cam.
For a better appreciation of the invention, the particular exemplary embodiment thereof with referen-ces to the appended drawings are discussed herein below, wherein:
FIG. 1 shows the proposed heald motion for one heald shaft and its driving connection with this heald shaft;
FIG. 2 shows the drive of each pair of shedding cams, partially in section;
FIG. 3 shows the body of the clutch with rotary keys used in the shedding cam drive;
FIG. 4 shows the control mechanism serving to turn the keys of the clutch illustrated in FIG. 3, partially in section;
FIG. 5 shows the program carrier of the proposed motion which sets the repeat of pattern, partially in sectron;
FIG. 6 same as in FIG. 5, side view;
FIG. 7 shows the program carrier drum with a punched tape;
FIGS. 8 and 9 show the means to locate the drum relative to the readout needles, partially in section;
FIG. 10 shows the mechanism for drawing the punched tape on the drum;
FIG. 11 is a cyclogram of the heald motion operation;
FIG. 12 is a diagram of the variation of angular rates in and to;
FIGS. 13, l4, l5, 16, 17, 18, 19, 20, 21, 22, 23, 24 show the various positions of the changeover clutch of the shedding cams and of their fixing means during the rise, dwell, and fall of the heald shafts in the proposed heald motion;
FIG. 25 shows a punched tape with a particular repeat of pattern.
The design of the heald motion is further described.
The heald motion comprises shafts 1 (FIG. I) with healds 2 for the passage therethrough of the warp threads 3. Each heald shaft 1 moves in the vertical plane from a pair of profiled cams 4 (FIG. 2) mounted on a hollow shaft 5. Motion to the heald shafts is communicated from the cam 4 through rollers 6 secured on a lever 7 swivelling on a pivot 8. Articulated to this lever is a link 9 which is hinged to a double-arm lever 10. This lever is in turn hinged to a link 11 through which a drawbar 12 (FIG. 1), double-arm levers 13, links 14, and drawbars 15 is associated with the heald shaft 1.
The shedding cams 4 (FIG. 2) are fitted with a means 16 for fixing them to the shaft 5, and have a separate drive comprising a clutch 17 with rotary keys 18. These keys are turned from a program carrier 19 through a control mechanism 20.
DETAILED DESCRIPTION OF THE MOTION UNITS Each of the shedding double cams 4 has a seating hole 21 with segmental cutouts 22, and are loosely mounted on the shaft 5 independent of the other cams so as to be capable of periodically rotating about it through the medium of the clutch 17, thus securing movement of the heald shaft 1 in the vertical plane. The clutch 17 has two half-clutches, one of which is constantly associated with the main shaft of the loom, and the other one is so associated with the double cam 4 and periodically comes into driving connection with the main shaft through the keys 18. The half-clutch constantly associated with the main shaft of the loom is made as a cylindrical body 23 secured on an axle 24 and provided with shoulders 25 and 26 (FIG. 3) and wells 27 accommodating the rotary keys 18 which permanently remain in these wells (in the drawing, the keys are moved out from the wells for better visualization). The keys 18 are fitted with toothings 28 whereby they are kept in internal engagement with a changeover gear 29 (FIG. 2). This gear is seated on the shoulder 25 of the body 23 and has outer recesses 30 to accommodate a roller 31 of the control mechanism 20.
On the inner surface of the gear 29 there are provided recesses 32 to receive the springed roller locators 33 serving to fix this gear.
The body 23 is, through a gearing 34, connected to an intermediate drive shaft 35 which by way of a chain transmission 36 and a shaft 37 is linked to the main shaft of the loom (not shown).
The other half-clutch is a gear 38 with segmental cutouts in its seating hole which is mounted on the shoulder 26 (FIG. 3) of the body 23 and meshes with another gear 39 (FIG. 2) placed between the paired cams 4 and connected thereto by a flared pin.
The means 16 fixing the paired cams 4 on the shaft 5 in a position appropriate to the dwell of the heald shaft 1 comprises spring-loaded blocks 40 disposed inside the shaft 5 and carrying rollers 41 which contact the seating hole 21 of the cam 4 and entering the segmental cutouts 22 of this cam.
The cams 4, in their fixed position on the shaft, are capable of oscillating within the cam profile angle appropriate to the dwell of the heald shaft, so as to level off the speeds of the half-clutches, shedding cams, and the fixing means just before the changeover.
The cams 4 are oscillated by means of a rocker 42 secured on a pivot 43, its arms being hinged to links 44. The free ends of these links are hingedly attached to a flange 45 fixed on the end face of the hollow shaft 5.
The rocker 42 swings on the pivot 43 through the medium of rollers 46 which are in permanent contact with the profiled cams 47 mounted on the shaft 35.
The control mechanism 20 comprises a frame 48 (FIG. 4) held in bearings 49 and carrying rollers 50 which interact with cams 51 placed on the shaft 35. Mounted on a crosspiece 52 of the frame 48 is a swinging bar 53 which, through a slide hinge 54, is connected to a springed rod 55 carrying the roller 31. As the rod 55 moves in slots 56 of a plate 57, the spring 58 tend to shift it to the uppermost position wherein the axis of the hinge 54 is aligned with that of the bearings 49. The bar 53 through another hinge 54a is linked to a threearm lever 60 which interacts with a movable stop made in the form of a plate 61 having a lug 62.
The program carrier 19 comprises a perforated drum 63 (FIG. 5) mounted in cylindrical recesses of a slide 64 which has slots in its sides. By means of these slots, the slide 64 is together with a drum 65 held in guides 65 so as to be capable of reciprocatory motion in a plane normal to that of the motion of the heald shafts. Such motion is communicated to the drum from a double-track cam 66 seated on the shaft 35, its track 67 interacting with a roller 68 mounted on a lever 69 is pivotable about an axle 70. The lever 69 is forked, as shown in FIG. 6. Secured on the ends of this fork are trunnions 71 links 72 attached thereto. These links are made through pivots 73 and connected to the slide 64.
The drum 63 has pins 74 (FIG. 6) to draw a punched tape 75 (FIG. 7) which defines the pattern repitition. Received by holes 76 of the tape 75, as well as the holes of the drum 63, are readout needles 77 (FIG. 5) which are held in a block 78 disposed between the guides 65. On one side the needles 77 abut against a check plate 79 and, on the other side, against the ends of the plates 61 mounted a bracket 80. The plates 61 are covered on by a strap 81 on top, and at the opposite end they have a spring 82 that tends to shift the plates 61 toward the readout needles 77.
The drum 63 has toothings 83 at its edges, one of which interacts with a toothed sector 84 seated on an axle 85 which is capable of swinging. The swinging of the sector 84 is effected from a track 86 of the doubletrack cam 66 by means ofa roller 87 secured on a lever 88 pivotable on an axle 89. Fixed on the end of the lever 88 is a trunnion 90 carrying a link 91. The latter is, through a pin 92, connected to a crank 93 fixed on the axle 85.
In order to stabilize the position of the drum 63 relative to the needles 77 and the toothed sector 84, a locating means is provided in the slide 64. This means comprises rods 95 (FIGS. 8, 9) with springs 94 which at their ends a carrying block 96. Secured to this block is a locating pin 97. The rods 95 are movably placed in the holes of the slide 64.
In order to improve the conditions for drawing the punched tape (i.e. to increase the angle of contact be tween the tape 75 and thedrum 63) rubberized rollers 99 are, provided on the slide 64 with the aid of axles 98 (FIG. 10), while the loose side of the punched tape 75 is supported by a roll 100 which can be spaced at will relative to the drum 63.
The gear 38 is provided .with segmental cutouts 101 for its interaction with the rotary keys 18.
FIG. 11 shows the cyclogram, wherein line I illustrates the operation of the control mechanism 20, viz. the motion of the three-arm lever 60, line II' the reciprocatory motion of the drum 63, line Ill the swinging motion of the toothed sector 84, and line IV the motion of the heald shafts 1.
ACTION OF THE MOTION Upon rotation of the drive shaft 35 (FIG. 2), the body 23 of the changeover clutch 17 together with the rotary keys 18 and the changeover gear 29 are, through the gearing 34 (having a reduction ratio of 1:4), given rotation about the axle 24 at a rate four times less than that of the drive shaft 35. Besides, during the rotation of the drive shaft 35, the cams 47 set the rocker 42 into swinging motion through the links 44 transmitted to the flange 45, and then through the springed locators 16 with the rollers 41, to the shedding cams 4. This oscillation of the shedding cams is not transmitted to the heald shaft 1, since it occurs within the cam profile angle appropriate to the dwell of the heald shaft 1. The oscillation of the shedding cams 4 is, through the gear 39, and transmitted to the gear 38 of the changeover clutch. Thus, the speed of the gear 38 with respect to the body 23 of the changeover clutch constitutes a variable quantity that at any instant equals the difference between the rotational speed of the body 23 and the speed of the swinging motion of the gear 39.
The cams 47 mounted on the drive shaft 35 are so profiled that, at a certain instant of the cycle, viz. at the changeover moment, the speeds of the body 23 and of the gear 38 in the clutch 17 should equalize. In this case, the relative speed of these two members will be zero.
Shown in FIG. 12 is a diagram for the variation of the angular rates to and m with an angle 4 d), where w is the angular rate of rotation of the clutch body 23, w the variable angular rate of oscillation of the shedding cams 4, the hollow shaft 5, and the gear 38, and 4 (15 is the angle of rotation of the drive shaft 35.
Further, the rotation of the drive shaft 35 (FIG. 4) through the cams 51 and the rollers causes a swinging motion of the frame 48 about its bearings 49. The bar 53 swings about the hinge 54 of the rod 55, and the three-arm lever 60 swings about its pivot 59. In this case the roller 31 of the rod is in its uppermost position and does not act on the changeover gear 29.
Besides, the drive shaft 35 rotates the double-track cam 66 (FIG. 5). Its track 67 through the kinematic chain of the elements 68, 69, 71, 72, 73, and 64 sets the perforated drum 63 in reciprocatory motion. The track 86 of this cam through the elements 87, 88, 90, 91, 92, and 93 brings into swinging motion the toothed sector 84. The tracks 67 and 86 are so profiled that in one of the extreme positions one of the toothings 83 of the perforated drum 63 engages the sector 84, whereupon the sector 84 performs its working stroke, thereby turning the drum 63 and moving the punched tape 75 one pitch further. Next, the perforated drum 63 moves back toward the readout needles 77, and is in the meantime fixed by the locator 97, while the punched tape 75 presses on the readout needles 77 which in turn shift the plates 61 with the lugs 62. After the toothing 83 of the perforated drum 63 disengages the sector 84, the latter performs its idle stroke.
When the heald shaft 1 dwells in the upper or lower positions for the several operating cycles of the loom, the clutch body 23 with the changeover gear 29 and the rotary keys 18 rotate about the axle 24, while the gear 38 loosely seated on the shoulder 26 of the body 23 swings about the same axle 24. This swinging motion is imparted to the clutch gear 38 from the shedding cams 4 connected with the hollow shaft 5 through the locators 16. As was said above, the oscillating motion of the shedding cams 4 is not transmitted to the lever 7 with the rollers 6. Thus, the heald shaft dwells for the requisite number of operating cycles of the loom which is defined by the program of the pattern.
Shown in FIGS. 13, 14, l5, 16 are the positions taken by the members of the heald motion during the dwell of the heald shaft 1 in its lower position for several operating cycles of the loom.
In order for the heald shaft 1 to change its position in the next operating cycle of the loom, say, to shift from the lower position to the upper one, the shedding cams 4 must be engaged and turned a quarter revolution. This is possible if a hole is provided in the respective track of the punched tape. In this case, as the perforated drum 63 moves toward the readout needles, the respective needle 77 runs into the hole 76 of the punched tape 75, where it remains at rest, while the lug 62 of the plate 61 turns out to be located in the line of action of the three-arm lever of the control mechanism 20. With such a position of the plate 61, the threearm lever becomes immovable (locked). Now, as the frame 48 of the control mechanism rises, the bar 53 swinging about the hinge 54a of the three-arm lever 60 moves the rod 55 downwards. The roller 31 now enters the recess 30 of the changeover gear 29 and thus stops it. From this moment on it starts the process of engagement of the shedding cams.
Shown in FIGS. 17, 18, 19 are various stages of the engaging process of these cams.
When the changeover gear 29 is stopped, the rotary keys 18 entrained by the clutch body 23 are turned in their wells 27 by the gearing 34 at a reduction ratio of 1:8 in the direction shown by arrow A, so that they enter the segmental cutouts 101 of the gear 38 of the changeover clutch 17. As the rotary keys 18 turn by a quarter revolution, their surface contacts the surface of the segmental cutouts 101 of the gear 38.
Since by this time the speed of the gear 38 relative to the body 23 will be zero and, these members will contact each other without an impact. From this time on the gear 38 will move together with the body, and the speed of the shedding cams 4 relative to the hollow shaft will being gradually increasing. The roller 41 of the locator 16 comes out of the segmental cutout 22 of the shedding cams 4 compressing the springs through the blocks 40.
Rotation ofthe keys 18 ends as they turn halfa revolution, thus completely filling the segmental cutouts 101 of the gear 38. The frame 48 of the control mechanism will at this moment be in its lowermost position, and the roller 31 will emerge from the recess 30 of the changeover gear 29.
Now starts the rising process of the heald shaft, with the various stages of which are shown in FIGS. and 21.
It should be noted that the changeover process occurs at a time when the rollers 6 of the levers 7 are located within the profile sections of the shedding cams 4 that correspond to the dwell of the heald shafts, and the line of action of normal pressure (between the cam and the roller) passes through the axis of rotation of the shedding cams 4, thus causing no torque.
After the frame 48 of the control mechanism takes its lowermost position, and the three-arm lever 60 stops acting on the lug 62 of the plate 61, the perforated drum 63 carrying the punched tape 75 starts its movement toward the toothed sector 84. As its toothing 83 engages the toothed sector 84, the drum 63 is unfixed (unlocked), and the sector 84 turns the drum 63 placing the next card in the line of action of the readout needles 77. In order for the heald shaft to be able to dwell in the upper position for several operating cycles of the loom, the shedding cams 4 must be disengaged. For this purpose the latter card of the tape should have a hole in the track appropriate to the heald shaft under consideration. In this case, at the moment the shedding cams start to disengage, the lug 62 of the plate 61 will proceed just as in the preceding cycle for location in the line of action of the three-arm lever 60. During the rise of the frame 48 of the control mechanism the roller 31 will enter the recess of the changeover gear 29. At this moment, the process of disengaging the cams 4 will start.
In FIGS. 22, 23, 24 are the various stages of the disengagement process of the shedding cams are shown.
By this time, the shedding cams 4 having turned a quarter revolution will finish lifting the heald shaft, and
the rollers 6 of the levers 7 will be located in the profile sections corresponding to the heald shaft dwell in the upper position. The speed of the shedding cams 4 relative to the hollow shaft 5 smoothly drops, and at the moment the rotary keys complete a quarter revolution it becomes zero. At the same moment, the rollers 41 of the locator 16 under the pressure of springs will completely fill the segmental cutouts 22 of the shedding cams 4. Thus, the process of fixing the shedding cams 4 with respect to the hollow shaft 5 will again cause no impacts. Thereupon the speed of the shedding cams 4 moving together with the hollow shaft 5 will reduce smoothly, whereas the speed of gear 38 relative to the clutch body 23 will start increasing.
The rotation of the keys 18 ends as they turn half a revolution and their slots are flush with the shoulder 26 of the clutch body 23. By this time, the roller 31 of the control mechanism will have left the recess 30 of the changeover gear 29 and start to rotate together with the clutch body 23.
If according to the interlacing pattern as shown in FIG. 25 one of the heald shafts 1a, 1b, 1c, 1d should dwell in the upper or lower position for several operating cycles of the loom, and behind the hole actuating the disengagement ofthe cams 4 there must be no holes in the tape for the given heald shaft. In this case, the readout needle 77 interacting with the tape will retract the lug 62 of the plate 61 from the line of action of the three-arm lever 60 of the control mechanism, the roller 31 thus having no effect on the changeover gear 29.
It should be noted that when the heald shaft 1 changes its position for each operating cycle of the loom, behind the hole commanding the engagement of the shedding cam 4 there must be no holes in the tape either, i.e. the shedding cams 4 should continuously rotate about the axle 5 until a card with a hole to actuate the disengagement of the cams 4 approaches the feeler.
What is claimed is:
1. An apparatus for the heald motion of looms, comprising: shafts with healds for the passage therethrough of warp threads, which are capable of alternately reciprocating in the vertical plans and dwelling so as to form a shed of said warp threads; a shaft; paired profiled shedding cams each having a seating hole with segmental cutouts for mounting them loosely on said shaft independently ofthe other pairs so as to be capable of periodically rotating about this shaft for communicating said reciprocatory motion to each of said heald shafts; clutches with rotary keys, each serving to periodically turn each of the said pairs of cams, one half-clutch of each of said clutches being constantly associated with the main shaft of the loom, and the other half-clutch of each of said clutches being constantly associated with a respective pair of cams, and periodically being engaged with said main shaft through said rotary keys; a control mechanism which turns said keys following the action of a program carrier; a means to fix each of said pairs of cams on the shaft in a position corresponding to the dwell of the heald shaft.
2. The apparatus as claimed in claim 1, wherein the shaft of the shedding cams is made hollow, and the means to fix them on said shaft comprises springed blocks located inside this shaft and carrying rollers that contact the seating hole of the cam and enter the segmental cutouts of this cam, said cams in their fixed position on said shaft being capable of oscillating within an angle of the cam profile that corresponds to the dwell of the heald shaft.
3. The apparatus as claimed in claim 2, comprising having a pivoted rocker which serves to oscillate each of the cams, and the arms of which are attached to links whose free ends are hinged to a flange affixed on the end face of the hollow shaft of the cams.
4. The apparatus as claimed in claim 1, wherein the half-clutch associated with the main shaft of the loom comprises a cylindrical body rotatably mounted on an axle and provided with shoulders and wells for the rotary keys fitted with toothings whereby these keys are kept in internal engagement with a changeover gear seated on one of said shoulders and having outer recesses to accommodate a roller of the control mechanism, while the other half-clutch is made as a gear with segmental cutouts formed in its seating hole, this gear being seated on the other shoulder of said body, and meshing with another gear which is placed between the shedding cams and is connected thereto by a flared pin.
5. The apparatus as claimed in claim 1, wherein the control mechanism comprises cams mounted on a drive shaft so as to interact with rollers, and a frame carrying said rollers. as well as a bar to which a springed rod is hingedly secured carrying the roller that periodically enters the recesses of the changeover gear, and a threearm lever through which a movable stop is associated with the program carrier.
6. The apparatus as claimed in claim 1, wherein the program carrier comprises a drum mounted in guides so as to be capable of reciprocatory motion in a plane normal to the plane of motion of the heald shafts, this drum being reciprocated from a double-track cam and having pins for drawing a punched tape whose holes accommodate readout needles, which needles are placed in a block, their free ends abutting against bracketmounted plates each carrying a lug to interact with the respective three-arm lever of the control mechanism, said drum being at its edges provided with toothings one of which interacts with a toothed-sector mounted on an axle so that it can be swung from said doubletrack cam.
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|International Classification||D03C1/12, D03C1/00|