Summation drive for controlling shogging in a warp knitting machine

A summing arrangement controls the shogging movement of a guide bar of a warp knitting machine. The arrangement has a plurality of ordered elements each having at least one curved face. The ordered elements are mounted on the machine to allow a variation in the spacing between each. Also included is a plurality of adjustable roller devices, one between each adjacent pair of elements. Each of these roller devices can roll upon and push at least one of the elements at its curved face.

BACKGROUND OF THE INVENTION 
1. Field of the Invention 
The present invention relates to a guidebar shogging guide apparatus for 
warp knitting machines and in particular to a guide apparatus that is 
adjustable and automatically programmable in fixed increments that are 
proportional to the knitting machine needle spacing. 
2. Discussion of the Relevant Art 
Shogging mechanisms of different types are available in the art and are 
disclosed in a textbook entitled, "Warp Knitting Technology" by D. F. 
Paling first published in 1952 and reprinted in 1970 by the Columbine 
(Publishers Limited). Another shogging or steering element is disclosed in 
"Die Kettenwirk Maschine" by Emil Michael, published by Konradinverlag 
Robert Kohlhammer of Stuttgart, West Germany; pages 37 through 40 disclose 
a guide mechanism to control the movement of a warp knitting machine 
guidebar which contains seven setting elements (see FIG. 55 at page 39) to 
obtain the incremental distances that the guidebar is to be moved. The 
movable setting elements are placed into position by means of a 
conventional jacquard arrangement. The jacquard arrangement moves the 
setting element into a predetermined position so that the head portion of 
the setting element provides a defined thickness along a longitudinal 
axis. By choosing a combination of different setting elements, having 
different thicknesses, the longitudinal thickness which determines the 
position of the silder bar that is operably coupled to the guidebar, may 
be modified in accordance with the preset program. 
In a known arrangement of this type (DE-PS 482,949) the summation drive 
comprises a plurality of cam plate pairs which are axially mounted upon a 
rod and this rod is rotatably supported. By a relative rotation of 
180.degree. between both plates of a pair there is provided a displacement 
of 1, 2, 4 8 or 16 needle spaces so that at the free end of the summation 
drive there may be provided a displacement of up to 31 needle spaces. 
Under the influence of a tension spring the guidebar is forced into 
contact with the free end of the summation drive. The tension spring 
causes the cam plates to contact one another in a force transferring 
manner. 
In such summation drives, however, there is a considerable amount of 
friction when the plates, under the influence of the spring tension, are 
moved relative to each other. This leads to an undesirable generation of 
heat as well as wear. The structural options for the curved surfaces are 
limited. This leads to disturbing noises during resetting. 
A novel arrangement is known for eliminating the problem of friction. This 
is disclosed in DE-OS 2926929 (allowed U.S. patent application 165,020 
filed July 1, 1980, and U.S. Pat. No. 4,312,196). This arrangement for the 
displacement of the guide bar comprises two alternately activated sliders 
which operate in conjunction with a series of jacquard influenced setting 
elements provided perpendicular to the shogging direction. These setting 
elements have different thicknesses and can be set to provide a desired 
amount of displacement. This arrangement requires a pair of summation 
drives. 
SUMMARY OF THE INVENTION 
A summing arrangement according to the principles of the present invention 
can control the shogging movement of a guide bar of a warp knitting 
machine. This arrangement has a plurality of ordered elements, each having 
at least one curved face. Each of the elements is mounted in the machine 
to allow a variation in the spacing between each. Also included is a 
plurality of adjustable rolling means. A corresponding one of the rolling 
means is engaged between each adjacent pair of the elements and can roll 
upon and push at least one of the elements at its curved face. 
Accordingly it is one object of this invention to provide an arrangement of 
the type hereinbefore described which comprises only a single friction 
free summation drive. 
By employing equipment of the foregoing type, a simple, efficient and 
reliable apparatus is provided for controlling shogging without 
unnecessary friction and wear. In a preferred embodiment the shogging 
adjustment is performed through an impulse roller which is displacable 
across the curved surface of an element. This roller can be supported on a 
neighboring element by means of an intermediate member, in some 
embodiments. In other embodiments duplex rollers engage two adjacent 
elements. 
In either mode of construction the amount of friction is minimal since the 
roller rolls upon the appropriate curved displacement surface. The amount 
of wear and frictional heating are similarly minimized. The exact 
positioning of the guides of a guide bar with respect to the associated 
needles of the needle bar is therefore not impaired either by reason of 
wear or by reason of thermal expansion. If the impulse rollers are 
supported on the neighboring element by means of an intermediate element, 
or if duplex rollers separate adjacent elements, the desired summation 
effect is achieved. The displacement curve surfaces can be designed for 
relatively quiet operation.

DESCRIPTION OF THE PREFERRED EMBODIMENTS 
FIG. 1 illustrates a longitudinally reciprocatable guide bar 1 having a 
spaced plurality of conventional guides 2. Spring 3 is held at one end 
thereof by a fixed support 4 its other end connecting to and acting upon 
guide bar 1 via connecting means 5. Rod 6 is held in contact with guide 
bar 1 via roller bearing 7 on one end of rod 6. The other end of rod 6 is 
connected via roller bearing 8 to the free end 9 of summing arrangement 
10. 
Summation drive 10 comprises fixed element 11 and six movable, ordered 
elements 12 through 17 in the shape of blocks, the latter six being 
longitudinally slidable in fixed guideway 18. Element 17 comprises a 
curved displacement surface 19 both of whose contiguous end segments 20 
and 21 are responsible for the displacement of element 17. Guideway 18 has 
a lower and upper channel for receiving the elements 12-17 and may 
incorporate ball or other bearings to facilitate motion in the guideway. 
A roller means is shown herein as a roller and intermediate means. The 
intermediate means is shown as bracket 23 pivoted at axle 24 to element 
16. The impulse roller 22 lies in contacting relationship with surface 19 
and is rotatably supported in pivoting lever 23 which serves as an 
intermediate member. Preferably, elements 12-17 are non-rotatably held in 
guideways 18 and impulse rollers 22 are displacable substantially 
perpendicularly to the longitudinal direction of the guideway. This 
results in a much simpler control mechanism than that achieved by using 
rotatable elements. Pivoting lever 23 is rotatable about axis 24 set in 
adjacent elenent 16 so that roller 22 can move between surfaces 20 and 21, 
changing the spacing between elements 16 and 17. Pivoting lever 23 is 
pivotally connected to eccentric rod 25 at one end thereof and its other 
end being rigidly connected to ring 26 which encompasses eccentric cam 27. 
Said cam 27 is rigidly fixed to shaft 28 which is rotatable through 
180.degree. by an unillustrated control arrangement suitably in the same 
direction, that is to say, in the direction of arrow U. Similar impulse 
rollers, intermediate means and cams are provided to the corresponding 
remaining elements 12 through 16. The net effect is that the individual 
displacements between adjacent pair of elements 12-17 is summed by 
pivoting selected ones of the levers 23 supported by the neighboring 
element on which the impulse roller is rotatably supported. The desired 
displacement is achieved thereby through a simple pivoting motion. 
The curved displacement surfaces 19 of individual elements 12-17 are graded 
differently so that by displacement of different ones of the pivoting 
levers 23 from the horizontal position into the upper contact position, 
individual pairs of elements can be separated by different amounts. Thus 
the amount of separation between elements 17 and 11 can be coarsely and 
finely controlled. The displacement achievable between elements 11 and 12 
comprise 1T where T is equivalent to the needle to needle space on the 
needle bar. The displacement achievable between elements 12 and 13 is 
equivalent to 2T, between elements 13 and 14 is 4T, between elements 14 
and 15 is 8T, between elements 15 and 16 is 16T, and between elements 16 
and 17 is similarly 16T. Thus, it is possible to displace guide bar 1 by 
every integer multiple of T from between 1T through 47T. In all of these 
actions the individual elements 12-17 are compressed into a force 
transferring relationship by the action of spring 3. Because of the use of 
impulse rollers, the net displacement movement may be carried out without 
substantial friction or heating effect despite the existence of the spring 
force. The arrangement may also be utilized during substantially high 
machine speeds. The noise effect during operation is minimal. 
In the arrangement illustrated in FIG. 2, corresponding parts are 
designated by unit numbers increased by 100. A similarity between these 
embodiments is the inclusion of circular eccentric cam 127 affixed to 
rotatable shaft 128. Rotation of shaft 128 through an angle of 180.degree. 
is controlled by a Jacquard or similar arrangement (not shown), for 
example, apparatus in accordance with the system disclosed in DE-PS 
482,949. Eccentric cam 127 operates through a sliding crank block 129 
which is slidable in vertical chambers in guideway 130, in the direction 
of arrow V. In this embodiment block 129 is a rectangular frame embracing 
in its lower chamber cam 127, which by rotating, vertically reciprocates 
block 129. This block comprises longitudinal slit 131 in which guide 
roller 132 attached to pivot lever 123 may run. Lever 123 has a generally 
triangular shape, one apex containing pivot 124. Roller 122 is supported 
on another apex, the remaining apex supporting roller 132. Also, lever 123 
has a forked apex at axis 124 to straddle the components thereat. Pivot 
124 of lever 123 is pivotally connected at a recess of element 116 to 
limit the total thickness. 
It is apparent that there exists between elements 116-111 apparatus similar 
to that between elements 116 and 117. The rollers 122 can be rolled 
upwardly over surfaces 119 of elements 117, 116, 115, 114, 113 and 112 to 
increase the net displacement of bar 101 by 16T, 16T, 8T, 4T, 2T and 1T, 
respectively, T being one needle space as previously defined. Thus the 
mode of operation in this embodiment is similar to that shown in FIG. 1. 
In the embodiment of FIGS. 3 and 4 corresponding elements carrying a 
numbering 200 units greater than that of FIG. 1. The opposing faces of 
elements 216 and 217 have opposing curved surfaces 233 and 219, 
respectively. Curved surfaces 233 and 219 are shaped as staggered, 
flange-like tracks extending from the main bodies of elements 216 and 217. 
While surfaces 233 and 219 face in opposite directions they are 
transversely misaligned to permit engagement by coaxial rollers 234 and 
222, respectively, without interference. In this embodiment impulse roller 
222 which rolls on the curved displacement surface 219 is supported and 
thrust into position by adjacent element 216. Element 216 bears on second 
impulse roller 234 which rolls on running surface 233. This running 
surface 233 similarly serves as a displacement curve and is oriented 
conversely to that of displacement surface 219. The impulse roller 234 is 
mounted on the same axis 235 as impulse roller 222 but is rotatable 
independently thereof. The axle of axis 235 is supported on the forked 
upper end of connecting rod 225 whose lower end is the same as and has the 
same cooperating apparatus as that shown in FIG. 1. When cam 227 is 
rotated 180.degree. to produce a peak upward stroke, the two impulse 
rollers 222 and 234 move upwardly whereby element 217 is moved to the left 
by 16T units (as defined earlier). The same is true for the other 
adjustment devices as they affect elements 212-216. The drive of the 
eccentric shaft 228 can be controlled in the usual manner, for example, 
with coupling means which operate in dependence upon a Jacquard 
arrangement. 
It will be understood that the five other illustrated eccentric cams are 
Jacquard-controlled and each control the spacing between an associated 
pair of elements 211-216. In particular, elements 212, 213, 214, 215, 216 
and 217 can each add an additional amount of displacement, to the extent 
of 1T, 2T, 4T, 8T, 16T and 16T, respectively. It is significant that the 
intermediate element is second impulse roller 234 which is rotatable about 
the same axis independently from first impulse roller 222 and which 
contacts contact surface 233 on the interface of the neighboring element 
216. Since second impulse roller 234 is rotatable independently of first 
impulse roller 222 both may also roll on the appropriate contact surface 
in a substantially friction free manner. Furthermore, since the contact 
surfaces 219 and 233 are also a curved displacement surface, the 
displacement caused by the activation of the adjusting arrangement is then 
determined by both curved surfaces. This gives rise to smaller angles on 
the contact surface 219 and 233 and gives rise to a quieter run. 
In a typical operation, after each stitch, guidebar 1 of FIG. 1 ought to be 
moved longitudinally (shogged) a desired amount (which amount may include 
zero) to perform an underlap. It will be assumed that all of the levers 23 
are in the downmost position at this time, although this is not 
necessarily so and will vary depending upon the desired pattern. 
Furthermore since cams 27 are Jacquard-controlled, they need not return at 
the end of each cycle to a specific state but can vary independently and 
non-periodically. Furthermore there are 64 possible combinations for the 
positions of levers 23, corresponding to possible displacements of guide 
bar 1 from 0T to 47T (each of the displacements 16T through 31T can be 
achieved in two ways). Also all of the foregoing combinations may or may 
not be used, depending upon the desired pattern. 
Accordingly, the first shogging motion is accomplished by rotating Jacquard 
controlled shaft 28 by 180.degree. to orient cam 27 as shown in FIG. 1. 
The consequent lifting of roller 22 across surface 21 drives element 17 
outwardly to accomplish an underlap. Thereafter guidebar 1 can swing 
through the needles (not shown) and shog in either direction to accomplish 
an overlap. This may be accomplished by resetting cams 27 to any one of 
the above noted combinations. Thereafter guidebar 1 may again swing after 
which another knitting cycle can be performed. The foregoing described the 
operation of the embodiment of FIG. 1 but it is apparent that operation of 
the cams of FIGS. 2 and 3 will produce the same result with different 
mechanical linkages and apparatus. 
It is advantageous in these adjusting arrangements to utilize an eccentric 
cam for the displacement of the impulse roller. Such a cam can, for 
example, operate via a push rod acting on the lever to displace the axis 
of the impulse roller. However, various alternate devices including 
various bell cranks, solenoids, pneumatic actuators and other actuators 
may be used instead. The levers may also be provided in the form of a 
rocker arm in various shapes and having one or more rollers in addition to 
the impulse roller. An additional roller can be slidably mounted or linked 
to a guideway of a sliding block crank or other device whose motion, 
perpendicular to the shogging direction, is similarly controlled by an 
eccentric cam or another Jacquard-controlled device. 
It will be understood that various changes in the details, materials, 
arrangement of parts and operating conditions which have been herein 
described and illustrated in order to explain the nature of the invention 
may be made by those skilled in the art within the principles and scope of 
instant invention.