4346 4350.output

* GB784753 (A)
Description: GB784753 (A) ? 1957-10-16
Improvements in or relating to slideway grinding machines
Description of GB784753 (A)
PATENT SPECIFICATION
784,753 Date of Application and filing Complete Specification: March
21, 1955.
1 No 8186/55.
Application made in Switzerland on March 20, 1954.
>, ' Complete Specification Published: Oct 16, 1957.
Index at Acceptance:-Class 60, Dl D 4 A 1, D 2 A( 8: 20).
International Classification:-B 24 b.
COMPLETE SPECIFICATION
Improvements in or relating to slideway grinding machines We,
GESELLSCHAFT DER LUDW VON ROLL'SCHEN EISENWERKE A G, of Gerlafingen,
Switzerland, a Company organized under the Swiss laws, do hereby
declare the invention, for which we pray that a patent may be granted
to us, and the method by which it is to be performed, to be
particularly described in and by the following statement: -
The present invention relates to a slideway grinding machine, wherein
the workpiece is secured to a carriage arranged for reciprocation
under one or more grinding wheels mounted above said carriage,
particularly one for grinding the slideways of the beds of lathes,
planing machines, millers and grinders.
To render work of this nature less expensive, grinding machines have
already been designed in which two grinding heads are provided which
are displaceable along guideways of the grinding machine so that at
least two slideways can be machined simultaneously, irrespective of
whether the sliding surfaces are flat or profiled The beds of the
above-mentioned machine tools are as a rule provided with under-grip
guides to secure the carriage moved along the slideways, which must be
ground from underneath by means of dish grinding wheels.
The purpose of the present invention is to enable this undergrinding
to be carried out at the same time as the grinding of the top surface

of the slideways.
According to the present invention there is provided a slideway
grinding machine comprising a reciprocable carriage for carrying the
workpiece and a cross-beam extending transversely of the direction of
said reciprocation and on which at least one grinding member for top
surface grinding is mounted, characterised in that the cross-beam has
guideways for slides carrying grinding wheels, the first of which
lPrice 3 s 6 d l guideways is arranged on one of the vertical surfaces
of the cross-beam and the second guideway is arranged on the lower
horizontal surface of the cross-beam.
A typical embodiment of the invention is illustrated in the attached
drawing in which: Fig 1 is a front view of part of a slideway grinding
machine with a workpiece in position and two under-grinding
attachments arranged on the additional guideways of the machine; Fig 2
is an elevation of an undergrinding attachment seen in conjunction
with a part of the cross-beam of the machine; Fig 3 is a cross-section
along the line Ill-III in Fig 2; Fig 4 is a plan view of the
attachment according to Fig 2; Fig 5 is a cross-section along line V-V
in Fig 2, the grinding spindle being axially adjustable in a vertical
slide.
Referring to the drawings, a workpiece 102 is secured to a carriage
101, which carriage is arranged for reciprocation upon a bed 103 The
reciprocation of the carriage 101 carries the workpiece under a
cross-beam 1 extending transversely of the direction of reciprocation
of the carriage 101, and the cross-beam 1 is adapted to have
adjustably mounted thereon one or more grinding heads or attachments.
On the underneath side of the cross-beam 1 of the grinding machine, on
the front of which guideways 2 are provided for the main slide
carrying grinding wheels 11, lla, there is a recess 3 with additional
guideways 4 and 5 (Fig 3) The slide 6 is mounted in the guideways 4, 5
so that it can be displaced horizontally, and it is provided with a
threaded nut 7 through which the screw 8 passes The slide 6 is
provided with clamping bolts 12 and 13 which are hydraulically
controlled by means of the handwheel 10 The slide 6 can be displaced
horizontally by means of the screw 8 mounted in the guideway 5,
independently of the main slide mounted in the guideways 2 In the
slide 6 there is arranged a vertical dovetail guide 6 a on which the
vertical slide 14 is mounted.
Bolted to the slide 6 by means of bolts a is a flange 15 (Figs 2 and
3) to which an internally threaded tube 16 is rigidly welded at right
angles The threaded spindle 17, which is mounted on ball bearings 18
and 19 in the housing 14 a, engages in this internally threaded tube
On its lower end the spindle 17 has a handwheel 20, by means of which
the spindle 17 can be rotated and the slide 14 roughly adjusted

Between the two ball bearings 18 and 19 a worm gear 21 is keyed on to
the spindle 17 This gear is engaged by the fine adjusting worm 22
which is mounted on the shaft 22 a and on which is arranged the
handwheel 23, by means of which the slide 14 can be vertically
adjusted during the fine infeed The shaft 22 a, on which the fine
adjusting worm 22 is arranged, is eccentrically mounted in a rotatable
bush 22 b which can be turned by means of the lever 22 c so that the
worm 22 can be disengaged from the worm gear 21 for coarse adjustment
of the slide 14 The vertical slide 14 has an arm 25 in which is
mounted the bearing bush 26 of the grinding spindle 27 Arranged on the
grinding spindle 27 is the belt pulley 28 which engages in the recess
3 of the cross-beam 1, which recess is open underneath Also mounted on
the said spindle is a grinding wheel 29, of the disk type for
instance.
Secured to arms 30 on the other side of the slide 14 is the motor 31,
the belt pulley 32 of which also engages in the recess 3 of the
cross-beam 1 and drives the belt pulley 28 of the grinding spindle 27
via the belt 33.
The grinding wheel 29 can therefore be adjusted both horizontally and
vertically by means of the threaded spindle 8 and the threaded spindle
17 in the slide 14.
For the vertical adjustment of the grinding wheel 29, the latter may
be mounted in a threaded bush so that, by turning the threaded bush or
the threaded nut, the said wheel may be vertically adjusted without
displacing the slide 14 Fig 5 shows this adjusting device The grinding
spindle 27 is, as shown in Fig 5, mounted in an axially shiftable bush
35 in the vertical slide The said bush 35 is provided with a thread 36
and held in a threaded nut 37 so that it is axially displaceable The
bush 35 also has a toothed rim 38 which is engaged by the worm 39
mounted on the shaft 40 Fine adjustment of the grinding wheel can be
effected by turning the shaft 40 with the nut 37 locked, and coarse
adjustment by turning the nut 37.
The vertical feed as well as the horizontal displacement of the
grinding spindle can also be automatically effected at the end of each
carriage travel by known means which are not described in detail, such
as motors and reducing gear for instance.
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* GB784754 (A)
Description: GB784754 (A) ? 1957-10-16
Improvements in or relating to infinitely variable gearing
I, ROBERT JAMES ROSTRON, of 187 Ashton
Drive, Bristol 3, a British Subject, do hereby declare the invention,
for which I pray that a patent may be granted to me, and the method
by' which it is to be performed, to be particularly described in and
by the
following statement: -
This invention relates to infinitely variable gearing and in
particular to gearing wherein the change of gear ratio takes place
automatically in proportion to the torque in or the speed of the
output shaft.
One of the objects of the present invention is to provide an
infinitely variable gear box having an automatic change of ratio with
change of torque in the output shaft, wherein there are no slipping or
rubbing parts and no servo-mechanisms.
According to the present invention I provide a gear box comprising an
input shaft and an output shaft, a first epicyclic gear one element of
which is coupled to said input shaft, a second epicyclic gear one
element of which is coupled to said output shaft and two separate
trains of gears of differing ratios coupled between the other elements
of said two epicyclic gears Said epicyclic gears may comprise a pair
of differential gears arranged in parallel relation, and the cages of
said gears may be coupled to the input shaft and output shaft
respectively The difference in gear ratio between the two different
trains of gears may be less than ten per cent of the total ratio of
each train The total gear ratio of each train may be greater than 100:
1.
Referring now to the drawing filed herewith which shows a diagrammatic
plan view of one form of gear box made in accordance with the present
invention In the form shown an input shaft 1 carries a bevel gear 2
driving a bevel gear 3 mounted on the cage 4 of a differential gear 5

Said shaft 1 and said differential gear 5 are mounted in bearings in
the casing 6 of the gear box.
Two lay shafts 7 and 8 are provided, one end of each of which is
mounted in bushes 9 and 10 respectively in the casing 6 and the other
end of each of which is secured in the bevel gears 11 and 12
respectively of the differential gear 5 and mounted in bearings in the
cage 4 A second differential gear 13 is mounted in bearings in the
casing 6 by its cage 14, and a second pair of lay shafts 15 and 16
respectively extend therefrom and run parallel to the shafts 7 and 8
and are mounted in like manner to the shafts 7 and 8 in bushes 17 and
18 in the casing Two pinions 19 and 20 keyed to the shafts 7 and &
mesh with the gears 21 and 22 of the double gears 23 and 24 mounted
free to rotate on the shafts 15 and 16 respectively.
The pinions 25 and 26 of the double gears 23 and 24 mesh with the
gears 27 and 28 of the double gears 29 and 30 mounted free to rotate
on the shafts 7 and 8 respectively.
The pinions 31 and 32 of the double gears 29 and 30 mesh with gears 33
and 34 keyed to the shafts 15 and 16 A bevel gear 35 is mounted on the
cage 14 of the second differential 13 and meshes with a second bevel
gear 36 mounted on the output shaft 37 The drive from the input shaft
is therefore in effect divided at the first differential gear for
transmission through two trains of gears, one train numbered by odd
numbers and mounted on the shafts 7 and 15 having a reduction gear
ratio of 100: 1, and the other train numbered by even numbers and
mounted on the shafts 8 and 16 having a reduction gear ratio of 105: 1
The two trains will hereinafter be referred to as "the lower ratio
drive" and "the higher ratio drive" respectively The second
differential gear combines the two drives and feeds the output shaft
37.
In use the input shaft of the gear box is coupled to a prime mover and
the output 784,754 PATENT SPECIFICATION
Date of filing Complete Specification: March 16, 1956.
Application Date: March 22, 1955 No 8355/55.
Complete Specification Published: Oct 16, 1957.
Index at Acceptance:-Class 80 ( 2), D 2 D 2.
International Clausification:-FO 6 h.
COMPLETE SPECIFICATION.
Improvements in or relating to Infinitely Variable gearing.
65.
shaft to the machine required to be driven.
If the engine used as a prime mover is idling and the input shaft is
being driven in a clockwise direction of rotation (looking a from the
input end) the cage 4 will rotate clockwise (looking in the direction
of the arrow X) All directions of rotation to be measured hereafter

will be in the two directions of viewing the gear box mentioned above
This clockwise rotation of the cage 4 will tend to drive the shafts 7
and 8 also in a clockwise sense Assuming that there will be a greater
resistance to drive the higher ratio gear train via the shaft 8 than
the lower ratio gear train via the shaft 7 the tendency will be for
the latter train to rotate in preference to the former Therefore the
lower ratio gear train will tend to be turned clockwise while the
higher ratio gear train will tend to remain stationary The shaft 7
driving through the lower ratio gear train will consequently rotate
the shaft 15 anticlockwise If the shaft 8 is stationary then the shaft
16 coupled to it must also remain stationary and the cage 14 will tend
to rotate anti-clockwise thus driving the bevel 36 and the output
shaft 37 anti-clockwise.
As soon as the resistance at the output shaft 37 is increased the
shaft 8 will begin :3 u to turn slowly in the opposite direction to
that of the shaft 7 i e anti-clockwise, thus turning the shaft 16 in
the clockwise sense.
This will reduce the speed of the shaft 7, (assuming input remains
constant) and thus 3,5 the speed of the cage 14 As the resistance at
the output shaft increases towards a predetermined value the speed of
the shaft 16 will approach the speed of the shaft 15 in an opposite
sense with the resultant slowing up of the cage 14 and a reduction of
the gear ratio When the speed of the shaft 16 is equal to that of the
shaft 15 the cage 14 will have no tendency to turn at all and the
output shaft will stall Under these conditions there is a point of no
drive being transmitted Between this point of no drive and the point
of direct drive through the lower ratio gear train there are an
infinite number of gear ratios automatically selected by the
resistance at the output shaft Since the ratios between the two
separate trains of reduction gears are different there will be no
tendency for the input shaft to stall as well as the output shaft as
the shafts 7 and 8 will never turn at the same speed in opposite
directions.
The point of no drive is determined by the ratios of the two separate
gear trains and by the difference of ratio between them.
One of the advantages of a gear box constructed according to the
example described above is that an infinitely variable gear box can be
built with standard parts and there are no rubbing surfaces, fans or
slipping belts nor are there any servo mechanisms.
Moreover the gear box automatically selects a position of no drive as
soon as the torque at the output shaft reaches a predetermined value
thus preventing overstraining the engine.
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* GB784755 (A)
Description: GB784755 (A) ? 1957-10-16
Improvements in or relating to pressure operated switches
We, TEDDINGTON AIRCRAFT CONTROLS
LIMITED, a British Company, of Cefn Coed, Near Merthyr Tydfil, South
Wales, do hereby declare the invention, for which we pray that a
patent may be granted to us, and the method by which it is to be
performed, to be particularly described in and
by the following statement:-
This invention relates to pressure-operated switches of the kind in
which a switch mechanism is actuated by changes in the pressure
differential across a spring-loaded diaphragm.
One use for switches of this character is in systems for controlling
flow of air or gas through a conduit where the pressure in the threat
of a venturi mounted in the conduit and the pressure at a point in the
conduit upstream of the venturi are transmitted respectively to
opposite sides of the diaphragm, the switch mechanism operated by the
diaphragm controlling the energisation of adjusting means for a flap
valve or like element regulating quantitive flow of air or gas through
the conduit This method of control is commonly used, for example, in
aircraft cabin pressurisation systems.
The object of the present invention is to provide novel or improved
means for varying the degree of spring loading on the diaphragm such
that the energisation of the adjusting means for the flap valve or
like element for a given change of pressure differential across the
diaphragm may be varied according to operational needs.
According to the invention a pressureoperated switch of the kind

referred to above comprises a coiled spring loading the diaphragm in
one direction, thrust means engaging one end of said spring, a
reversible electric motor driving through reduction gearing a rotary
cam device, and lever lPrice 3 s 64 2 7849755 mechanism actuated by
said cam device and operable to impart movement to said thrust means
to vary the degree of compression of said spring.
An embodiment of the invention will now be described with reference to
the accompanying drawings of which:Fig 1 is a partly sectional
elevation of the complete instrument, and Fig 2 is a section on the
line II-II of Fig 1.
In the illustrated embodiment of the invention the diaphragm, variable
spring loading means and switch mechanism are associated to form a
single instrument, for which purpose there is provided a base plate 1
and a cover 2 having sealing engagement therewith to form a closed
chamber.
Attached to the outer side of the base plate 1 is a pair of recessed
discs 3 and 4 between which the peripheral edge of the diaphragm is
clamped, the inner disc 4 being formed with a tubular extension 6
which passes through an aperture in the base plate and into the closed
chamber The central portion of the diaphragm is clamped between outer
and inner support plates 7 and 8 The two operating pressures are
transmitted respectively to the recess or space on the outer side of
the diaphragm and to said closed chamber.
Mounted within the tubular extension 6 with a close sliding fit is a
hollow plunger 9 which at one end is attached to the diaphragm support
plate 8, a coiled compression spring 10 being interposed between the
other end of said plunger and a piston-like cap element 11 slidably
but non-rotatably mounted within the right hand end portion of the
tubular extension 6 Both the extension 6 and the plunger 9 are formed
with diametrically opposed window-like openings PATENT SPECIFICATION
Inventor: -ANTHONY BASIL CARTER.
Date of filing Complete Specification: March 26, 1956.
Application Date: March 25, 1955 No 8839155.
Comnplete Specification Published: Oct 16, 1957.
Index at Acceptance:-Class 38 ( 5), B 2 A 130 C: B 4: C 602).
International Classification:-H Oln.
Improvements in or relating to Pressure Operated Switches.
784,755 through which project portions of the switch mechanism now to
be described with particular reference to Fig 2.
The switch mechanism in this particular embodiment comprises an on-off
switch unit 12 (shown made) and a change-over switch unit 13 Axial
movement of a rod 14 to the left opposes the natural springiness of
the spring blades and causes switch unit 12 to ( open and switch unit

13 to change over This axial movement is imparted by a screw 15 set in
the right hand end of the plunger 9.
Located adjacent the outer end face of the cap member 11 is a thrust
ring 16 with a ball race 17 interposed between the cap and said ring,
and extending axially through the ring is a stud 18 provided with an
enlarged flat head 19 on its outer end, said stud preferably having
screw-threaded connection with the ring to facilitate initial setting
or adjustment.
Mounted alongside the tubular extension 6 is a reversible electric
motor which through built-in reduction gearing (not shown) drives a
rotary eccentric cam 20 supported externally of the motor housing 21
Pivotally mounted at one end on the motor housing 21 is a lever arm 22
which at its other end carries a roller 23 engaging the head 19 of 3 o
the stud 18 in the thrust ring 16, whilst intermediate its ends the
lever arm 22 supports a second roller 24 which rides upon the
periphery of the cam 20, the arrangement being such that rotation of
the cam 20 in 3.5 either direction by appropriate actuation of the
motor rocks the lever arm 22 and effects axial displacement of the
thrust ring 16 to increase or decrease the degree of compression of
the diaphragm loading spring 10.
4 o) Thus it will be seen that the invention provides a simple method
of remote control adjustment of the spring loading of the diaphragm
and in the application of the invention to mass flow control of the
air supply in cabin pressurisation systems as above mentioned, it
enables the rate of flow of air to be readily adjusted by either
manually or automatically controlling the energisation of the electric
motor during the cam 20.
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* GB784756 (A)
Description: GB784756 (A) ? 1957-10-16

A method and means for applying protective coverings to metal pipes
A Method and Means for Applying Protective Coverings to
Metal Pipes.
We, WELLINGTON TUBE WORKS LIMITED, of Great Bridge, Tipton, in the
County of
Stafford, a British Company, do hereby declare the invention, for
which we pray that a patent may be granted to us, and the method by
which it is to be performed, to be particularly described in and by
the following statement:
This invention relates to a method and means of applying to gas and
water service or other pipes, a protective covering of the kind
consisting of bitumen or the like and a reinforcement consisting of
hessian, glass fibres, slag wool or other fibrous material.
According to the invention a succession of pipes interconnected by
rapterable couplings are fed as a continuous tube through a means for
applying the covering thereto, and after emerging from the said means
a lateral force is exerted on the leading pipe for rupturing the
coupling between this and the next pipe and severing the part of the
covering which encloses this coupling.
In the accompanying drawings:
Figure 1 is a plan illustrating diagrammatically an apparatus for
carrying the invention into effect.
Figure 2 is a sectional view illustrating the means for
interconnecting a pair of pipe ends during the covering operation.
Figure 3 is a sectional view illustrating the condition of a pipe end
after detachment of the coupling means.
Referring to the drawings, the reinforcement material of the covering
consists of a continuous band a of any convenient width made from
hessian, felted or woven glass fibres, or slag wool, or any other
fibrous material, and this is fed through a bath b of bitumen or the
like of such consistency as will provide a relatively thick protective
coating on the reinforcement material. The protective coating may,
however, be applied in other ways. Thus it may be applied directly to
the pipes, in which case the reinforcing material is applied in a dry
condition.
The pipes c to be coated are usually screw threaded at their ends, and
to each of these ends is attached a coupling member d in the form of a
short sleeve which is engaged with the screw thread and which also
extends along a short length of the pipe beyond the screw thread so as

to prevent that length from being coated. In the outer end of one of
the coupling members in each co-operating pair is formed a central
hole e of polygonal or other non-circular shape, and on the adjacent
end of the other member is formed a short complementary spigot f which
is tapered along a part of its length to form a lead-in which can
enter the said hole. The two members of each coupling are such that
whilst they can transmit rotary motion from one pipe to the next, they
can easily be disconnected from each other by lateral deflection of
one of the pipes relatively to the other.
To enable the couplings to be easily detached from the pipe ends and
to obviate adhesion of the covering material to the couplings, each
coupling member has applied to it a paper sleeve g which is inwardly
flanged at one end, so that the flanges of an associated pair of
sleeves can be gripped between the coupling members. Alternatively the
couplings may be coated with a material such as, for example, an
oil-bound distemper to which the covering does not adhere.
For feeding the pipes longitudinally through the position at which the
covering material is to be helically coiled thereon, there are
provided at the approach side of the said position a pair of
power-driven cross-rolls 12 having their axes mutually inclined so
that they can impart both rotational and longitudinal motion to the
pipes.
Also pipe-supporting or guide rolls i are provided for feeding the
pipes to the crossrolls, the guide rolls being adapted to feed the
pipes forward at a faster rate than the cross-rolls.
When the apparatus is in action the first length of pipe is fed
forward to the position at which the covering material is applied.
At or adjacent to this position excess material (in one example) is
removed or is smoothed by a scraper or other means indicated by k and
a coating of whitewash, sand or a paper covering In is applied to
prevent adhesion of the coated pipes when bundled together. Where
paper is used the pipe is sluiced with water by a sprayer o to cool
and harden the coating. When the rear end of the first pipe approaches
the cross-rolls the next pipe is placed on the guide rolls as
indicated at the right hand part of Figure
1, and this pipe is rapidly fed forward so that its forward end
overtakes the rear end of the first pipe and effects interconnection
of the coupling parts. When the coupling passes through the covering
position it also is enclosed by the covering material. In like manner
other pipes are successively fed into the apparatus, so that a
virtually continuous pipe consisting of interconnected individual
pipes passes through the covering position, and has deposited on it a
continuous covering.
For separating the covered pipes, these are fed on to supporting

rollers p and so lateral force is exerted on the leading pipe so as to
deflect it relatively to the following pipe.
This force is applied to the forward end of the leading pipe and may
be exerted by a roller q. The effect of this deflection is to separate
the members of the coupling between the leading pipe and the next pipe
and at the same time break the part of the covering enclosing this
coupling. The separated pipes successively fall away to a collecting
position. Subsequently the coupling parts are detached and cleaned if
necessary, and are again used on other pipes.
The parts of the covering material which enclosed the couplings may be
left in position as shown in Figure 3, as they then serve to protect
the screw-threaded ends of the pipes during storage or transport. When
it is required to put the pipes into use the said parts can easily be
severed at the position indicated by the line marked r in Figure 3,
and then detached
By this invention the application of a protective covering to pipes
can be effected in a very expeditious, cleanly, and economical manner.
What we claim is:
1. A method of applying to pipes a protective covering of the kind
specified, in which a succession of pipes interconnected by rupturable
couplings are fed as a continuous tube through a means for applying
the covering thereto, and in which after emerging from the said means
a lateral force is exerted on the leading pipe for rupturing the
coupling between this and the next pipe and severing the part of the
covering which encloses this coupling.
2. An apparatus for effecting the method claimed in Claim 1, which
includes means for applying the covering material to the pipes, feed
rolls adapted to impart rotary and axial movements to the pipes,
supporting rolls adapted to impart axial movements to the pipes for
interengaging the coupling members on the adjacent ends of successive
pipe ends, other supporting rolls at the discharge side of the pipe
covering means, and means adapted to exert a lateral force on the
leading pipe for rupturing the coupiings and covering.
3. Pipe coupling means for use in the method and apparatus
respectively specified in Claims 1 and 2, comprising a pair of
interengageable members of the spigot and socket type for connection
to a pair of pipe ends, the said members being adapted to enclose the
pipe ends and being mutually disconnectable by relative lateral
movement.
4. A method and apparatus for applying a protective covering to a
succession of pipes, substantially as described and as illustrated by
the accompanying drawings.
PROVISIONAL SPECIFICATION.
A Method and Means for Applying Protective Coverings to

Metal Pipes.
We, WELLINGTON TUBE WORKS LIMITED, of Great Bridge, Tipton, in the
County of
Stafford, a British Company, do hereby de
clare this invention to be described in the
following statement:
This invention relates to a method and means of applying to gas and
water services or other pipes, a protective covering consisting of
bitumen or the like and a reinforcement consisting of hessian, glass
fibres, slag wool or other fibrous material.
According to the invention a succession of
* GB784757 (A)
Description: GB784757 (A) ? 1957-10-16
Improvements in circular knitting machines for the production of seamless
knitted footwear
A high quality text as facsimile in your desired language may be available
amongst the following family members:
FR1149866 (A)
FR1149866 (A) less
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The EPO does not accept any responsibility for the accuracy of data
and information originating from other authorities than the EPO; in
particular, the EPO does not guarantee that they are complete,
up-to-date or fit for specific purposes.
PATENT SPECIFICATION
Inventor: -BERT SMITH.
Date of filing Complete Specification: April 17, 1956.

Application Date: May 27, 1955 No 153211/5.
Complete Specification Piblihsihed: Oct 16, 1957.
Index at Acceptance:-Ciass 74 ( 2), C 1 A 5.
International Classifioation:-D 04 b.
Improvements in Circular Knitting Machines for the Production of
Seamless Knitted Footwear.
We, G STIBBE & Co LIMITED, a British Company, of Maxim Buildings,
Great Central Street, Leicester, do hereby declare the invention, for
which we pray that a patent may be granted to us, and the method by
which it is to be performed, to be particularly described in and by
the following statement -
This invention relates to circular knitting machines for the
production of seamless hose, three-quarter hose, half hose and like
articles of knitted footwear, and has reference particularly to such
machines of the single rotary needle cylinder type equipped with
outside sinkers.
In a seamless hose machine of this type, the needle cylinder has
secured thereto a radially tricked external ring constituting a bed
for the outside sinkers and there is fitted upon this ring a
stationary annular cap serving to carry the cams for operating the
sinkers in appropriate timed relation with 'respect to the needles The
periphery of the external sinker ring is in the nature of a journal
which is rotatable within the sinker cam cap, and the latter is
accordingly located by the said ring.
Heretofore, in a machine of the type concerned the periphery of the
sinker ring was solely relied upon to maintain the stationary sinker
cam cap concentric with respect to the axis of the machine But whilst
this necessary concentricity of the cap, and hence also the accuracy
in the positioning of the sinker-operating cams was satisfactorily
maintained when the machine was new, in due course wear between the
ring and the cap caused the latter to become eccentric.
As a consequence, the sinker-operating cams were displaced and
inaccurate timing of the lPrice 3 s 6 d 1 sinkers resulted Such wear
was in large measiure caused by foreign matter from needles, sinkers
and other parts passing between the ring and the cap.
The object of the present invention is to provide, in a circular
knitting machine of the type referred to, means of a simple and
efficient character for steadying the sinker cam cap and positively
maintaining it concentric with respect to the axis of the machine.
According to this invention, steadying elements carried by a
stationary support and suitably spaced apart about the machine are set
to engage the periphery of the sinker cam cap and thereby maintain the
latter concentric with respect to the sinker ring and the needle

cylinder to which said ring is secured.
The said stationary support may conveniently consist of a ring
disposed in a horizontal plane beneath the sinker cam cap, and the
steadying elements may take the form of blocks which are fixed upon
the ring and have slightly concave inner surfaces arranged in contact
with the exterior peripheral surface of the cap The support ring may
be attached to any convenient parts on the machine.
Any appropriate number of such steadying blocks may be provided;
three, however, is a convenient number since these can be readily
spaced at equal distances apart around the sinker cam cap suchwise as
to provide a three-point steadying arrangement In order that the
invention may be more clearly understood and readily carried into
practical effect, a specific constructional example thereof will now
be described with reference to the accompanying drawings, wherein:
784,757 Figure 1 is a vertical sectional view of so much of the head
of a knitting machine of the single rotary needle cylinder type as is
necessary to illustrate the external sinker a ring, the sinker cap and
the stationary support ring for the steadying blocks; Figure 2 is a
general perspective view of the steadying blocks mounted upon the
support ring and showing also the parts to which this ring is
attached; Figure 3 is a detail sectional view depicting the manner in
which a steadying block is arranged to engage the periphery of the
sinker cam cap; and Figure 4 is a fragmentary elevational view
illustrating one of the clips used for holding down the sinker cam
cap.
Like parts are designated by similar reference characters thoughout
the drawings.
In Figure 1, the single rotary needle cylinder of the seamless hose
machine is indicated at 1, and the relatively stationary cam box 2 is
mounted upon a bed plate 3 in the usual way At 4 is represented the
conventional latch ring above which is mounted the inturned welt dial
WD The needle cylinder 1 has secured thereto a radially tricked or
grooved external sinker ring 5, and there is fitted upon the latter a
stationary sinker cam cap 6 The sinker ring 5 rotates within and
locates the sinker cam cap 6 One of the latch needles operating in the
cylinder 1 is indicated at N, whilst at S is shown one of the outside
sinkers mounted in the ring 5.
For steadying the cam cap 6 and maintaining it concentric with respect
to the axis a of the machine, there are provided, in the illustrated
example, three steadying blocks 7 which are equally spaced apart
around the said cap and are mounted upon and fixed to a horizontal
support ring 8 As will be seen in Figure 1 this support ring, which is
of flat section, surrounds a lower reduced portion Sa of the external
sinker ring 5 and is attached, by means of screws 9, to a plate 10 in

turn carried by a main feeder column 11, at one side of the machine,
and by means of screws 12 (Figure 2) to a plate or like part such as
13 carried by an inturned welt dial drive column 14 at the opposite
side of the machine.
The inner face of each of the steadying blocks 7 is undercut at 7 a
suchwise as to accommodate and yet avoid contact with the peripheral
portion Sb of the rotary sinker ring 5 and to provide an operative
surface 7 b arranged in contact with the exterior peripheral surface 6
a of the stationary 68 sinker cam cap 6 The operative inner surfaces 7
b of the blocks 7 are slightly concave, the concavity of these
surfaces corresponding with the circumference of the outer vertical
surface 6 a of the cap 6.
d 5 The blocks 7 may advantageously be made readily adjustable upon
the support ring 8 to enable them to be adjusted and accurately set in
position in contact with the periphery of the cap 6 In this regard the
said blocks may, as shown more clearly 70 in Figure 3, be secured to
the ring 8 by means of screws 15 which extend through radial slots 16
in the ring and are screwed into tapped holes formed in the undersides
of the blocks 75 For the purpose of holding down the sinker cam cap 6
there are provided clips or the like, such as that indicated at 17 in
Figure 4, which are attached to the said cap and are adapted for
engagement with So the underside either of the support ring 8 or, as
shown, of the lower portion 5 a of the sinker ring The vertically
disposed portion 17 a of the clip depicted in Figure 4 is received in
a vertical slot 18 cut in a lug 85 6 b formed on the periphery of the
sinker cam cap 6 and is forked or slotted for engagement with a
securing screw 19.
If necessary or desirable, the support ring 8 may be made in two
parts, e g halves, to g O facilitate assembly.
Thus, as will be appreciated, the capsteadying arrangement provided by
the invention tends to reduce wear between the sinker ring 5 and the
cap 6, but, in any 95 case, the amount of such wear is no longer of
any consequence since the sinker cam cap is positively prevented from
becoming eccentrically disposed In fact, maintenance of the
concentricity of the cap ensures lou accurate timing of the sinkers
notwithstanding wear The invention is particularly advantageous in
fine gauge machines.
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