-

1. * GB785919 (A)
Description: GB785919 (A) ? 1957-11-06
Improvements in or relating to internal combustion engines with two or more
cylinders
Description of GB785919 (A)
PATENT SPECIFICATION
785 9919 Date of Application and filing Complete Specification Jan 18,
1955.
Application made in Germany on Jan 18, 1954.
Complete Specification Published Nov 6, 1957.
Index at acceptance: -Classes 7 ( 2), B( 2 C 71 F 4: 4 A); and 7 ( 6),
B 2 P( 11 A 3: HA: 11 C 2), B 2 Q( 1 C: 5 B).
International Classification: -FO 2 b, f.
COMPLETE SPECIFICATION
Improvements in or relating to Internal Combustion Engines with Two or
l More Cylinders We, NSU WERKE A G, of Neckarsulm/ Wurttemberg,
Germany, a German company, and FELIX WANKEL, of Bregenzer Strasse 82,
Lindau/Bodensee, Germany, of German nationality, 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:-
Designs of rotary valve engines have been made and have become known,
where several working cylinders are controlled by means of one rotary
valve The present invention relates to an engine of this type, where
by means of a special arrangement of the working cylinders, rotary
valve and valve drive, an advantageous and simple design is achieved.
The invention consists in an internal combustion engine with two or
more cylinders, in which one rotary vale with a flat sealing surface
and with bent channels curving, in axial section, towards said
surface, is arranged above two adjacent cylinders of which the axes do
not intersect, or above each pair of adjacent cylinders of which the
axes do not intersect, to control the inlets and/or outlets thereof,
characterized in that the rotary valve rotates at half the crank shaft
speed and that the driving shaft of said valve is co-axial with the

2. valve and inclined at an angle between 15 and 450 to the cylinder
axes, and extends between the two cylinders.
It is essential for this invention, that the axis of the rotary valve
and thus its driving shaft are inclined to the axis of the cylinder.
The angle of inclination shall be about 15 to A spur wheel drive from
the crank shaft to an intermediate shaft, which is parallel to the
crank shaft, is employed to drive the rotary valve shaft The
intermediate shaft drives the rotary valve through a pair of bevel
gears The advantages of this drive are that a minimum of engaging
teeth is required, that the spacing of the cylinders is kept very
small and the &ameter of the rotary valve can be reduced to a minimum,
and above all that it makes possible an advantageous shape of the
combustion chamber and a particularly advantageous position of the
spark plug In order to reduce the diameter of the valve as much as
possible, it 50 is also proposed to arrange the control opening of
each cylinder not centrally, but offset in a direction towards the
appropriate rotary valve axis in a manner known per se.
This type of design can be employed for 4 55.
stroke engines as well as for 2-stroke engines.
For the 4-stroke engines a common suction pipe can be employed for
each pair of two cylinders, the inlet channel entering the rotary
valve centrally In the case of 2-strolke engines 60 the rotary valve
arranged and driven as described above will only control the outlet of
each cylinder, the inlet ports being piston controlled This means that
the rotary valve containing only two channels rotates at one half 65
the speed of the crank shaft in each case In the case of a 4-stroke
engine, the inlet of any given cylinder must be opened once every four
strokes, i e once in every two revolutions of the crank shaft, so that
the valve which in 70 this case has only one inlet channel must make
one revolution for every two revolutions of the crank shaft; in the
case of a 2-stroke engine the outlet of each cylinder must be opened
once in every 2 strokes, i e once for every 75 revolution of the crank
shaft, so that the valve which in this case has two outlet channels
must make only one half of one revolution for every revolution of the
crank shaft In order to reduce the spacing of the cylinders as much 80
as possible, the engine of this type is most conveniently designed for
liquid cooling The coolant is admitted to the rotary valve or valves
through the tubular drive shaft and is removed through a pipe coaxial
with the said 85 drive shaft.
It is also convenient to extend the shaft of the rotary valve at its
lower end and to employ it directly or indirectly for the drive of the
coolant pump Also, in addition to the coolant 90 785,919 pump, one or
several lubricating oil pumps can be connected to it in the same
manner.

3. The invention will be better understood from the following examples of
several methods of carrying it into effect, which should be taken in
conjunction with the accompanying drawings, in which:Figure 1 is a
sectional view, with certain parts shown in elevation, of an internal
combustion engine with rotary valve control according to the
invention, the section plane containing the axis of the rotary valve
and being perpendicular to the crank shaft; the rotary valve itself
and the gears driving it are shown in elevation and not in section.
The right hand half of Figure 2 is a sectional view with certain parts
shown in elevation, of a 2-cylinder unit corresponding to Figure 1
designed as a 4-stroke engine, the section being on line A-B-C of
Figure 1; the left-hand half is a sectional view with certain parts
shown in elevation of the same twocylinder unit, the section being on
the bent line A-B-D of Figure 1, Figure 3 is a section, as in the
left-hand half of Figure 2, through a two-cylinder unit designed as a
two-stroke and not a four-stroke engine but otherwise identical with
the engine shown in Figures 1 and 2, and Figure 4 is a diagrammatic
illustration showing the rotary valve control for a 6cylinder engine
consisting of three pair of cylinders each identical with the pair
shown in Figure 2, in section as in the left hand half of Figure 2 and
in Figure 3.
Figures 2 to 4 clearly show that in each case one rotary valve with a
flat sealing surface and curved channels is used for two cylinders 1
In Figures 2 and 4, one of the channels in the valve body is used as
inlet channel for the combustible mixture, and the other as outlet for
the combustion gases In the embodiments shown, the rotary valve 2 has
a vertically disposed driving shaft 3 coaxial with the valve and
extending between the two cylinders and driven by the crank shaft 14
of the engine through spur gears 4 and bevel gears 6 coupled therewith
The transmission ratias of the gears are made such that the rotary
valve rotates at one half the speed of the crank shaft.
Figure 1 also shows the further characteristic of the invention, that
the rotary valve 2 and its driving shaft 3 arranged between the
cylinders are inclined at an angle between 15 and 450 to the cylinder
axes By this expedient a considerable advantage is achieved, more
especially as regards saving of space, which is equivalent to a
relatively smaller construction of the rotary valve Moreover the
combustion chamber is given an advantageous shape and the spark plug
10 is disposed at a point in the combustion chamber which, as shown in
Figure 1, is easily accessible The curved channels in the body of the
rotary valve 2 connect the control openings 12 of the cylinder either
with the inlet duct 7 for the fuel-air mixture or with the outlet 8
for the combustion gases.
In the embodiment shown in Figure 3 the 70 rotary valve 2 only

4. controls the outlet from the cylinder, whereas the mixture intake is
through the transfer ports 13.
The 6-cylinder arrangement diagrammatically illustrated in Figure 4 is
obtained essen 75 tially by trebling the arrangement according to
Figure 2.
In Figure 1, at 11 a pump unit is indicated which can be used in the
other embodiments also It comprises a coolant pump, a lubricat 80 ing
oil pump and a return pump for returning the lubricant into the
lubricant container This pump unit is connected to the drive of the
rotary valve through an intermediate shaft 5 formed as a downward
extension of the rotary 85 valve shaft.
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* GB785920 (A)
Description: GB785920 (A) ? 1957-11-06
Improvements in or relating to copying machines
Description of GB785920 (A)
We, THE BIRMINGHAM SMALL ARMS COM-
PANY LIMITED, a British Company, of Small Heath Works, Birmingham 11,
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 copying machines in which a tool effecting
its cutting by relative reciprocation between the tool and the work is
positioned hydraulically in accordance with the position of a tracer
that is caused to follow a former in corresponding relative
reciprocation between the tracer and the former The invention is

5. particularly concerned with copy-forming work-pieces to produce a
surface that is pronouncedly "three-dimensional", an important example
of this kind of surface arising in turbine blades, where on both the
convex and the concave faces any cross-section may show a very
considerable curvature, which has to be followed in the successive
reciprocatory cutting strokes, apart from each stroke having to follow
the varying lengthwise shape of the surface.
It is known to effect hydraulic copyforming of turbine blades in a
shaping machine in which the work-piece is held stationary and the
tracer makes successive reciprocations along a former that does not
simulate the actual shape of the eventual article but has to be
specially developed for each different article from the dimensions of
the final surface required in that article.
It is also known to effect hydraulic copyforming of turbine blades in
a milling machine in which a milling cutter makes successive traverses
over a stationary workpiece under the control of a rotatable tracer
wheel of the same diameter as the milling lPrice 3 s 6 Mce 45 M"
cutter and caused to traverse similarly a stationary former profiled
to correspond directly with the final surface required in the
work-piece.
And it is also known to effect hydraulic copy-forming of turbine
blades by a rotating end-mill that is moved over a stationary
work-piece in accordance with a tracer of similar end-forn to that of
the end-mill and moved similarly over a stationary former profiled to
correspond directly with the final surface required in the work-piece.
These known methods, by their various limitations, make the forming of
turbine blades very costly, not least by requiring special elaborate
machines to carry them out; and this is the case even when each tracer
is used to control the simultaneous operation of a substantial number
of cutters on a corresponding number of work-pieces.
The object of the invention is to enable hydraulic copy-forming to be
readily carried out on basically simple machines such as shaping
machines and planing machines using a reciprocating cutting stroke,
with a, former profiled to correspond directly with the final surface
required in the work-piece, even when that surface is pronouncedly
"three-dimensional".
According to the present invention, hydraulic copying equipment for a
shaping, planing, or like machine using a reciprocating cutting stroke
and transverse feed movement comprises a former holder and at least
one work holder, both or all rotatable about axes parallel to each
other and adapted to be mounted parallel to the direction of
reciprocation of the machine, means to rotate the holders
Drogressively and simultaneously at each transverse feed movement, and
hydraulic mountings to position a tracer and one or more cutting tools

6. similarly with 785,920 PATENT SPECIFICATION
Inventor: -GEORGE HENRY LEVERINGTON.
Date of filing Complete Specif cation: Dec 23, 1955.
Application Date: Jan 1, 1955 To 2155.
Compilsvete Sl)ecdfcation Publishled: Nov 6, 1957.
Index at Acceptance:-Class 83 ( 3), L 2 H, L 3 (B 9: D 1: EX: G: J).
International Classification:-B 23 d.
COMPLETE SPECIFICATION.
Improvements in or relating to Copying Machines.
respect to the holders, with the hydraulic mounting for the tool or
tools controlled by the mounting for the tracer so that the tool or
tools during each reciprocation with respect to the work held in the
rotatable work holder or holders is positioned in accordance with the
position to which the tracer is brought by a former held in the
rotatable former holder during each corresponding reciprocation with
respect to the former.
With a face to be copied that is convex, or generally convex in
cross-section, the rotation of the former (and the likewise of the
work-piece) is about an axis in the approximate centre of curvature, i
e, behind the face itself; similarly with a concave, or generally
concave, face, the rotation is about an axis in front of the face In
each case, the rotation effects successive lines of cut that maintain
substantial uniformity of engagement between the cutter and the
workpiece, so that substantially the same narrow portion of the
cutting edge of the cutter remains in operation throughout the cutting
of the whole face This is of advantage in enabling correct side relief
to be given to the cutting edge, when each successive cut may be
performed under optimum conditions.
The rotation of the work brings each successive cut substantially
laterally alongside the preceding cut, regardless of the transverse
curvature of the work The narrow portion of the edge of the tool is
thus left to perform substantially similar cuts, mainly varied by the
end-to-end profiling of the portion of the former corresponding to
each cut, which-in the case of turbine bladesdoes not depart very much
from a straight line These provisions make for both rapidity of
machining and accuracy of the machined face, and the complicated
profile may thus be economically machined to fine limits, in fact to
limits so fine that only the final polishing needs to be performed.
The rate of rotation may be uniform; but in general, the rotation of
the work to position it correctly with respect to the tool cannot be
relied on to produce the amount of feed required at each stroke This
condition would only be satisfied fully if the work were cylindrical
or conical, but such simple work shapes can generally be machined
without recourse to the use of hydraulic copying However, by using a

7. hydraulic cylinder and piston to effect the simultaneous rotation, as
by means of a rack meshing with pinions on the holders, a hydraulic
valve, and a cam operable by the reciprocating action of the machine,
the amount of rotation can be made appropriate to any work of awkward
section Moreover, the holders may be given a simultaneous transverse
movement, as by mounting them on one part of a two-part fixture, the
other Dart of which carries a further hydraulic cylinder and piston,
controlled by a further hydraulic valve and a further cam operable by
the reciprocating action of the 70 machine The cams may have a common
mounting, so that they may be simultaneously operated.
The rack and pinion drive of the holders may be interchangeable with
worm wheels 75 for the holders and worms on a common shaft rotatable
directly from the reciprocating action of the machine, for the copying
of shapes that do not require cam control, through hydraulic
mechanism, to effect the SO rotatory and transverse movements.
The invention will now be described in greater detail with reference
to the accompanying drawings, in which: Figure 1 is a perspective view
of the work 85 table end of a shaping machine as set up with equipment
in accordance with the invention; Figure 2 is a side elevation of a
work mandrel as used in Figure 1;, Figures 3 and 4 are diagrams
illustrating the difficulties encountered in shaping the convex and
concave faces respectively of a turbine blade; Figures 5 and 6 are
similar diagrams illus 't trating the desirable relation between tool
and work obtainable by means of the invention; Figure 7 shows
diagrammatically the relationship of two turbine blades and two 100
tools to a former and a tracer when shaping the convex faces of the
blades; Figure 8 is similar to Figure 7, but relates to shaping the
concave faces of the blades; Figure 9 is a front elevation of
equipment 105 shown in Figure 1; Figure 10 is a plan of the front end
of the equipment; Figure 11 is an elevation of the righthand ends of
Figures 9 and 10; 110 Figures 12 and 13 are diagrams to illustrate an
even more acute difficulty than those illustrated in Figures 3 and 4;
and Figure 14 is a sectional diagram of means for lifting the tool
from the work on the 115 return stroke.
In Figure 1, a work fixture 1 is carried on the knee 2 of a shaping
machine, the knee 2 being in turn carried from the cross-slide 3, as
normally used to effect a traverse with 120 respect to a tool carried
by the head 4 of the ram 5, which reciprocates in the top of the
machine frame 6 The fixture 1 includes a base 7, secured on the knee
2, and an upper part 8 making sliding connection at 125 9, 10 with the
base 7, so as to be capable of traversing in the same direction as the
traverse movement of the knee 2 along the cross-slide 3.
An upstanding rear wall 11 of the upper i:30 785,920 contact at
position (iv), though maintained at position (v), is lost at position

8. (vi).
What the invention makes possible is shown in Figures 5 and 6 In
Figure 5, the section 44 has been rotated from position 70 (a) to
position (b), and then again to position (c) so that the tool tip 45
makes similar contact with whatever part of the convex face 46 it
meets by the relative transverse feed movements between the blade and
the 75 tool Similar cutting thus takes place throughout the width of
the convex face.
Similarly with the concave face 47, as shown in Figure 6.
The problem is somewhat complicated by 80 the twist of the blade
section from one end to the other Figure 7 (b) shows the sections 44
(a) and 44 (b) at the root and shroud ends respectively, and makes it
clear that these two sections can have no common axis of 85 curvature
Nevertheless, both are convex to the axis of the flange 16 of the
workholder 14 and the tool tip 45 makes satisfactory contact at all
points along the length of the convex face as it moves lengthwise of
the 90 blade from 44 (a) to 44 (b) Figure 7 (a) showis a convex former
48 A in position in relation to the tracer 30 to control the two tool
tips 45 at Figures 7 (b) and 7 (c) The former 48 A rotates about the
axis of the 95 holder-flange 16, which axis constitutes a very
approximate common axis of curvature of the convex face 46 (a)
throughout the twisted length of that face, but a sufficiently close
approximation for the tool tips 45 to 100 make correct cutting contact
with the convex faces of the blades 35 as they follow the vertical
movements imposed on the tracer when the tracer moves over the length
of the former 48 A 105 In Figure 7, the tracer 30 and the tool tips 45
are at an early stage in the shaping of the convex faces of the two
blades at (b) and (c); the simultaneous rotation of the former and the
blades 35 at each feed 110 traverse of the fixture 1 (Figure 1)
maintains the correct contact of the tips 45 throughout the shaping
operation, i e, as shown in Figure 5 Figure 8 (a) shows a concave
former 48 B with a tracer 30 approximately 115 halfway across the
width of the twisted concave face 47 (a), rotation of the former about
the very approximate axis of curvature provided by the axis of the
holder flange 16 ensuring that the tool tips 45 at 120 (b) and (c)
always make correct cutting contact with the concave faces of the
blades 35.
Figures 7 and 8 show special formers 48 A, 48 B, one for convex
shaping and the other for concave cutting However, since in full 125
scale copying, the former corresponds exactly as to its face with the
face to be shaped, the hydraulic copying equipment according to the
invention enables work-pieces to be put into actual production
immediately a 130 part 8 carries centres 12 (see also Figure 2) for
the location of the rear ends 13 of holders 14, the front ends 15 of

9. which are connected to flanges 1 carried by shafts 17 that pass
through the front portion 18 of the fixture As shown in Figure 1,
wormwheels 19 are carried on the front ends of the shafts 17, and
these are simultaneously driven by worms 20 on a shaft 21 The shaft
carries a ratchet wheel 22, engaged by a reversible pawl 23 on a lever
24 connected by a link 25 to a lever 26 pivoted at 27 The upper end of
the lever 26 carries a bar 28, which lies behind the head 4 of the ram
5, so as to be struck at each full movement of the ram The form wheels
19 and the holders 14 are thus rotated after each cutting stroke of
the ram 5.
On the head 4 are mounted side-by-side a hydraulic unit 29 carrying a
tracer 30, and a hydraulic unit 31 carrying two cutting tools 32, the
transverse spacing of the tracer and the tools 32 equalling the
spacing of the holders 14 The units 29, 31 are conventional, the
former containing a valve controlled by the tracer 30 and serving to
supply hydraulic fluid to the unit 31 so that the latter positions the
tools 32 as dictated by the vertical position of the tracer 30.
The flexible pipes 33 connect the units 29, 31 to each other and also
to a hydraulic pump (not shown) The general height of the head 4 is
controlled by a handwheel 34, and Figure 1 shows the head lifted to
bring the tools 32 quite clear of the holders 14.
Figure 2 shows a turbine blade secured in one of the holders 14 The
root 36 is clipped between pads 37 and the shrouded end 38 is clipped
by a pad 39 A turbine blade being narrow, it is readily possible for
more than one rotatable holder 14 to be accommodated in a shaping
machine, and the fixture 1 thus provides for two blades in two of the
holders 14 to be simultaneously machined by copying from a single
former in the third holder 14 The surface to be machined is shown at
40, machining starting from a "neck" 41 near the root 36, and the tool
32 running into another "neck" 42 near the shrouded end 38 at the end
of each cutting stroke.
The pipe 43 in Figure 1 for the supply of cutting compound to the
tools 32.
Figure 3 shows that if, by mere relative transverse movement between a
blade section 44 and a tool tip 45, the tip is brought from the
position (i) near one edge of the convex face 46 to position (ii), the
point of contact of the tip with the face 46 has changed from one side
to the other of the tip, and if the tip is then brought to position
(iii) the point of the tip has altogether lost contact with the face
46 Similarly, in the attempted shaping of the concave face 47 shown in
Figure 4, the satisfactory point of 785,9-20 785,920 master former has
been made to stipulated dimensions, using a shaping machine of
conventional type and high output, fitted with simple hydraulic units
and with a simple fixture 1 and simple holders 14 for the former and

10. the work It is, however, possible to effect copying to a larger or
smaller scale by appropriate interoperation between the hydraulic
tracer mounting and the hydraulic tool mounting controlled by the
tracer mounting.
A planing machine may be similarly used, the fixture 1 being mounted
on the reciprocating table to provide for the cutting strokes, and for
the rotation of the holders from the reciprocating action, and the
usual feed traverse of the tool cross-slide may be used to provide for
the feed of the tracer and the tools across the former and the
workpieces in the fixture Similarly with a slotting machine, the
fixture 1 being mounted on the work table, which traverses to effect
the feed, the holders being rotated from the reciprocating action In
both cases, an interconnection to the ratchet mechanism of Figure 1
provides for uniform rotation of the holders between cutting strokes.
The fixture 1 of Figure 1 is however, also adapted for combined cam
and hydraulic control of both the rate or rotation and the relative
transverse disposition of the tracer and tools with respect to the
former and the work The provision for this is shown in Figures 9, 10,
and 11, in which the worm wheels 19, worms 20, shaft 21, and ratchet
wheel 22 are dispensed with, and instead of carrying the worm wheels
19 the shafts 17 of the carriers 14 carry pinions 49.
A rack 50 meshes with the pinions 49 It is carried on arms 51 on the
ends of a piston rod 52, the piston 53 of which slides in a cylinder
54 secured to the upper part 8 of the fixture 1 The arms 51 may be
swung about the axis of the rod 52, to bring the rack 50 to the
inoperative position shown in Figure 1 when the worm wheels 19 and the
worms 20 are in use.
With the rack 50 meshing with the pinions 49, movement of the piston
53 in the cylinder 54 causes the minions to rotate Hydraulic
connections 55, 56 to the cylinder 54 are connected to a valve 57
carried by one arm 51, with connections 58, 59 to the connections 55,
56 respectively The valve plunger 60 is engaged by a follower lever 61
operated by one cam 62 on a cam drum 63 (Figure 10) The valve 57
resembles the tracer valve 29 in that any movement of its plunger 60
produces a corresponding movemient of the piston 53, just as any
movement of the tracer 30 produces a corresponding nmovement of the
tools 32.
The cam drum 63 carries a pinion 64 driven by a smaller pinion 64 A on
a shaft 6 d 65 carrying a ratchet wheel 66 driven by a reversible pawl
67 on a lever 68, which is rocked by the head 4 of the ram, much as
the lever 24 of Figure 1, at each cutting stroke A hand wheel 69
(Figure 10) enables the drum 63 to be re-set 7 o A cylinder 70 secured
to the lower part 7 of the fixture 1 has the piston rod 71 of its
piston 72 connected to the upper part 8.

11. Hydraulic connections 73, 74 (Figure 10) are connected respectively to
connections 7 h 75, 76 of a valve 77 carried on the cylinder 70, the
plunger 78 of the valve being engaged by a follower lever 79 operated
by another cam 80 on the drum 63, so that any movement of the plunger
78 produces a corre Si sponding movement of the piston 72 and
therefore of the upper part 8 of the fixture 1.
Although the ratchet wheel 66 and the cam drum 63 are rotated at each
cutting stroke, the resultant movements of the 55 pistons 53 and 72
depend on the form of the cams 62 and 80, and these cams may be shaped
in accordance with the section of the work that is to be shaped in the
machine.
Figures 12 and 13 show an example of a 96 difficult section where
these special cams may be used with advantage In Figure 12, a tool 81
has just shaped the portion 82 of a work-piece 82 A rotatable
counter-clockwise in the direction of the arrow about an axis is 323
The tool 81 has just encountered a step 83, which cannot be shaped by
mere continuation of the rotation At this point, the cam 80 moves the
axis 82 towards the left and the cam 62 rotates the work 82 A mi
clockwise, the corresponding former (not shown) being similarly moved
and rotated, to bring the step 83 to the position in relation to the
tool 81 shown in Figure 13.
The tool is now in correct position for the l O), progressive shaping
cuts required for the step 83, at the completion of which step further
movement and rotation under the control of the cams 62 and 80 bring
the work 82 A into correct position for the tool to lit-} shape the
part 84 of the section.
The cam, valve, and piston mechanism of Figures 9 to 11 thus add
considerably to the versatility of the machine.
Figure 14 shows diagrammatically pro 11 vision for enabling the
cutting tools 32 to be lifted clear of the work 85 on the return
strokes, notwithstanding the maintained contact of the tracer 30 with
the former 86.
The tracer cylinder 29 is carried by a fixed i 2:
part 87 of the ram head 4 and the cutter bar 88 is not only controlled
by the cutter cylinder 31 in direct response to the movement of the
tracer 30 but is also controlled by a piston 89 in a cylinder 90 on
the bar KS 88 The piston 89 is carried by a stem 91 suspended from 87
and adjustable by a nut 92 A nut 93 enables the piston 89 to be
adjusted in the cylinder 90, so that a gap 94 may be varied, in
accordance with the 134 + 785,920 tool clearance required on the
return stroke, say 0 040 inch A hydraulic valve 95 operated by a cam
96 on each stroke of the machine lowers and raises the piston 89 by
the height of the gap 94 and thus lifts the cutter bar 88 by that
amount on each return stroke Consequently, although the tools 32

12. continue to respond to the tracer 30 on the return stroke, they remain
clear of the work by the amount of the gap throughout that stroke, but
are immediately dropped to the work when the piston 89 is raised at
the end of each return stroke.
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* GB785921 (A)
Description: GB785921 (A) ? 1957-11-06
Improvements in valves for gas containers
Description of GB785921 (A)
PATENT SPECIFICATION 72
Inventor:-FREDERICK DERRICK OLIVER.
Date of filing Complete Specification: Feb 17, 1956.
s M 1 Application Date: Feb 18, 1955 No 4911 5 o 5.
Complete Specification Publi 8 hed: Nov 6, 1957.
Index at Aeceptance:-C S 135, VD( 4 X 601: 9 F 11 E:11 X: 20 X), VW 1
C 5 D.
International Classification:-FO 6 k.
COMPLETE SPECIFICATION.
Improvements in Valves for Gas Containers.
We, CALOR GAS (DISTRIBUTING) COMPANY LIMITED, a British Company, of
Poland House, 161-167 Oxford Street, London, W.1, 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 valves for gas containers and more
particularly to valves for attachment to gas storage cylinders for use
in controlling the discharge of gas from such cylinders to a burner or

13. other point of consumption.
The main object of the invention is to provide an improved
construction of such valve which is proof against becoming
frictionally locked in the open position, A further object of the
invention is to provide the valve with means which render it proof
against unauthorised dismantling.
According to the invention the valve comprises a valve pin movable
axially in a valve chamber towards or away from a valve seat to close
or open a passage between the interior of the container and a gas
outlet, a resilient sealing stop within the valve chamber for limiting
the opening movement of said valve pin and sealing means for trapping
lubricant between the resilient sealing stop and a point intermediate
said stop and the end of the valve pin which engages the valve
seating.
The construction and advantages of the valve according to the
invention will be apparent from the following description of one
particular embodiment shown by way of example in vertical
cross-section in the drawing accompanying the Provisional
Spccification.
Referring to this drawing the valve cornprises a body portion 1 having
an externally l,Price 3 s 6 d 1 4 S i screw threaded plug or nipple 2
by means of which the valve is adapted to be screwed into an
internally screw threaded opening in the upper end of a gas storage
cylinder or other container The plug or nipple 2 is provided with an
axial bore 3 which opens into a bore 4 leading to a valve chamber and
through said valve chamber into a bore 6 formed axially in a gas
outlet extension 7 extending at right angles to the plug or nipple 2
The gas outlet extension is provided at its outer end with external
screw threads $ by means of which said outlet is adapted to be
connected to a pipe line (not shown) leading to, for example a gas
burner or other point of consumption This gas outlet extension is
provided with a screw closure cap 9 for closing the gas outlet when
not in use, said closure cap being provided with a sealing washer 1,Q
for preventing possible leakage of gas when the value is disconnected
from the point of consumption.
In the valve chamber 5 is an axially movable valve pin 12 having a
conical part 13 at its inner end adapted to engage a seating 14 to
close the valve Near the conical end of said valve pin is a screw
threaded portion which screws into correspondingly screw threaded
portion 16 of the valve chamber.
By reason of this screw threaded arrangement the valve pin 12 can be,
moved axially by rotation to move the conical portion 13 into or out
of engagement with the valve seat 14 to close or open the valve, The
rotation of the valve pin to open or close the valve is effected by a

14. knurled control knob or the like 17 which is secured to the outer end
of the valve pin by locking nut 18, the portion 19 of the valve pin
being of square or rectangular section so as to prevent relative
rotation of said valve pin 12 and said control knob The said control
15,921 65.
s O ' r_ 11 '.
785,921 knob 17 is provided at its outer end with an axial recess
which houses the locking nut 18 and said recess is normally closed by
a blanking disc 20 which snaps into an annular groove 21 in the
control knob This blanking disc 20 cannot be removed from its seating
without buckling or fracturing said disc so that the valve assembly
cannot be dismantled by unauthorised persons without leaving evidence
that dismantling has taken place The shank portion 11 of the valve pin
12 is slidable in a guide plug 22 secured in a recess in the valve
housing by a grub screw 23 Between the plug 22 and the bottom of the
recess in which it is secured is a rubber or other resilient buffer
sealing washer 24 which forms a resilient stop against which engages
the upper or outer of two annular flanges 25, formed on the valve pin
between the shank and screw portions 11, 15 respectively When the
valve is opened to its maximum limit By this means the valve is
prevented from being friction locked in the open position.
The provision of the two valve pin guide flanges 25 limits side thrust
on the guide plug 22 and permits the upper and lower ends of the valve
pin to float freely in free fit bores, thus eliminating the high
degree of concentricity normally required between the bearings of
rotary pin-like members.
Between the two annular guide flanges 25 is a sealing ring 26 which
permits lubricant to be trapped between said sealing ring and the
sealing washer 24 whereby lubrication of the bore by scavenging action
is ensured.
The valve control knob 17 and the body 1 of the valve are each
provided with an eyelet or the like 27 and 28 respectively to enable a
sealing element, such as a length of wire, to be used to connect the
two parts when the valve is screwed into a newly filled gas storage
cylinder so that the valve cannot be opened without breaking said
sealing element.
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15. * GB785922 (A)
Description: GB785922 (A) ? 1957-11-06
Improvements in or relating to machines for roughing shoe parts
Description of GB785922 (A)
PATENT SPECIFICATION
Index at Acceptance:-Classes 31 ( 1), H 3; and 80 ( 4), F 5 B.
International Classification-C 1 jib F 06 p.
COMPLETE SPECIFICATION.
Improvements in or relating to Machines for Roughing Shoe Parts.
We, THE BRITISH UNITED SHOE MACHINERY COMPANY LIMITED, of Union Works,
Belgrave Road, in the City of Leicester, a British Company registered
under the Companies Acts 1862-1898, do hereby declare the invention (a
communication from United Shoe Machinery Corporation, of Flemington,
in the State of New Jersey, United States of America, a Corporation
duly organised under the laws of the said State of New Jersey, and
having a place of business at 140 Federal Street, Boston, Commonwealth
of Massachusetts, United States of America), 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 is concerned with improvements in or relating to
machines for roughing shoe parts (the term "shoe" being used herein
generically as including outer footwear generally) and is to be
regarded as constituting an improvement in or modification of the
invention of British Letters Patent No.
687,260.
There is hereinafter described one convenient machine, provided by the
invention and illustrative thereof, which illustrative machine (like
the machine described in the Specification of the aforesaid patent)
has a toothed roughing tool or cutter which is particularly suitable
for roughing the margins of the flesh sides of leather outsoles
supported flesh side up, in the machine, preparatory to the attachment
of the outsoles to shoes by cement.
The machine described in the Specification aforementioned comprises a

16. roughing tool having blades which lie approximately on a
frusto-conical surface generated about the axis of rotation of the
roughing tool, a work support comprising a pair of work suplPrice 3 s
6 d l porting sleeves which are yieldable axially independently of
each other, an edge gauge concentric with said sleeves and presenting
an arcuate surface to a workpiece engaging it, a second edge gauge,
and work feeding means comprising a feed roll and a feed wheel
mutually co-operating, the construction and arrangement being such
that the edge gauges may guide a workpiece (for example an
"unattached" outsole), acted upon by the work feeding means, past the
roughing tool The roughing tool, the work support, and the first
mentioned edge gauge are so mutually positioned within the machine
that the roughing tool is offset relatively to the work support to an
extent that causes its axis of rotation to lie outside an edge portion
of a workpiece supported by the work support and engaging said edge
gauge The edge gauge is so located that that portion of it which is
engaged by the workpiece lies between the axis of rotation of the
roughing tool and the portion of the work support engaged by the
workpiece.
The roughing tool is so inclined that its axis of rotation makes an
acute angle with the general plane of the workpiece A general object
of the invention is to provide improvements in a machine of the nature
described above.
With this object particularly in mind the illustrative machine
hereinafter described like that described in the aforementioned
Specification includes an edge gauge, a work support and a rotary
roughing tool so mutually positioned within the machine that the
roughing tool is offset relatively to the work support to an extent
which causes its axis of rotation to lie outside an edge portion of a
workpiece supported by the work support and engaging the edge gauge,
the edge gauge being so located that the portion of the edge gauge
that is engaged by the workpiece lies @ y heo 4 41 '1 7859922 Date of
filing Complete Specification: July 6, 1956.
Application Date: July 7, 1955 No 19609/55.
(Patent of Addition to No 687,360, dated Nov 22, 1951).
Complete Specification Published: Nov 6, 1957.
65.
between the axis of rotation of the roughing tool and the portion of
the work support engaged by the workpiece The roughing tool of the
illustrative machine, also like that described in the aforementioned
Specification, has teeth which lie on a frusto-conical surface
(generated about the axis of rotation of the tool) and is so inclined
that its axis of rotation makes an acute angle with the general plane
of the workpiece The edge gauge of the illustrative machine, again

17. like that of the machine described in the aforementioned
Specification, comprises a cylindrical member concentric with and
surrounded by a work support comprising a pair of concentric workpiece
supporting sleeves which are yieldable axially independently of each
other.
In contrast, however, with the machine described in the aforementioned
Specification the roughing tool of the illustrative machine is movable
horizontally into different operating positions with relation to the
work support in such a manner as to vary the distance inwardly of the
edge of the sole to which the tool roughens the sole Means are also
provided in the illustrative machine for limiting the axial yielding
movement away from the roughing tool, of the inner workpiece
supporting sleeve relatively to the outer one.
When this limit is reached the two sleeves yield together, and thus
obviate the possibility of the inner sleeve standing above the outer
sleeve and obstructing the insertion of a workpiece Means are also
provided for adjusting the resistance of the workpiece supporting
sleeves to yielding away from the roughing tool and consequently for
adjusting the pressure with which the workpiece is held against the
roughing tool To facilitate insertion of workpieces upper and lower
workpiece guiding members, outside the supporting sleeves, are
provided, the upper member comprising an arcuate abutment which is
fixed to a cover of the machine and which surrounds a portion of the
roughing tool This abutment has a workpiece-guiding face substantially
in alignment with cutting edge portions of the roughing tool The lower
guiding member comprises an arcuate rest which surrounds an outer
portion of the outer workpiecesupporting sleeve and has a guiding face
substantially in alignment with the workengaging face of the outer
sleeve These guiding members together form a passage through which the
workpiece may be conveniently presented to the roughing tool.
In order that the above and others of the various objects of the
invention may become more clear, there will now be given a detailed
description, with reference to the drawings accompanying the
Provisional Specification, of the illustrative machine above referred
to It is to be clearly understood however that the particular
illustrative machine is selected for description merely by way of
exemplification of the invention and not by way of limitation thereof.
The several features of the invention will 70 be found set out
respectively as appended
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* GB785923 (A)
Description: GB785923 (A) ? 1957-11-06
Means for mounting a liquid fuel injection pump on an internal combustion
engine
Description of GB785923 (A)
We, C A V LIMITED, of Warple Way,
Acton, London, W 3, 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 has for its object to provide in a simple and
convenient form, a means for mounting a liquid fuel injection pump on
an internal combustion engine.
A means in accordance with the invention comprises a hollow bracket
having an opening in its rear face and in one of its sides, a pair of
interengaging toothed wheels contained within the bracket, one of
which wheels is adapted for spline connection with the driving spindle
of the pump, and the other of which is adapted for engagement with a
driving toothed wheel on the engine.
The invention also comprises the combination of a means as defined in
the preceding paragraph and a pump one end of the body part of which
is adapted to be secured to an open side of the bracket.
In the accompanying drawings Figures 1 and 2 are respectively
sectional side and end views illustrating a pump mounting means in
accordance with the invention.
Referring to the drawings, the hollow bracket a is provided with a
flat rear face adapted to be secured to the exterior of the body part
of an engine b over an aperture which exposes a gear wheel c on, for
example, the cam shaft of the engine, and in the said face of the
bracket is formed an aperture through which can extend into engagement

19. with the said wheel a portion of a gear wheel d rotatably supported
within the bracket Also in the bracket is mounted in lPrice 3 s 6 d l
engagement with the wheel d a gear wheel e having a splined inner
periphery.
One side of the bracket is provided with a flat surface which has
formed therein an aperture through which can be inserted into
engagement with the wheel e the splined end f of the pump driving
spindle g.
One end of the body part h of the pump is adapted to be placed in
contact with the said fiat side of the bracket, and is provided with
lugs or a flange through which securing screws i are inserted
Preferably the said end of the pump body part has also formed thereon
a short spigot j which closely fits the aperture in the side of the
bracket.
By this invention the mounting of a fuel pump on an engine can be
effected in a very simple and convenient manner.
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