US3447300A - Mechanism for effecting rising and falling movements of spindles for textile bobbins - Google Patents

Description

June 3, 1969 J. F; HERUBEL 3,447,300 ING R ENTS OF Sheet Z of 3 MBCHANISM FOR EFFECT ISING AND FALLING MOVEM SPINDLES FOR TEXTILE BOBBINS Filed Aug2 31, 1967 ma .Q

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ATTONYS June 3, 1969 J. F. HERUBEL 3,447,300 TING RISING AND FLLING MOVEMEN MECHANISM FOR EFFEC TS OF SPINDLES FOR TEXTILE BOBBINS Filed Aug. :51, 1967 sheet 3 of s [wenn:

721 94W@ @my Armen/sys June 3, 1969 J F HERUBEL 3,44%300 MECHANISM FOR EFFECTIG 'RISING AND FALLING MOVEMENTS O SPINDLES FOR TEXTILE BOBBINS 3 Filed Aug. 31, 1967 Sheel'l Of 3 Affile/U6 YI United states Patent o Int. Cl. D01h Li/; B65h 54/00 U.S. Cl. 57--95 7 Claims ABSTRACT OF 'THE DISCLOSURE A mechanism for effecting the rising and falling movements of spindles for winding bobbins of filamentary textile material and providing for progressive reduction in the travel of the spindles to give the bobbins cone-shaped ends, reversing of the drive causing the rising and falling movement being under the control of two spaced detents engaged on screw-threaded portions of opposite pitch of a reduction screw which is turned through a part revolution for each rising or falling movement thereby adjusting the spacing of the detents and the lateral movement required of the member supporting them to effect the next change-over of movement.

Background of the invention The invention relates to devices for effecting the rising and falling movements used to wind bobbins of lamentary textile material such as roving.

As is known, the roving delivered by the spinning frame is wound onto bobbins in layers parallel to the axis of the winder and whose coils are close, with edges touching. To this end, all the spindles being wound are moved with a vertical reciprocating motion wit-l1 -a speed directly proportional to the diameter of the roving and inversely proportional to the diameter of the bobbin. Moreover, in order to obtain bobbins of good presentation and of which the coils of the two extremities do not cave on manipulation, the length of each successive layer is shortened with a view to giving the bobbin the shape of a truncated cone. The travel of the spindles is corrected, a-fter each rising and falling movement, by a correcting device which reduces the travel in such a way that each new layer of roving is shortened at the two extremities by a constant (but adjustable) value.

These mechanisms, currently called basculesj7 are of different types, but they all use in -a general manner the same principle. They control at the same time;

(a) the reversal of the rising and falling movement of the spindles;

(b) the decrease in the extent of the reciprocating travel of the spndles;

(c) variation in the general speed of rotation of the spindles dependent on the increase in the diameter of the bobbins.

These known bascules are `composed of a number of mechanisms which do not meet modern work requirements. They make use of counterweights or springs and work with relatively high response times. The reversing of the movement is often dicult as the parts are turning at high speed. Thus, the reversing device is often composed of a conical twinned sliding pinion coming into engagement with a conical driving pinion. At the moment of reversal the two pinions are turning at speed and the arrangement does not therefore lend itself to operation at high speeds. Moreover the resetting of the reversing mechanism is driven by ratchet wheel. This atter is fore-` seen as a spare.

Such devices have numerous disadvantages. On the one hand, the whole of these mecahnsms constitutes a device occupying considerable floor space, with numerous regulating points. On the other hand, a malfunction of the ratchet, therefore of the cone belt which does not shift, creates an increase in the tension of the` roving detrimental to its good regularity. An unsuitable number of teeth of the ratchet for a given roving can likewise create irregularities. Other incidents, such as the nongearing of the conical reversing wheels, instigated byl a bad setting of the bascule, disconnection of the driving rods, defects in the chains, wearing of the ratchets and of the pawl noses of the bascule, require frequent attention and are a hindrance to the good performance of the machine. The maintenance and lubrication of such mechanism, are, moreover, very costly.

On other types of bascules, and for purposes of simplication, certain mechanisms have been replaced by electrical devices. In this way two limit switches, mounted on a lead screw, may replace the conventional rack. In its rising and falling movement the spindle carriage -actuates the twin switches which, through the intermediary of an electromagnetic reverser, control the movement of the carriage. On such bascules the switches are subjected to very frequent and fairly sudden actuations. A bad contact on a level with the switches or a current failure, entails disturbance to the bobbin filling cycle. Under the effect of the inertia of the machine the spindles continue their travel, winding of the bobbin then being carried beyond the normal position of the cone. This yis all the more -annoying because the fault occurs on all the bobbins being wound.

In accordance with another known embodiment, the conventional driving devices of the spindle carriage have been replaced by a device of turning yand retractable shoes, driven by a rack. Such a mechanism works on shock and is prone to break down.

An object of the invention is to realise rst all of a driving device for the rising and falling movement of the spindles on the spindle beds which does not have the aforesaid disadvantages of the known devices.

Summary of the invention To that end the invention uses a device of the type comprising an input shaft which is driven permanently in a certain direction of rotation, preferably through the intermediary of a speed changer, and which drives an out put shaft through the intermediary of a mechanical direction reverser, placed under the control of two detents carried by a sliding part actuated by a lead screw drivably connected for rotation by the said output shaft. The said detents are movable on the sliding part which carries them and their spacing is adjustable by the movement of rotation of a reduction screw having two screw-threads of opposite pitches. The mechanical direction reverser may be actuated by a mechanism which comprises an intermediate shaft driven, for one revolution at a time, from a power take-oft in permanent motion, through the intermediary of a clutch of a type having a retractable peripheric key with a stop member inthe path of which two Such a device comprises only simple parts of conventional conception and of inexpensive realisation, needing less maintenance. Moreover, this bascule has the advantage of taking up a reduced amount of floor space, all the more so because the parts which constitute it are, in an advantageous specific embodiment, arranged one above the other, in the same Vertical plane, which facilitates access to the apparatus and consequently its maintenance and adjustment. :The drive of all the parts is positive, which eliminates inaccuracies of the movement and the risks of breakdown which are often imputable, in conventional bascules, to the use of racks or ratchet wheels with pawls. Finally the driving parts shift at low speed, especially the control detents, which enables operation to be carried on without shocks :and consequently making little noise and suffering little wear. :In an advantageous embodiment the driving parts for regulating the gear controlling the speed of rotation of the spindles are actuated by the reduction screw having screwthreads of opposite pitch for controlling the variation of the spacing lof the detents.

Brief description ofthe drawings The invention will be better understood by reading the following description taken together with the attached drawings which show, by way of a non-restrictive exam-v ple, a specific embodiment of a device in accordance with the invention for effecting rising and falling movements of the spindles on a roving frame and for driving means controlling the speed of rotation of the said spindles.

In these drawings:

FIG. 1 is a diagrammatic front view of the device, some parts being omitted;

FIGS. 2 and 3 are, on a larger scale, vertical sections taken respectively along the lines II-II and III--III of FIG. 1;

FIG. 4 is a horizontal section taken along the line lV-IV of FIG. 2; and

FIG. 5 is, on a larger scale, a partial horizontal section along the line V-V of FIG. l.

Description of the preferred embodiments The driving device shown in the drawings is arranged for driving spindles 1 of ra roving frame which comprises a large number of spindles similar to the spindle 1 and likewise mounted. The device also provides the drive for the speed controller indicated at 3 through the intermediary of which the spindles 1 are rotated.

Purely by way of example, the spindle 1 indicated on FIG. 1, is shown in a diagrammatic manner as being tubular and mounted for rotation with its axis on a rising and falling plate 6 supported by vertical screws such as 7 mounted for rotation in the bed 2. Each vertical screw,

such as 7, is rotatably driven by a horizontal shaft 9,4

mounted for rotation in the bed 2. The spindles 7 are connected to the shaft 9 by a couple of cylindrical toothed wheels 11, 12 and a couple of conical toothed pinions 13, 14. According to whether the horizontal shaft 9 iS made to turn in one direction or the other, this will instigate the simultaneous rotation of the vertical screws, such as 7, in one direction or the other, and, consequently, bring about the rise or fall of the plate 6 and of all the spindles 1 which it carries.

`Still in a diagrammatic manner, the speed controller 3, by which each spindle 1 is rotated, is shown as having an input shaft 16 and an output shaft 17 on which are mounted head to tail, respectively, two conical drums 18, 19 over which passes Ia belt 22. The input shaft 16 carries a Ipulley 23 on which is mounted a belt 24 driven itself by a drive pulley (not shown). The output shaft 17 of the speed controller 3 is connected through a couple of conical pinions 26, 27, to a shaft 28. A drum 29 is carried by this shaft, and a belt 31 passes round the drum 29 and a pulley 32 for each spindle. Each pulley 32 is rigidly carried on a vertical splined shaft 33 on which the associated tubular spindle 1 can slide without turning in relation to the said shaft. All the spindles are therefore set rotating at the same speed, during their rising and falling movement, from the output shaft 17 of the speed controller 3.

There is shown diagrammatically a driving device for regulating the ratio of the speeds of the input and output shafts of the speed controller in the form of a rod 37 which can slide in a direction parallel to that of the shafts of the controller and one extremity of which is provided with a fork 38 imprisoning the belt 22 and the other extremity of which is cut in the shape of a rack 39 in mesh with a toothed pinion 41 referred to below.

The driving device shown in the drawings is therefore to be used to effect, on the one hand, rotary movement of the shaft 9 for bringing about the rise and fall of the spindles and, on the other hand, pivoting of the toothed pinion 41 to shift the part regulating the output speed of the controller 3 controlling the speed of rotation of said spindles.

. This device comprises a vertical frame, denoted at 51 and formed substantially by two side plates 52, 53 connected at their middle parts by a plate member 54 and fixed on a base `55 integral with the bed 2.

In the frame 51 yare pivotally mounted first an input shaft 56 and an output shaft 57. T-he input shaft `56 is rotated continuously, always in the same direction, and inv the present example the drive for the shaft 56 is taken from the output shaft 17 of the speed controller 3 as shown diagrammatically in the drawing by a belt drive or chain drive 59.

Mounted loosely on the shaft 56, for example through the intermediary of ball bearings as shown, are two toothed pinions '61, 62 which can be made selectively rigid for rotation with the said shaft through the intermediary of a sleeve 63 which slides on a splined part of this shaft and the extremities of which are provided respectively with dogs 65, 66 capable of coming into mesh, either with dogs 67 of the toothed pinion 61, or with dogs 68 of the toothed pinion 62.

The toothed pinion 61 is in mesh with another toothed pinion 71 secured to the output shaft 57, whereas the toothed pinion 62 is in mesh with an intermediate pinion 72 of considerable length in mesh also with a toothed pinion 73 likewise secured to the output shaft 57.

This latter carries another toothed pinion 76 in mesh with a toothed wheel 77 secured to a shaft 7K8 connected through a coupling 79 to the shaft 9 controlling the rise and fall of the spindles and which is located in the bed 2.

It can be seen that, for the same rotational direction of the shaft 56 the shaft 9 c-ontrolling the rise and fall of the spindles turns in one direction or the other according to whether the sleeve 63 is brought into mesh with the toothed pinion 61 or else with the toothed pinion 62.

The control of the shifting of this sleeve 63 is effected by a bell crank lever 81, shown on FIG. l (see also FIG. 5) the two arms of which are indicated respectively at 82 and 83 and which pivots Ion a fixed vertical spindle 80. On the extremity of the arm 82 is fixed a spindle 84 on which there turns loosely a roller- 85 housed in a corresponding medial groove of the sliding sleeve 63. The other arm 83 of the lever -81 is 4connected to a cam 86 (assumed turned by between FIGS. 1 and 2 to give greater clarity in the drawings) fixed on the lower extremity of a vertical control shaft 187 mounted for rotation in the chassis 51 by means of two bearings 88, 89.

The connection between the arm 83 and the cam 86 is effected by two small plates `91, 92 resiliently applied against the two opposed faces of the arm 183, which has a width equal to the diameter `of the cam 86, by two springs 93, 95. One extremity of each of the springs 93, 94 rests against the bottom of a corresponding recess in the exterior face of the plate 91 or 92 and the other extremity rests against a nut 95 or 96 mounted on a screwthreaded end of a rod 97 fixed on the end of the arm 83 and extending freely through two holes 98, 99 made respectively in the plates 91 and 92. The plates 91, 92 are, furthermore, retained on the arm 83 by two positioning catches 101, 102 which are fixed in `the said arm and which extend freely through two holes 103, 104 in the plates.

The vertical `shaft 87 is rotated intermittently but always in the same direction and each time by half a revolution only, through the intermediary of a couple of conical pinions 106, 107 of the ratio 1/2, from an intermediate shaft 108. The shaft 108 is driven by a clutch 109 of a conventional type ensuring rotation of the shaft through one revolution, drive being imparted to the clutch from a wheel 111 mounted loosely on the said shaft 108 and rotated continuously always in the same direction by a suitable power take-off. In the example, this power take-off is effected from the input shaft 56, through the intermediary of two chain drives 113, 114.

The clutch 109, of a kind often used on presses, has a retractable key and is represented diagrammatically in FIG. 3. It comprises a finger 117, inte-gral with a key 118 projecting at right angles thereto and urged by a spring 119 in the direction which pivots the key in a housing in the outer cage 121 of the clutch and connects this latter with the inner cage 122 keyed on the shaft 108. When the finger 117 cornes into abutment with a knife 124 (see also FIG. l) or 125, the key turns on itself and draws aside from the driving notch of the outer cage, thus making the two cages no longer rotatably connected with one another.

The two knives 124, 125 are integral with two socket members 126, 127 which can slide on a rod 128, itself mounted slidingly in the chassis 51.

The two knives 124, 125 are urged towards one another and against the two end faces of a collar 129 of the rod 128 by a helical extension spring 130 of which the two extremities are attached respectively to the two socket members 126, 127. The two end faces of the collar 129 thus constitute detents limiting the movement of the socket members 126, 127.

The sliding movement of the rod 128 is brought about by the vertical shaft 87 which carries a cam 131 (see also FIGS. 2 and 4) having two lips 133, 134 between which are imprisoned the two prongs of a fork 135 secured to the rod 128.

The initial alternating shifting of the two knives 124, 125 is brought about by a disc 137 (FIG. 1) fixed centrally along a tubular member 138 which will be called hereinafter a reduction screw, and which can slide on a shaft 139 rotatably mounted in the chassis 51. The reduction screw 138 is connected for rotation with the shaft 139 by a key 141 (see also FIG. 3)

Engaged on the two extremities of the reduction screw 138, screw-threaded with contrary opposite pitches, are two nuts 143, 144 which carry two detents 14'5, 146 slidingly mounted against two trued horizontal slideways 147, 148 (see also FIG. 2) of the vertical member '54 of the chassis 51.

The reduction screw 138 is rotated with an intermittent movement, always in the same direction, by the shaft 1108, through a transmission which comprises a toothed pinion 15.1 secured to the shaft 108, a toothed wheel 152 in mesh with the toothed wheel 151 and mounted loosely on a fixed pin 153, a chain wheel 154 integral with the toothed wheel 152, a chain 155 which passes over the wheel 154, another wheel 156 over which the chain 155 also passes and which is secured to a coupling 157 comprising elements with mating saw teeth, one of the elements 158 being integralwith the wheel 156 and mounted loosely on the shaft 139, whilst the other element 159 is secured to the said shaft.

The role of the coupling 157 is as follows. After doffing, it is necessary for commencement of bobbin filling to return on the one hand, the belt 22 of the speed changer 3 and, on the other hand, the detents 145 and 146 on the screw 138 to their initial position, Iand this must be done -without having to turn the whole of the `drive for the spindles.

To this end, the coupling 157 allows the shaft t139 to be rotated independently of its drive from the wheel 154, the said shaft then being driven from an auxiliary drive (not shown). The auxiliary drive can be either manual from a hand wheel mounted directly lat the end of the shaft 139, or automatic from an auxiliary motor connected with the shaft in question. The starting up of the auxiliary motor can be effected automatically at the end of the bobbin filling cycle. During this phase of preparation for the bobbin filling cycle, to enable the belt 22 to be shifted on the cones 18 and 19, these latter are also arranged to be driven by the 'auxiliary drive.

The sliding of the reduction screw 138 is effected by la shoe 161 mounted slidingly on the trued way 148 and o-n another way 162 parallel to the way l148 the said shoe being integral with a nut 164 engaged on a rotary lead screw 165, parallel to the two aforesaid slideways '148 and 162 and the two extremities of which pivot respectively in the two side plates 52, 53 of the chassis 51.

The lead screw 165 is rotated in a reciprocating motion in phase with the movement of the output shaft 57 through a transmission which comprises a toothed wheel 167 secured to the shaft 57, and a chain 168 which passes over the toothed wheel 167 and over another toothed wheel 169 secured to the screw 165.

The toothed pinion 411 causing movement of the part adjusting the speed ratio of the controller 3 which controls the rotation of the spindles is connected to the shaft 139 and, in the example, it is represented as being integr-al with the said shaft.

The working of the whole o-f the device is as follows:

All the parts are driven in the directions indicated by the arrows by the speed controller 3. The spindles, such as 1, carrying the windings 10, are rotated by the output sh-aft 17 of the controller 3 through the transmission described above and are also caused to effect a rising and falling movement which, for the moment, finds itself in the descending stage, let us suppose. This falling movement is likewise brought about from the output shaft 17 of the speed controller 3 through the belt transmission 59, the shaft 56, the toothed pinion 61 at present connected for rotation with this shaft, the toothed pinion 71, the shaft 57, the toothed pinions 76, 77, the shaft 78, the coupling 79, the conical couple 14 and 13, the cylindrical couple 12 and 11, the screw 7 and the plate 6.

The lead screw 165 is rotated in the direction of the arrow by the output shaft 57 through the chain 168 so that the shoe 161 shifts in the direction of the arrow,i.e. towards the left when one regards FIG. l.

There comes la moment when the shoe 161 meets the left-hand detent l145 and shifts it towards the left; this movement causes sliding of the reduction screw 138 on the shaft 139, towards the left, and this carries the disc 137 which is integral with the shaft 139 to the left as well. This disc 137 immediately meets the socket member 126 which it shifts, in its turn, towards the left, so that the knife 124, carried by this socket member, also shifts towards the left and frees the finger 117 of the retractable key clutch 109.

The key 118 then connects the inner and outer cages 121, I122 'of the clutch together. During the shifting toward the left of the socket member 126 which carries the lefthand knife 124, the other socket member 127 which carries the right-hand knife remains immobile in abutment with the collar 129 of the sliding rod 128 under the action of the spring ywhich has stretched slightly. Seeing that the wheel 11'1 is rotated permanently from the input shaft 56 through the transmission 113 and 114, the retractable key clutch 109 now brings about rotation of the intermediate shaft `108 by connecting this latter with the Wheel 111, for one complete revolution only, since from the start of the rotation of this intermediate shaft 108 the sliding rod 128 finds itself shifted to the left by the cam 131 on the shaft 87 driven from the shaft 108 by the conical couple 106, 107. It follows that before the end of the revolution of the shaft 108, the right-hand knife 125 finds itself already on the path of the control linger 117 of the clutch 10-9. The key 118 is therefore put into the inactive position at the conclusion of the complete revolution of the shaft :108. The shaft 87 has therefore made half a revolution and the sliding rod 128 is now at the end of its travel towards the left.

Whilst the vertical shaft 87 effects half a revolution, the cam 86 fixed to its lower part pivots the bell crank lever 81 which, in its turn, slides the sleeve 63 towards the right, so that the toothed pinion 61 becomes loosek on the input shaft 56, whilst the toothed pinion 52 is connected to this shaft. The drive of the output shaft 57, instead of being effected by the two toothed pinions 61 and 71, is now effected by the toothed pinion 62, the intermediate pinion 72 and the toothed pinion 73, so that the direction of rotation of the output shaft 57 is reversed. This reversing produces reversing of the direction of rotation of the toothed pinions 77, 14, 13, 12 and 11, so that the vertical screw 7 turns in the opposite direction to that of the arrow so that, consequently, the plate 6 which supports the spindles now imparts a rising movement to these latter.

The reversing of the rotational direction of the output shaft 57 also instigates the reversing of the direction of rotation of the lead screw 165, so that the shoe 161 now shifts in the direction `contrary to that of the arrow, i.e. towards the right.

When the shoe 161 approaches the end of its right-hand travel, it pushes thel right-hand detent 146 and therefore carries the reduction screw 138, as well as the disc 137, towards the right. The disc 137, in its turn, pushes towards the right the socket member 127 which carries the right-hand knife 125 so that said knife is moved away from the linger 117 of the retractable key clutch 109. The clutch thus once more effects the driving of the shaft 108 for one revolution. From the start of the rotation of the shaft 108, the cam 131 slides the rod 128 towards the right so as to place the left-hand knife 124 on the path of the finger 117 of the clutch 109, i.e. in the position shown in FIG. 1.

The rotation of the vertical shaft 87 by half a revolution returns the sliding sleeve 63 towards the left, as shown in FIG. 1, so that the toothed pinion 62 is now loose on the input shaft 56, whilst the toothed pinion 61 is connected to this shaft, and so that the output shaft 57 once more changes its direction of rotation and resumes that shown by the arrow so as to ensure a fresh movement downward of the plate carrying the spindles.

It will be observed that at each revolution of the retractable key clutch 109 the shaft 108, driven for one revolution, always in the same direction, instigates a corresponding angular movement of the reduction screw 138 by the pinion 151, the toothed wheel 152 and the chain transmission 155. This angular movement of the reduction screw 138 brings about a corresponding drawing closer of the two detents 145, 146 which always remain equidistant from the disc 137. Thus, at each reversal of the rising and falling movement of the spindles, the reduction screw 138 turns through a fraction of a revolution and the interval between the two detents 145, 146 finds itself reduced.

This leads to a reduction in the duration of movement of the shoe 161 between the two detents, so that the travel of the plate carrying the spindles finds itself progressively diminished by a corresponding amount. A decrease in the travel of the spindles is therefore brought about which allows the bobbins 10 in course of formation to be given a conical shape at their two extremities.

Moreover, upon each reversal of the rising and falling movement of the spindles, the angular movement of the shaft 139, which carries the reduction screw brings about a corresponding angular movement of the toothed pinion 41 which shifts the rack 39 integral with the control fork 38 of the belt 22 of the speed controller 3, so that the rotational speed of the spindles iinds itself periodically reduced and so that one thus avoids any increase in the tension of the roving as a new layer of roving isv being wound on the bobbin.

It will be observed that the elbowed bell crank lever 8.1 (FIG. 5) is connected to the cam 86 which moves it through the intermediary of the system composed of the two small plates 91, 92 subjected to the action of the springs 93, 94. It follows that, from the start of the pivoting movement of the cam 86, the dogs in mesh disengage, but that the opposed dogs enter into mesh only when they arrive exactly facing one another, bringing about a slight compression of one or other of the' two springs, according to the pivoting direction of the lever, whilst the cam 86 effects half a revolution with a regular movement. One thus realises a rapid interlocking, without risk of deterioration of the device.

The advantages of the whole mechanism have already been set forth above.

The invention is, of course, not restricted to the specific embodiment which has been described and shown and which has been given by way of example, and one can make modifications thereto.

Thus, for example, the toothed wheel 111 driving the retractable key clutch 109 could itself be driven by some source of movement other than the input shaft 56 as shown; the retractable key clutch 109 could be replaced by any type of clutch able to make the shaft 108 turn each time by one complete revolution or by any desired constant angle; the input shaft 56 could be set rotating from some source of movement other than the output shaft 17 of the speed controller 3 rotating the spindles; the direction changer having dogs could be constructed differently; the system for rotating the spindle could be quite different from that shown very diagrammatically as an example; and the speed controller 3 having conical drums could be of another typel and the regulating drive of this controller taken from the shaft 139 of the reduction screw could be of some other construction.

I claim:

1. A drive mechanism for effecting the rising and falling -movements of spindles for winding bobbins of filamentary textile material, the mechanism comprising (a) an input shaft permanently driven in one direction of rotation;

(b) an output shaft providing drive to effect said rising and falling movements;

(c) a mechanical direction reverser drivably connecting said input shaft to the output shaft, said direction reverser comprising (d) reversing transmission means between said input and output shafts engageable for one or other direction of drive of said output shaft;

(e) a sliding carrier member including a rotatable reduction screw having two screw-threaded parts of opposite pitch,

(f) two spaced detents, one engaged on each of the screw-threaded parts whereby the spacing of the detents is adjustable upon rotation of said reduction screw,

(g) a lead screw drivably connected to the output shaft,

(h) a shoe-member screw-threadedly engaged on the lead screw and in a slideway so as to be laterally moveable in one direction or the other on rotation of said lead screw in one direction or the other, said shoe ymember being arranged to engage alternatively with one or other Vof said detents to carry the detent and said sliding carrier member with it,

(i) an intermediate drive shaft,

(j) permanently rotating driving means,

(k) a clutch for drivably connecting said intermediate drive shaft with said driving means, the clutch being of a type engaging, when actuated, for one revolution,

(l) means for actuating said clutch, said means being operable by engagement thereof by either of said detents,

(m) transmission means interconnecting the said intermediate shaft and reduction screw for adjusting 5 the spacing of the two detents on each revolution of the intermediate shaft, and

(n) means operable on each rotation of said intermediate shaft for causing re-engagement of said reversing transmission means thereby effecting reversal of 10 the drive from input shaft to output shaft.

2. A mechanism according to claim 1, wherein said means for actuating said clutch comprise (o) a retractable key on said clutch for connecting parts of the clutch together for transmission of drive,

(p) a rod mounted for sliding movement,

(q) two abutments on said rod, (r) two ngers slidably carried on said rod and elastically urged one against each of said abutments, (s) drive transmission mechanism connected to the intermediate shaft and to said sliding rod to position the latter on each revolution of the intermediate shaft to bring one or other of said lingers into position to retract said key preventing drive through the 25 clutch, `and a disc carried by said reduction screw and arranged to shift a corresponding one of said ingers along said rod releasing the key and engaging the clutch.

3. A mechanism according to claim 1, further including means for regulating the speed of rotation of the spindles, said means being controllable by rotation of said reduction screw.

4. A mechanism according to claim 1, wherein the parts of the mechanism are mounted in a vertically extending frame.

5. A mechanism according to claim 4, wherein said permanently rotating driving means are driven from the input shaft.

6. A mechanism according to claim 1, wherein said means for causing re-engagernent of said reversing transmission means comprises,

(t) a reduction gear train of ratio 1:2,

(u) a control shaft driven by said gear train,

(v) a cam carried on said control shaft,

(w) a part for eiecting engagement of the transmission means, and,

(x) resilient means connected with said part and engaging said cam.

7. A mechanism according to claim 6,

including a further cam carried on said control shaft and means connecting said cam with said sliding rod, said cam and said connecting means constituting said drive transmission mechanism connecting said intermediate shaft to the sliding rod.

References Cited UNITED STATES PATENTS 2,732,683 1/1956 Hoffmann 57-95 2,785,527 3/1957 Lewellen et al. 57-95 XR 2,898,729 8/ 1959 Anderson et a1. 57--95 2,996,870 8/ 1961 Fornes et al. 57-95 JOHN PETRAKES, Primary Examiner.

U.S. Cl. X.R.

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