4331 4335.output

* GB784738 (A)
Description: GB784738 (A) ? 1957-10-16
Improvements in the manufacture of tubular elements
Description of GB784738 (A)
PATE
4 " C Date of Applic, No 13734/56.
Application mu Complete Spec ENT SPECUICATION 784,7 ation and filing
Complete Specification: May 3, 1956.
ide in France on May 6, 1955.
c 1 fication Published: Oct 16, 1957.
Index at Acceptance:-Classes 12 ( 1), A( 4: 7 82); 44, BE 6 C; 83 (
2), and 83 ( 4), Q( 1 T: 2 A 12: 2 E).
A 122 F; International Classification:-B 23 d, p F 06 b, c.
COMPLETE SPECIFICATION
Improvements in the manufacture of tubular elements I, ANDRE HUET, a
Citizen of the French Republic of 11 Avenue Myron T Herrick, Paris 8,
France, 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 collapsible supports for forging tools e g
in the manufacture of tubular elements and headers.
It is known that, for example in a machine for making apertures in
tubular headers, use is made of a movable jack placed inside the
header and bearing on the bottom of the latter for the purpose of
passing a punch through the opposite wall and thereby producing an
aperture Apertures to be provided on a header are usually numerous and
aligned along generatrices.
The jack which is to produce the series of apertures is then moved
inside said header, or vice versa, from one aperture site to the next
and for this purpose it is carried by a tube or supporting means which
also contains the passages for the fluid feeding the jack, the cooling
passages, the passages supplying gas to the banks of heaters, and so
on The weight of the jack at the end of the support may cause the

latter to sag, which during the displacement for the purpose of making
successive apertures effects a certain scraping or chattering of the
jack on the bottom of the cylinder In addition, despite the rigidity
of the support tube, the jack may be moved slightly out of centre at
the moment when pressure is applied, so that the passage of the punch
through the metal wall is no longer effective in a direction strictly
perpendicular to the axis of the header.
With a view to obviating these disadvantages, Applicant has envisaged
a collapsible lPrice 3 s 6 d l support device which is for example
applicable to the jack placed inside a header.
This device consists in providing the support tube, preferably near
the jack, with one or more cylinders which are directed after the
style of radiating struts and the basis of which comes near the bottom
of the header Inside each of these struts or cylinders are provided
Belleville washers and a ball or roller which bears against the wall
of the header During the displacement of the jack, the support tube
rolls by means of the balls or rollers over the bottom of the header
and at the moment when the jack applies its pressure the rollers,
crushing the stack of Belleville washers, retract inside the struts so
that the sole of the jack bears against the bottom of the header over
a large surface, as should be the case in order to apply a pressure
perpendicular to the axis of the header.
The following description which, with reference to the attached
drawings given by way of example, will enable the invention to be
better understood and in such drawings Figure 1 shows in section the
interior of a header with a jack and its support rod provided with the
device forming the subject of the invention; Figure 2 is a section on
the line II-II in Figure 1, Figure 3 shows in section on a larger
scale the collapsible support.
As can be seen from Figure 1, the interior of the header a in which it
is desired to provide branch apertures contains, in known manner, a
jack b carrying the punch c which, by passing through the wall of the
tube previously pierced at d, will effect the formation of a branch
aperture or nipple at that spot.
The jack b which is to be displaced inside the header a is carried by
a support rod e, on the head g of which it is fixed by a 738 movable
joint f As can be seen in Figure 2, cylinders, of which there are for
example three: h', h 2, h', disposed like radiating struts, are
mounted on the head g of the support rod e Inside each cylinder h I
are provided a ball i and a stack of Belleville washers j, the whole
arrangement being closed by an adjustable threaded stopper k.
The arrangement is such that the ball i projects slightly from the
base of the cylinder h (Figure 3), so that this ball in the normal
state bears on the inside wall of the header a, as seen in Figure 1 In

this way the jack can be easily displaced inside the header because
its bottom I is held at a certain distance from the wall by the balls
i which project below the cylinders h.
The jack is then without difficulty brought in line with the aperture
d where it is desired to provide the nipple When pressure is applied
inside the jack, the punch c rises and is applied against the header,
while the bottom 1 of the jack bears over a wide surface against the
bottom wall of the header, while the balls i are retracted into the
interior of the cylinder h by the crushing of the Belleville washers j
The nipple having been produced and the action of the pressure ceasing
in the jack, the Belleville washers automatically push the balls i
back into the position shown in Figure 3 and the jack can without
difficulty be removed for the purpose of bringing it into the next
position.
The invention is not limited only to the application of this
collapsible support to a tube carrying a jack in a machine for making
branch apertures or nipples It extends to all the applications in
which it is necessary to support a part during its movement in the
course of forging work.
Thus, in operations in which it is desired to close the end of a
header by means of a ram, and where said header has to be gradually
driven in between dies which hammer its end, a collapsible support of
the type just described is provided on the collars intended to support
the header during this work.
It is obvious that modifications of detail may be made in carrying out
the present invention without thereby departing from its scope.
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* GB784739 (A)
Description: GB784739 (A) ? 1957-10-16
Improvements in or relating to automatic rammer mechanisms for guns

PATENT SPECIFICATION
Inventors: JAMES GODDARD SHONTS 79 and SAMUEL HENRY STEPHENSON Date of
application and filing Complete Specification: April 11, 1950.
N' No8835150.
Complete Specification Published: Oct 16, 1957.
Index at acceptance:-Class 92, C 4 C.
Internatioual Classification:-FO 7 d.
Improvemieints in or relfiing to Automatic Rmnner Mechanisms for Guns
We, WESTINGHOUSE EL Ec TRIC INTERNATIONAL COMPANY, of 40, Wall Street,
New York 5, State of New York, United States of America, a Corporation
organised and existS ing under the laws of the State of Delaware, in
said United States of America, 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 1 i be particularly described in and
by the following statement:-
This invention relates to improvements in automatic rammer mechanisms,
and more particularly to ramming devices which are IS adapted to
provide free-flight delivery of rounds of ammunition into the breach
of quick-firing guns.
In the operation of anti-aircraft and other types of quick-firing
guns, it is desirable that a ramming or loading device be provided
which will automatically deliver the individual rounds of ammunition
to the breech of the gun at a rapid rate and in such manner that no
damage to the ramming device can result from premature or accidental
closure of the breechblock, or from failure of the ramming device to
retract itself out of the way of the breechblock Interlock systems of
various types have sometimes been employed with the view of protecting
the gun ramming mechanism from such damage, but these systems
frequently fail to perform their intended function in the event the
damaging action of the breechblock begins before the ramming mechanism
is free and clear of the breech, particularly when the time interval
between successive breechloading operations must be reduced to a
minimum Free-flight delivery of each 4 ( round of ammunition into the
gun, on the other hand, does not require such close proximity between
the gun breech and rammer at the end of the ramming stroke, thereby
positively protecting the ramming mechanism from possible damage which
may result from malfunctioning of the P Frfie 3 s 6 d l breechblock
closing mechanism In addition to providing such positive protection
for the ramming mechanism, free-flight delivery allows each round of

ammunition to be de 50 livered into the breech in a shorter interval
of time and in such a manner that the accuracy of the delivery
operation will not be adversely affected under varying conditions of
pitch and roll or gun elevation It is also 55 desirable that the
ramming mechanism be constructed and operated in such a manner that it
can be reloaded while the gun is being fired, thereby increasing the
rapidity with which successive operating cycles can be per 60 formed.
It is therefore an important object of the present invention to
produce a fully automatic rammer for a quick-firing gun which provides
for a free-flight delivery of each 65 round of ammunition into the gun
breech in a minimum period of time.
It is also an object of this invention to provide an automatic
gun-ramming mechanism which delivers successive rounds of am 70
munition for free-flight movement into the breech of the gun in such a
manner as to protect the ramming mechanisms from damage resulting from
unsynchronised closure of the breechblock or resulting from failure of
75 the rammer actuator to retract the rammer out of the way.
It is also an object of this invention to provide a gun ramming and
loading mechanism which is positive in operation at rapid 80 firing
speeds, and which further reduces the dwell period between the firing
of successive rounds by permitting the next or succeeding round to be
loaded into the rammer while the gun is being fired 85 It is another
object of this invention to produce a gun ramming mechanism which
provides free-flight delivery of the round into the gun breech by
combined centrifugal and linear motion in such a manner that the accu
90 racy of the delivery operation is not adversely affected by the
presence of centrifu43739 a 784,739 gal forces acting on the round.
It is a further object of the instant invention to provide an
automatic gun-ramming mechanism movable along an arcuate path S by a
parallel linkage arrangement in such a manner as to accelerate each
round for freeflight delivery into the breech of the gun, the
gun-ramming mechanism also being movable to a load receiving position
parallel to but out of alignment with the gun barrel, and being
capable of starting the ramming stroke during counter recoil, so that
the ramming stroke is completed before the barrel has reached battery
position.
IS With the above objects in view the improved rammer mechanism in or
for combination with a gun, according to the present invention
comprises a rammer case movable in an arcuate path from a receiving
position for a round of ammunition to a delivery position in such a
manner as to deliver the round into the breech of the gun by free
flight delivery, centering and supporting means movable with the
rammer case to maintain the round in a predetermined aligned position
within the rammer case during the movement in said acuate path to said

delivery position, the said centering and supporting means being
further adapted to direct the course of the round as it leaves the
rammer case under its own inertia for freeflight delivery into the
breech of the gun.
in order that the invention may be more clearly understood and readily
carried into 33 effect, reference will now be made to the accompanying
drawings, in which:Figure 1 is a perspective view showing the rammer
case empty at the load receiving position and with the walking beam
mechanism swung forward.
Figure 2 is a perspective view showing the load starting out of the
rammer case at the start of the rammer buffing operation and with the
walking beam mechanism swung back.
Figure 3 is a side elevational view of the rammer case assembly
showing the sliding collar and cam toggle arms.
Figure 4 is a front elevational view of the rammer case assembly of
Figure 3.
Figure 5 is a bottom sectional view of the rammer case assembly of
Figure 3, showing the latch in the down position and the cam toggle in
the disengaged position.
$ Figure 6 is a fragmentary sectional view of the latch taken along
the line VI-VI in Figure 5.
Figure 7 is a bottom sectional view of the rammer case assembly of
Figure 3 showing the latch in the up position and tihe cam toggle
rollers in the load engaging position.
Figure 8 is a fragmentary sectional view of the latch taken along the
lines VIII-VIII in Figure 7.
Referring now more particularly to the drawings, in which like
reference numerals indicate like parts in the several views, there is
shown generally at 10 a rammer case assembly, preferably of
cylindrical shape, having one end 11 open and the opposite end 70
closed by the buffer assembly 12 A rear support ring 13 is secured by
welding or other suitable means to the rammer case 14 in a position
adjacent to the buffer assembly 12 and has affixed thereto the
diametrically 75 opposed upper and lower trunnions 15 and 16
respectively Another supporting ring 17 is similarly secured to the
forward portion of the cylindrical case 14 and has an upwardly
extending trunnion 18 affixed thereto 80 Between the forward and rear
support rings 17 and 13 is an intermediate support ring 19, also
secured to the case 14 and having a downwardly extending trunnion 20
welded thereon 85 The main drive arm 23 for the rammer assembly 10 has
one end 24 pivotally supported on the trunnion 18 of the forward
support ring 17 and has a bifurcated yoke 25 at its opposite end which
is pivotally sup 90 ported by the bearing bolts 26 on the drive arm
support bracket 27 of the main support base 28 An actuator arm 29,

preferably formed integral with the main drive arm 23, extends
angularly outwardly therefrom and 95 has a free end 30 pivotally
attached by the pin 33 to one end of the walking beam 34, the latter
being pivotally attached by the pin to one end of a lever 36 whose
opposite end is pivotally supported by the pin 37 on 100 the bracket
extensions 38 carried by the main support base 28 Thus, the walking
beam 34 is free to rock about the pin 37 as a centre, and has its
other end pivotally connected by the pin 39 to a fitting 40, which is
1 jo secured to the free end of the piston rod 43 of the hydraulic
actuator 44 The actuator 44 is pivotally supported by the transverse
pinion 45 for free rocking movement within the bracket extensions 46
carried by the main 110 support base 28, so that the linear motion of
the piston rod 43 of the actuator 44 is converted into rotary motion
by the walking beam 34 and linkage elements associated therewith Thus,
the fluid under pressure 115 may be supplied to actuate the hydraulic
cylinder 44 through suitable flexible tubing not shown, which
communicates the cylinder 44 with an easily controlled fluid supply
system of conventional design The yoke 25 12 C of the main drive arm
23 is keyed to the bearing bolt 26 on one side of the support bracket,
and a short link member 47 has one end 48 keyed to the bolt 26 on the
opposite side of the bracket 27 Pivotally attached 121 by the pin 49
to the other end 50 of the link 47 is a drag link 51 having its
opposite end 42 pivotally attached by the pin 52 to a short arm 53
keyed at its other end to the bolt 54, which is journalled in the
supporting struc 13 ( thereof and the forward support ring 17 The
assembly 72 includes a three-segment, fixed collar 73 and a coacting
sliding collar 74 which tends to move longitudinally along the rammer
case 14 toward the open end 11 70 thereof in accordance with the
resilient pressure exerted by a compression spring 75 having one end
76 which seats in an annular shoulder 77 formed on the sliding collar
74 and another end 78 which coacts with the 75 adjacent side 79 of the
forward support ring 17 Three circumferentially spaced apart support
brackets 82 are secured to the fixed collar 73, the extension 821
thereof being disposed on opposite sides of the three circum 80
ferentially spaced apart oblong slots or apertures 83 which extend
through the rammer case 14 adjacent the open end 11 thereof.
Pivotally supported by a bolt 84 on each pair of brackets 82 are the
circumferentially 85 spaced apart cam toggle arms 85 One end of the
toggle arms 85 supports a short pin 86 which serves as an axle for the
toggle rollers 87 The opposite end of each toggle arm 85 has a notch
88 cut therein so as to 90 coact with the edge of the apertures 83
when the toggle arms 85 are in the fully disengaged position shown in
Figure 5, thereby allowing the cam trigger 89 to extend through the
aperture 83 and into the interior of the 95 rammer case 14 A pin 90

disposed above each notch 88 pivotally attaches one end of spaced
apart links 92 to the toggle arm 85 The opposite end of each link 92
is pivotally attached by 100 a pin 93 to one of the three radially
spaced apart brackets 94 which are carried by the sliding collar 74
Whenever a closely fitting round or ammunition 21 is inserted into the
rammer case 14 with the toggle arms 85 in 105 the fully cocked
position illustrated in Figure 5, direct contact between the rim and
the cam triggers 89 will uncock the toggle arms 85 by moving each of
the pins 90 past the dead centre position, thereby enabling 110 the
sliding collar 74 to move forward under action of the compression
spring 75 so as to impart a pivotal movement simultaneously to all of
the toggle arms 85 about the bolts 84 as an axis In this manner the
cam rollers 115 87 are gradually depressed through the apertures 83 so
as to exert a resilient pressure radially inwardly against the
exterior surface of the round 21 inserted in the rammer case 14 The
pressure exerted by the 120 rollers 87 on the surface of the round 21
is applied substantially uniformly by all of the rollers 87 to the
coacting surface of the tapered or untapered round 21 so that the
latter is supported thereby with its axis sub 125 stantially in
alignment with the longitudinal axis of the case 14, and so that a
substantially uniform annular space is maintained between the interior
surface 91 of the case 14 and the exterior surface of the round 21 ?
30 ture 41 for free turning movement therein.
The other end of the bolt 54 is affixed to the rear auxiliary drive
arm 55, which has its free end 56 pivotally supported on the trunnion
15 carried by the ring 13 Although most of the torque required to move
the rammer case assembly 10 is imparted thereto through the main drive
arm 23, a small portion of the driving torque is transmitted by the
auxiliary drive arm 55 to the case assembly 10 through the short link
47, the drag link 51, and bolt 54 The rear auxiliary drive arm 55 and
associated linkage components also insure that all components of the
entire linkage system follow through the dead centre position in such
a manner as to impart a smooth and uninterrupted swinging movement to
the rammer case assembly 10.
A lower support arm 57 has one end 60 thereof pivotally supported on a
trunnion 58 secured to the forward of the aft support bracket 59, and
the arm 57 has its other end pivotally attached to the trunnion 20 of
the intermediate support ring 19 Another lower support arm 62 has one
end 71 pivotally attached to the lower trunnion 16 on the rear support
ring 13, and has its other end secured to one arm 63 of the bell crank
64 which is pivotally supported on the aft support bracket 59 by the
pin 65 The other arm 66 of the bell crank 64 carries a pin 61 having
its free end swivelled in the free end 67 of the link member 68 The
opposite end of the link member 68 is secured to a movable disposal

conduit or case deflector chute 69 so as laterally to move the same in
accordance with the movement of the bell crank 64 as it turns about
the Pin 65 as an axis Thus, the main drive arm 23, the rear auxiliary
4 g drive arm 55, the lower support arms 57 and 62, form a parallel
linkage arrangement adapted to support the rammer case assembly 10 for
a free swinging movement from the load receiving position illustrated
in Figure 1 to the load delivering position at the end of each ramming
stroke as illustrated in Figure 2 An endless conveyor 172 having a
plurality of cam controlled automatic clamping mechanisms 173 thereon
preferably so delivers individualy in time sequence the case assembly
10, when positioned as illustrated in Figure 1, a round of ammunition
or projectile 21 Upon the operation of suitable conventional sequence
control or interlock devices, hydraulic fluid under pressure may be
supplied to the actuator 44 so as to extend the piston rod 43 to exert
a thrust on the main drive arm 23 and the auxiliary arm 55 so as to
move the rammer case assembly 10 to the delivery position at the end
of the ramming stroke as illustrated in Figure 2.
Figures 3 to 8 inclusive illustrate the preferred form of construction
for the toggle arm assembly 72 which is positioned on the rammer case
14 between the open end 11 784,739 which is inserted therein.
Laterally supported on the external surface of the case 14 and in a
position between two of the three circumferentially spaced apart
toggle arms 72 is a fourth toggle arm assembly 140, which includes a
link member 141 pivotally attached by a pin 142 to a bracket 143,
which is carried by the sliding collar 74, and a second link member
144 pivotally attached by the pin 145 to the fixed collar 73 One end
of link member 144 is pivctally attached to the link 141 by a pin 146,
and the free end of the link 144 rotatably supports a roller 147 which
is adapted to be depressed into the cavity 31 of the case 14 through a
fourth aperture 831 therein When in the fully depressed position
illustrated in Figure 7, the roller 147 is toggled past the
dead-centre position in such a manner as to maintain a predetermined
spacing between the coacting surface of the round 21 and the adjacent
interior surface of the case 14 Thus, the toggle arm 140 absorbs any
thrust imnposed upon it by the centrifugal forces present when the
raninmer case assembly 10 is moved to the delivery position
illustrated in Figure 2, thereby preventing any centrifugal forces
created by arcuate movement of the round 21 from unequally actuating
the toggle arm assembly 72 in such a manner as to adversely affect the
accuracy of the free-flight delivery of the round 21 Whenever a round
21 is ejected from the rammer case 14, the toggle arm 140 is actuated
by the coacting rim of the round so that it assumes the position
illustrated in Figure 5, which position is maintained until the next
sliding movement of the collar 74 for the next loading cycle is

initiated by coaction between the rim of the round 21 and the cam
triggers 89 of the camrn toggle arms 85.
Preferably the hydraulic actuator 44 incorporates a hydraulic buffing
means adapted to decelerate the swinging movement of the rammer case
assembly 10 both in the load receiving position illustrated in Figure
1 and in the load discharging position Illustrated in Figure 2 In the
latter position, the forward movement of the rammer case 14 is rapidly
decelerated at a predetermined rate by the buffing action of the
hydraulic actuator 44 with the result that the round 21 moves forward
within the case 14 because of its inertia, as soon as relative
movement is permitted by release of a latch assembly 22.
The latch assembly 22 is so constructed and arranged as to engage the
rim of the round 21 so as to hold it within the case 14 until such
time as the buffing means for the hydraulic actuator 44 begins to
decelerate the forward movement of the case 14 just prior to
completion of the ramming or delivery cycle As the inertia of the
round 21 carries it forward after the case 14 comes to rest, the rim
of the round 21 slides along the interior surface 91 of the case 14
with the toggle rollers 87 maintaining the axis of the round 21 in
substantial alignment with the longitudinal axis of the case 14 As
soon as 70 the round 21 moves forward within the interior cavity Aof
the case 14 to the position where the rim of the round 21 engages with
the toggle rollers 87, these rollers are caused to impart a pivotal
movement to the cam 75 tocggle arms 85 to position the arms 85 and
linkl 92 from the uncocked position illustrated in Figure 7 to the
fully cocked position illustrated in Figure 5, thereby moving the
sliding collar 74 along the case 14 in 80 opposition to the action of
the compression spring 75 Thus, ihe cam toggle arms 85 rotate past
dead centre and are automatically, held by the suring 75 in the
position required for the next ramming or delivery 85 cycle.
The caml actuated latch assemrbly 22 coacts with tihe rim of tihe
round 21 to secure it withlir the ramwmer case 14, until the case
assembly 10 has been positioned for proper 90 delivery anrd until such
time as the buffing action of the hydraulic actuator 44 begins to
decelerate the forward movement of the case 14 as it approaches the
delivery position illustrated in Figure 2 The buffer assem 95 bly 12
is preferably of the fluid dampening type, absorbs the kinetic energy
of the round 21 as it comes to rest within the rammer case 14 The
buffer assembly 12 preferably is constructed as an integral unit which
100 may be readily removed from the rammer case 14 for replacement or
repair by removing the attaching bolts 97 The buffer assembly 12
preferably is formed by a corrugated rubber bellows 98, one end of
which is se 105 cured by rivets 100 to the inner surface of a
cup-shaped member 99, and at the other end of the bellows 98 is

secured to an interior member 101 having an annular ring 102 on one
side thereof adapted to form a fluid re 110 taining well 103 within
the bellows 98, which may be filled with oil 104 or other suitable
hydraulic fluid An orifice rod or plunger secured to the interior of
the member 99 by the bolt 106 has a conical frustum end 115 portion
107 of slightly smaller diameter than the well 103 and is adapted to
coact with the ring 102 to form an annular fluid dampening recess of
substantially uniform predetermined configuration around the periphery
of 120 the orifice plunger 105 If desired, the member 99 may have
cooling fins 108 on the exterior surface thereof to facilitate cooling
of the buffer 12, and may have an annular flange 109 thereon adapted
to coact with a 125 sliding collar 110 A compression spring 111
interposed between spaced annular rings 112 and 113 which threadedly
engage with the members 99 and 101 respectively, tends at all times to
move the orifice plunger 105 out 130 784,739 the fixed pins 135 and
the other end thereof secured to the ends of the roller 136 so as to
normally tend to force the long arm 132 of the latch 127 through the
aperture 133 as shown in Figure 8 As the incoming rim of 70 the round
21 slides past the latch 127, the long arm 132 thereof is depressed in
opposition to the action of the torsion springs 134 until the rim
passes over the latch and the round 21 is retained in place within the
in 75 terior 31 by locking engagement between the rim thereof and the
vertical surface 137 of the arm 132, which position is maintained
until the latch 127 is depressed in opposition to the action of the
torsion springs 134 by 80 coaction between the sliding cam 122 and the
short arm 131 as illustrated in Figure 6.
Rebound energy of the round 21 in striking the buffer assembly 12 may
readily be absorbed by the outer spring 124 without inter 85 ference
with the normal operation of the latch assembly 22, since the pins 128
which pivotally support the latch 127 are free to move along the
oblong slots 129 and the short arm 131 thereof is free to slide the 90
washer 121 within the housing 116 in opposition to the resilient
action of spring 124.
Such limited sliding movement of the latch 127 permits the absorption
of substantial rebound energy without subjecting the latch 95 assembly
22 to severe strain or adversely affecting its normal operation.
OPERATION.
In operation, the parallel linkage mechanism which supports the rammer
case 14 is 100 moved to the position illustrated in Figure 1 by
retracting the hydraulic actuator 44 so as to move the walking beam
assembly 34 to its most forward position The buffing action of the
hydraulic actuator 44 gradually de 105 celerates the rammer case 14 as
it comes to rest in the load receiving position so as to avoid
subjecting the component parts of the rammer assembly to excessive

shock loads.
As soon as the rammer case 14 has come to 110 rest in the position
illustrated in Figure 1, it is free to receive a round or projectile
21 from a suitable loading point such as an endless chain carrying
automatic clamping devices which may release by cam or other 115
suitable means as the round 21 is transferred from the hoist conveyor
to the ramming or delivery assembly 10 Before each round is injected
into the rammer case 14, the cam toggle arms 85 are in the cocked-open
posi 120 tion so as to readily receive the incoming round 21 from the
hoist, as shown in Figure If the rounds 21 to be delivered by the
rammer are of considerable length, each round preferably is engaged by
a pair of 125 automatic clamping devices, the first of which may be
released at the beginning of the transfer operation by suitable cam so
asto allow the remaining engaged clamps to supply the thrust required
to transfer the 130 of fluid entrapping engagement with the fluid well
103 so that a maximum amount of fluid 104 will be present within the
well 103 at the beginning of each energy absorbing cycle of the fluid
dampening buffer 12 The spring 111 therefor repositions the buffer
assembly 12 to its normal position after each buffing operation has
been completed and the round 21 has come to rest within the rammer
case 14, whereupon the rim of the object 21 ceases to exert pressure
upon the coacting surface 114 of the buffer assembly.
The latch assembly 22 positively engages with the rim of the round 21
to secure the same within the rammer case 14 throughout most of the
delivery cycle and until the buffing means of the fluid actuator 14
begins to decelerate the forward movement of the rammer case 14 The
latch assembly 22 includes a cam follower rod 115 slidably supported
within a housing 116 affixed to the bottom of the rammer case 14 One
end of the rod 115 carries a roller 117 adapted to coact with a cam
quadrant 118 affixed to the end of the lower support arm 57 which is
journalled on a trunnion 20 When the case assembly 10 is in the
position illustrated in Figure 1, the cam quadrant 118 is in
theposition shown in Figure 8, and does not contact the roller 117 to
move the rod 115 until the ramming or delivery cycle of the case 14
has been substantially completed Coaction between the quadrant 118 and
the rod 115 preferably occurs just prior to the action of the buffing
means of the actuator 44 in decelerating the forward movement of the
loaded rammer case 14 The portion 119 of the rod 115 furthest removed
from the roller 117 preferably is of a substantially lesser diameter
and forms a shoulder 120 at one end thereof and at its opposite end
extends through the washer 121 to support a sliding cam 122 attached
to the outer extremity thereof The washer 121 engages with the rod
portion 119 in a free sliding manner and the washer 121 is itself
slidably retained within the housing 116 An inner compression spring

123 exerts resilient pressure on the shoulder 120 and on the washer
121, thereby tending to force the washer 121 into contact with the
abutting surface of the cam 122 whenever the roller 117 is not in
contact with the quadrant 118 An outer spring 124 exerts resilient
pressure on the closed end 126 of the housing 116 and against the
washer 121 A latch 127 is pivotally supported by the pin 128 in a
horizontally disposed oblong slot 129 of the supporting member 130,
and has a short arm 131 adapted to coact with the sliding cam 122 and
a long arm 132 adapted to normally project itself upwardly into the
interior 31 of therammer case 14 through theaperture 133 formed in the
bottom portion thereof The torsion springs 134 have one end thereof
secured to 784,739 rounds to the rammer 14, the rim portion thereof
being inserted into the rammer case first If desired, an independent
emergency rammer positive return mechanism may be provided to assure
that the rammer assembly 10 is in the fully retracted position to
receive the round 21 in the event the parallel linkage mechanism
should for any reason fail to fully retract the ramming device As soon
as the round 21 has travelled a few inches into the rammer case 14,
the rim of the round 21 engages the cam shaped projections of the cam
toggle arms 85 to force them beyond the dead-centre position and cause
the three rollers 87 carried by the toggle arms to contact the tapered
or untapered exterior surface of the round 21 for supporting the same
within the rammer case 14 in a longitudinally slidable manner, while
at the same time keeping the round 21 centered with its axis
substantially concentric with the axis of the rammer case 14
throughout the rammer loading and unloading operations.
The automatic clamp on the chain hoist which remains engaged with the
round 21 during the rammer loading operation continues to drive the
round 21 into the rammer case 14 until completely released from
clamping engagement by the suitable cam actuated clamp release
mechanism forming part of the chain hoist assembly During the final
portion of the rammer loading stroke, the round 21 continues to move
under its own inertia until it strikes the buffer assembly 12 at the
closed end of the rammer case 14 where it strikes the latch 127 which
engages with the rim of the round 21 to retain it in a position within
the rammer case 14.
In its centered and last position within the rammer case 14, the round
21 begins its travel along a delivery path determined by the action of
the parallel linkage supporting mechanism which is operated by torque
supplied to the main and auxiliary drive arms by the hydraulic
actuator 44 and its associated interconnecting linkage elements During
the delivery stroke of the rammer assembly10, the action of the
compression spring 75 tends to centre the round 21 within the case 14
by exerting a thrust upon the sliding collar 74, the toggle arm bolts

84, and the toggle arms 85 However, during the first portion of the
rammer delivery stroke, the round 21 is subjected to rapid
acceleration along an arcuate path, and the centrifugal forces which
result tend to unbalance the normal centering action of the toggle arm
assembly 72.
The centrifugal force exerted by the round 21 during ramming tends to
force the round horizontally outwardly along the supporting drive arms
and tends to disturb the normal centering action of the toggle arms 85
which direct the round 21 along its free flight delivery course This
disturbing centrifugal action is therefore taken up by the fourth arm
140, which is toggled over the deadcentre position during the loading
operation so as to formn a positive stop which eliminates the tendency
of centrifugal action to 70 disturb the normal alignment of the round
21 within the case 14.
At a predetermined point along the arc of travel for the rammer
delivery stroke, the actuator 44 ceases to apply additional ram 75
ming power, and begins a buffing action which buffs the rammer 10 to a
stop at the end of its delivery stroke, at which time the centre line
of the rammer case is in alignment with the axis of the barrel, and
the 80 open end of the rammer is within the recoil area of the gun,
but is not in sufficient proximity to the breech to be damaged by
inadvertent, unsynchronised movement of the breechblock Just prior to
the beginning of 85 the buffing action of the actuator 44 near the end
of the ramming stroke, the cam roller 117 contacts the cam quadrant
118 carried by the lower forward support arm, thereby actuating the
cam rod 115 so as to depress 90 the latch 127 to the position shown in
Figure 6 so that the round 21 is free to move out of the rammer case
14 Since the round 21 has been unlatched from the rammer case 14 and
has been accelerated to a relatively high 95 linear velocity before
the beginning of the buffing operation, the round 21 will move out of
the rammer case 14 due to its own inertia, first along the guided
flight course determined by the centralising action of the 100 toggle
arm assembly 72, and secondly along a free-flight course leading into
the breech of the gun During the buffing operation, the three cam
toggle arms 72 exert equalised radial forces on the case of the round
21 as 105 it leaves the rammer case 14, thus supporting and centering
the round 21 in the rammer case under maximum conditions of pitch and
roll The round 21 is also supported and centered by the close fit
between the rim 110 and inside wall of the rammer case 14 As the rim
of each round 21 leaves the rammer case 14 to begin its free-flight
delivery course, it cocks open the three cam toggle arms 72, forcing
the collar 74 back, which rotates the 115 anti-centrifugal force
toggle arm 144 upward, and at the same time energises an interlock
which causes hydraulic pressure to be applied to the retract side of

the hydraulic actuator to initiate the retraction stroke The 120 case
deflector chute 69 is actuated by the return motion of the rammer
stroke to bring it into a position behind the breechblock but beyond
the recoil area of the gun so as to receive the empty projectile case
after the 125 gun has been fired Thus, the deflector chute 69 is
actuated by the rammer assembly 10 in such a way that it will not
interfere with the travel of the rammer at any time The rammer
assembly 10 is then retracted to the 130 784,739 a manner as to tend
to centre the round when inserted rim end first within the rammer
case, a releasable latch adjacent the said buffer assembly and adapted
to engage with 50 the said rim to retain the said round within the
said case during a substantial portion of the arcuate movement of said
case to delivery position, and positive means resisting the tendency
of centrifugal action to inter 55 fere with the normal centering
action of the cam toggle arms during the said arcuate movement of the
rammer case.
A rammer mechanism as claimed in any of the preceding claims including
a 60 parallel linkage arrangement adapted to support the said rammer
case for movement in the said arcuate path from a load receiving
position to a load delivery position behind the breechblock of the gun
and in substan 65 tial alignment with the axis of the breech and
actuating means for the said parallel linkage mechanism adapted to
impart a predetermined buffing action to the said rammer case at each
end of the said arcuate path 70 6 A rammer mechanism as claimed in
* Sitemap
* Accessibility
* Legal notice
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* 5.8.23.4; 93p
* GB784740 (A)
Description: GB784740 (A) ? 1957-10-16
Improvements in and relating to flexible hose assemblies

PATENT SPECHFICATION
Date of filing Complete Specification: March 10, 1954.
Application Date: Dec 11, 1952 No 31460/52.
Index at Acceptance:-Classes 99 ( 1), G 2 (B: K), G 24 E( 1: 2: 5);
and 99 ( 2), P 1 A( 8:9:15 B), P 1 B( 5 B: 7: 8).
International Classification:-F 061.
COMPLETE SPECIFICATION.
Improvements in and relating to Flexible Hose Assemblies.
We, WALTER AP THUR MELSOM, a British Subject, of 112 Vivian Avenue,
Wembley Hill, Wembley, Middlesex, and BOW Dnu N (ENGINEERS) LIMITED, a
British Company, of Bowden Works, Victoria Road, Willesden Junction,
London, N W 10, 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 flexible hose assemblies which
incorporate end fittings by which the hoses are adapted to be coupled
to other apparatus, and especially to such assemblies which are
suitable for pressures of from 500 lb per square inch upwards.
The hoses of these assemblies usually comprise an inner tube of
resilient material such as rubber (natural or synthetic) or
thermoplastic synthetic material and a surrounding flexible
reinforcing tube of metal, usually having fabric covering, e g, made
up of ribbon-like groups of fine high-tensile steel wires braided to
tubular form and with or without a fabric covering, the reinforcing
material being embedded between the inner tube and an outer tube of
resilient material.
The manufacture of such hoses is a comparatively expensive
undertaking, and when the hoses with their fittings are in service
there is a difficulty in inspecting and checking them for faults,
particularly in the inner resilient layer In aircraft servicing
stations, for example, where the engines and other parts of the
aircraft are periodically dismantled for checking, inspection for
faults of hose assemblies is hindered by the inaccessibility of the
vulnerable inner resilient layer Greater facility for testing the
inner resilient layer is also wanted in the manufacture of these hose
assemblies There is a need therefore for a hose assembly whereof the
inner resilient layer and the reinforcing layer can be separated from
one another and conveniently reassembled in operative relation to one
another with the aid of the end fittings and preferably so that the
inner resilient layer can be replaced and the same reinforcing layer

and end fittings re-used.
To these ends the present invention consists in a hose assembly
adapted to be coupled to other apparatus and comprising a flexible
armouring consisting of or comprising one or more flexible metallic
tubes and a separate inner tube of resilient material with or without
one or more tubular layers of textile reinforcing material and closely
sheathed by the said armouring, the inner tube being secured between
inner and outer members of end attachments and the armouring having
end attachments, the inner tube and the armouring being endwise
clamped by clamping components co-operating with said attachments so
that the inner tube and the armouring co-operate to form an armoured
hose, the construction being such that the inner tube can be freed and
withdrawn with its attachment through the armouring In the term "
textile reinforcing material " we include material made of threads of
synthetic material.
At each end a locking ring or like may be provided through which the
clamping pressure is transmitted from one attachment to the other at
that end, the locking ring or the like being adapted to be freed,
after unclamping components, in order to free the inner tube Each
locking ring, e g, a split ring, collet or collar or the like, may be
sprung into an annular groove in the end attachment of the inner tube
and abut the end attachment of the armouring.
The clamping components may be cooperating members screwed or bolted
together.
784,740 8 s One of each of co-operating pairs of clamping components
may be slidably retained in connection with the armouring and have an
inward flange to engage an abutment formed by the corresponding end
attachment on the armouring Such components are hereinafter called the
"nuts " The other of the companion components (hereinafter termed the
"screws ") may be completely detachable from the inner tube and the
armouring.
The said inner tube and the armouring can be produced separately and
cheaply in relation to the aforesaid hoses with embedded I reinforcing
tubes of metal usually fabric covered.
The inner tube with or without a fabric e.g, cotton, reinforcing tube
embedded within the resilient material, is closely sheathed by the
armouring The armouring may consist of a single tube, e g, made of
ribbon-like groups of fine high tensile steel wires braided as
aforesaid, or of two or more such tubes one within the other, and if
desired with a layer or layers of fabric, e.g, cotton braid, or of
rubber, between the metal layers, the clearance between the inner tube
and the armouring being made as small as is practicable so that any
tendency of the internal fluid under pressure to distend the inner
tube radially outwards is resisted by the armouring The braided

armouring may be surrounded by a closewound wire coil or a coil as
sold under the registered Trade Mark "Bowdenex ' and constructed
according to Patent No 412,367.
Inasmuch as the attachments at each end of the inner tube may be alike
and the attachments at each end of the armouring may be alike,
reference will be hereinafter made to the attachments at one and the
same end only of the inner tube and armouring.
The end attachment on the inner tube may comprise ferrule and insert
members between which the tube is gripped and sealed.
The ferrule and insert members may be fixed to the inner tube by
permanently deforming one of them, e g, by swaging or contracting the
ferrule around the inner tube.
They may be otherwise secured, e g, the insert may have a conical or
tapering external surface and be forced into the inner tube so as to
press the resilient material outwards 5,5 firmly against the inside,
preferably cylindrical, surface of the ferrule, the resilient material
being forced into one or more annular or helical, preferably
continuous grooves in the said surface The inner tube e O may be
inserted between the ferrule and insert so as to leave a cavity
between its inner end and the ferrule and insert, the insert, in
entering the inner tube forcing the resilient material into said
grooves so that i,5 the outer skin is anchored and the resilient
material flows in opposite directions and fills the cavity as the
tapering insert moves into the inner tube.
The ferrule may be let into an annular recess in the wall of the inner
tube so that its 70 external diameter or finished external diameter
when it is swaged, does not exceed or is substantially the same as,
that of such tube.
Each end attachment of the armouring may comprise inner and outer
rings between 75 which the armouring is secured The armouring may be
frictionally gripped by the rings by relative axial movement thereof,
if desired with a wedge action The end portions of the armouring may
be passed 50 through and folded back onto the outside of the inner
ring and the outer rilig forced axially over the folded back material
to grip it onto the inner ring The armouring need not be folded back
but the outer ring i; 5 may have an inwardly extending collar which
grips the armouring between it and the end of the inner ring where the
armouring has been bent outwards to lie between the rings and
preferably also gripped by the f"e inner and outer faces of the outer
and inner rings, when the outer ring is forced over the inner ring.
The tapering or conical insert may have an end collar and this may
co-operate with l)5 the screw and preferably also with the ferrule to
effect a metal to metal seal between these parts when the screw and
nut are screwed together The said parts may make an edge to face

sealing engagement so that 10 o) under the clamping pressure the edges
bite into the faces to promote effective sealing.
Gaskets may however be used.
The nut may engage behind the forward end of one of the rings whilst
the serew 10,5 engages the aforesaid collar on the conical or tapering
insert so that when the screw and nut are screwed home, the ferrule
bears on the rear side and the other ring on the forward end of the
locking ring, the 110 inner and outer gripping rings are forced
axially towards one another, if they are not already forced home
completely, to tighten their grip on the metal armouring and the
collar of the insert is sealed with the screw 115 and if desired with
the ferrule The term "forward end" means the end nearer to the body of
the hose.
In another form the locking ring may abut the wall of a recess in the
rea_; of the 120 attachment on the armouring and the screw may be
provided with an axial bore having a conical enlargement at one end
against which a rounded or other suitable shaped sealing face of the
end attachment of 125 the inner tube is engaged to make a metal to
metal seal, when the screw and nut are screwed together with the
flange of the nut engaging the aforesaid abutment on the end
attachment of the armouring 130 784,740 inner peripheral portion 6 to
increase the surface area of the end wall 6 a which provides an
abutment as is hereinafter described.
The outer ring forms with the inner ring a deep annular recess in
which the rough ends 70 of the braided wire tubes are received The
rings are anchored to the tubes permanently by brazing, swaging or
otherwise andlor by forcing the outer ring axially over the armouring
around the inner ring The 75 armouring assembly is provided at each
end with an internally screwed nut 7 which is provided with an inward
flange 8, the said nut being slidden on to the armouring before the
end attachment is completed With the 80 end attachments fixed the nuts
are retained as part of the armouring assembly, each being prevented
by the engagement of the flange with the aforesaid abutment wall 6 a
from displacement off the armouring 85 The inner tube 9 is of
resilient material, e.g, of suitable thermoplastic synthetic material
or a rubber preferably reinforced by a fabric, e g, cotton, layer 10
The end attachments of this tube each consist of a 90 ferrule A and an
insert B which may be separate components as in the example
illustrated or may be integral with or joined to one another The
internal peripheral wall of the ferrule tapers inwards at 11 to a 9)5
central bore 12 and the external peripheral surface of the ferrule is
curved at the outer end to form a sealing face 13 An annular groove 14
is formed in the external periphery of the ferrule and one side of
this groove may 100 taper gradually as shown at 15 The ferrule is

swaged or contracted around the end of the inner tube and the insert
so that its finished diameter is substantially the same as the
external diameter of the tube The 105 inner tube with its end
attachments provides a simple low or medium pressure hose unit, which
is a slidable fit into the armouring with the minimum possible
clearance The end attachments of the inner tube 110 and the armouring
are coupled by a spring ring 16 which is forced over the sealing face
13 into the groove 14 and abuts the radial wall of the recess 5 The
screw 17 is screwed into the nut 7, and has a radial wall 18 Its 115
inner periphery tapers at 19 to a bore 19 a, the tapering portion 19
providing an appropriately smooth or machined face to cooperate with
the sealing face 13 of the ferrule A When the screw and nut are 120
screwed together with the flange 8 abutting the abutment face 6 a, the
co-operating sealing faces 13 and 19 are brought into sealing
engagement, and the inner tube is prevented from movement in either
direction 125 When the screws 17 are detached the inner tube can be
displaced endwise to a small extent sufficient to enable the locking
ring to be removed.
The component 17 of the end fitting may 130 The screw component may be
constructed in any suitable way for coupling the hose assembly to
other apparatus, e g, it may have a reduced boss rotatably supporting
a a union nut, e g, in the manner described and claimed in our prior
Patent No 540,490.
The removal of the inner tube is accomplished after unscrewing the
screw components, by sliding back the nuts along the 1 f armouring,
and removing the locking rings.
The armouring with its end attachments and the two nuts retained by
the said end attachments may form an article of manufacture complete
in itself The inner tube with its end attachments may likewise form a
complete article of manufacture and the latter can be replaced by
another such article, utilising the same armouring assembly and the
same detachable clamping components In certain cases the inner tube
with its end attachments can be removed and examined and checked and
then reinserted if found in order without any disturbance of the
sealed connection of the end attachments to the tube Where the inner
tube is gripped with the aid of a tapering insert, there may be some
tendency when the attachments are not clamped by the clamping
component for the resilient material to recover and move the insert
somewhat towards the outside of the tube but if it becomes unsealed it
can be readily forced in again when re-clamped or for test purposes
The tapering insert will generally be forced in by tools before
applying the detachable clamping component Where the armouring is
gripped between rings by relative axial movement of the rings, the
grip is usually effected by tools before the clamping screw is applied

When the clamping components are subsequently unclamped the armouring
remains gripped between the rings The clamping operation ensures that
the tapering insert will be forced fully into the inner tube and that
the rings will effectively grip the armouring.
The drawings accompanying the Provisional Specification illustrate two
constructional forms of hose assemblies according to the invention by
way of example, Figure 3 being a drawing accompanying the Complete
Specification.
In Figure 1 the armouring comprises two tubes 1, la of braided wire,
disposed one ic closely within the other, each tube being made of
ribbon-like groups of fine high tensile steel wires braided to tubular
form.
One or each tube may have a fabric cover if desired The armouring has
similar end attachments at each end Each said attachment consists of
inner and outer rings 2, 3, the inner ring having an integral external
collar 4 forming a thickened end which is provided with an annular
recess 5 The 435 outer ring which has an inwardly converging 784,740
784, 740 be constructed for coupling to other apparatus in any
suitable way, in the form show N 1-eing provided with a reduced boss
20 whvlich is grooved to receive a ring 21 axially retaining on the
boss a rotatable union nut 22, e g, in the manner described and
claimed in our Patent No 540,490.
The components of the end fitting may be milled or knurled as shown at
23, 24 for facilitating screwing them together.
In the improved form shown in Figure 2 the rings 30 and 31 form the
end attachment of the armouring 1 Prior to applying the clamping screw
the end portion of the armouring is passed through the inside of the
inner ring 30 and folded back on to the outside of the said ring and
the outer ring 31 is forced axially over the folded back material to
grip it on to the inner ring The inner ring has an external flange 32
and the outer sleeve an internal flange 33.
The end attachment of the inner tube 9 (of resilient material) which
may have a fabric reinforcement 10, comprises an insert 34 with a
tapering or conical external periphery and a ferrule 35 which is let
into an external annular recess in the tube, its external diameter
eorresponding to that of the tube The internal cylindrical wall of the
ferrule is provided with annular or helical grooves 36 arranged so as
to surround the tapering portion of the insert when this is forced
into the tube The rear end of the insert has an external collar 37 the
rear face 38 of which is ehamfered to form a sealing edge 39 and the
rear end of the ferrule closely surrounds the externally cylindrical
portion 40 of the insert and its rear end abuts the collar and is
chamfered or bevelled to provide a sealing edge Before assembly of the
tube in the armouring the insert is forced into the tube and presses

the resilient material thereof outwards firmly against the inside of
the ferrule and into the grooves therein A cavity is initially left
between the end of the inner tube and the insert and ferrule By the
action of the insert 34 the outer skin of the tube becomes locked by
the grooves and resilient material is displaced towards the closed end
of the chamber formed by the ferrule and insert and fills the said
cavity The tendency for the tapering insert to displace the resilient
material wholly towards the open end of said chamber is thus countered
The inner tube with its end attachments thus sealed thereto forms a
separate unit The ferrule has an external annular groove 41.
The inner tube and the armouring are C-0 assembled so that the inner
tube is sheathed by the armouring and a split, locking ring 42 is
arranged in the groove 41 of each ferrule.
The armouring is provided at each end with a nut 43 having an inward
flange 44, the nuts being slidden on to the armouring before the end
attachimcents are applied thereto, these nuts being retained on ithe
armouring as part of lhe armouring assembly.
A serew 45 is provided to co-operate with each nut, this screw having
a coulnterlbore 46 t to receive the ring 42 and to provide a radial
face 47 to engage the sealina edge 39 of tihe insert collar.
By screwing together the screw 45 and nut 43 axial pressure may be
applied to 75 press the collar 37 on the insert and the flange 32 on
the inner ring towards one another The sealing edge 39 may thus be
sealed to the radial face 47 of the screw and the bevelled rear edge
of the ferrule 35 sealed so to the front radial wall of the collar The
rings 30 and 31 if not fully home are forced towards one another
between the flange 44 of the nut and the locking ring 42 so as to grip
the folded back end portion of the metal 15 tube more tightly and the
insert, if not fully home, is forced further into the inner tube.
The portion of the screw surrounding the locking ring prevents the
latter from opening out of its groove:o, In the modified and preferred
formn shown in Figure 3, the outer ring 31 a has an inward collar 48
and is forced over the armouring around the inner ring 30 a so that
the armouring is gripped between the collar and the end,5 of the inner
ring where the armouring has been bent outwards to lie between the
rings.
It is also gripped between the inner and outer faces of the outer and
inner rings.
Whilst we in general prefer to employ a 1 I J, flexible metal tube to
sheath the resilient tube, the invention is also applicable to cases
in which a flexible armouring tube of other than metal, e g, textile
material such as a braided cotton tube or two or more such 105 tubes
one within the other replace the metal tube.
In the Specification of our co-pending

Application No 24366/55 (Serial No 784,741) we have claimed a hose
assembly adapted 110 to be coupled to other apparatus and comprising
(a) an inner tube component of resilient material (with or without one
or more tubular layers of reinforcing material) and provided with end
fittings comprising 115 inner and outer members between which the tube
is sealed and (b) a flexible armouring component consisting of or
comprising at least one flexible metallic tube which closely sheaths
the resilient tube and is held against 12 ( removal therefrom by
anchorage to the said end fittings, or such an assembly save that the
armouring is of non-metallic material.
e.g, textile material such as a cotton braided structure 125
* Sitemap
* Accessibility
* Legal notice
* Terms of use
* 5.8.23.4; 93p
* GB784741 (A)
Description: GB784741 (A) ? 1957-10-16
Improvements in and relating to flexible hose assemblies
784,741 ' Date of filing Complete Specification: March 10, 1954.
B, Y Vi Application Date: Dec 11, 1952 No 24366/55.
(Divided out of No 784,740).
Index at Acceptance:-Classes 99 ( 1), G 24 E( 1: 2: 5); and 99 t 2); P
1 (A 8: A 9: A 15 B: B 5 B: B 7).
International Classification:-F 061.
COMPLETE SPECIFICATION.
Improvements in and relating to Flexible Hose Assemblies.
We, WALTER ARTHUR MELSOM, a British Subject, of 112 Vivian Avenue,

Wembley Hill, Wembley, Middlesex, and BOWDEN(ENGINEERS) LIMITED, a
British Company, of Bowden Works, Victoria Road, Willesden Junction,
London, N W 10, 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 flexible hose assemblies
incorporating end fittings by which they are adapted to be coupled to
other apparatus, and especially to such assemblies which are suitable
for pressures of from 500 lb per square inch upwards.
The hoses of these assemblies frequently comprise an inner tube of
resilient material such as rubber (natural or synthetic) or
thermoplastic synthetic material and a surrounding flexible
reinforcing tube of metal, e g, made up of ribbon-like groups of fine
high-tensile steel wires braided to tubular form and with or without
fabric covering The reinforcing material is bonded to the inner tube,
usually being embedded between the inner tube and an outer tube of
resilient material In the manufacture of such hose assemblies as
aforesaid greater facility for testing a sealed inner resilient layer
is wanted in the manufacture of these hose assemblies and we aim at
providing a hose assembly whereof the inner resilient layer and the
reinforcing layer are separate from one another and assembled in
operative relation to one another with the inner layer a separate
component with sealed end fittings, and preferably so that the inner
resilient layer can be replaced and the same reinforcing layer
re-used.
To these ends the present invention consists in a hose assembly
adapted to be coupled to other apparatus and comprising (a) an inner
tube component of resilient material (with or without one or more
tubular layers of reinforcing material) and provided with end fittings
comprising inner and outer members between which the tube is sealed
and (b) a flexible armouring component consisting of or comprising at
least one flexible metallic tube which closely sheaths the resilient
tube and is held against removal therefrom by anchorage to the said
end fittings This construction permits the inner tube after its end
fittings have been sealed to it and tested for faults and sealing
properties to be assembled within the armouring component prior to the
latter being anchored as aforesaid.
The assembly may be so constructed as to allow of the anchorage being
readily released thus freeing the inner tube with its sealed end
fittings for withdrawal from the armouring, e g, the end fittings of
the inner tube and end fittings of the armouring may be anchored
together with the aid of detachable clamping means, e g, screw clamps
The inner tube and its end fittings on the one hand and the armouring

unit on the other may then be subsequently re-assembled and
re-anchored.
The outer member may be a ferrule which is contracted to grip the hose
between it and the insert, the ferrule being made of a metal which is
suitable to contraction, e i, which will be permanently deformed, the
external diameter of the ferrule not exceeding the internal diameter
of the armouring.
The inner tube with or without a fabric, e.g, cotton reinforcing tube
embedded within the resilient material, may be a slidable fit into the
armouring The armouring may consist of a single tube, e g, made of
ribbon-like groups of fine high tensile steel wires braided as
aforesaid, or of two or more such tubes one within the other It 65.
j M 1 P Tmie, M 1 'It 784,741 need not be wholly of metal, e g, there
may be a layer or layers of fabric e g, cotton braid, or of rubber
between the metal layers.
The armouring may be one or more tubes of braided wire surrounded by a
wire coil or a coil as sold under the Registered Trade Mark "
Bowdenex" and constructed according to Patent 412,367, the armouring
closely surrounding the inner tube so that any tendency of the
internal fluid under pressure to distend the inner tube radially
outwards is resisted by the armouring.
The drawings accompanying the Provisional Specification illustrates a
constructional form of hose assembly according to the invention by way
of example.
The armouring comprises two tubes 1, la of braided wire, disposed one
closely within the other, each tube being made of ribbonlike groups of
fine high tensile steel wires braided to tubular form One or each tube
may have a fabric cover if desired The armouring has similar end
attachments at each end Each said attachment consists of inner and
outer rings 2, 3, the inner ring having an integral external collar 4
forming a thickened end which is provided with an annular recess 5 The
outer ring has an inwardly converging inner peripheral portion 6 to
increase the surface area of the end wall 6 a which provides an
abutment as is hereinafter described The outer ring formns with the
inner ring a deep annular recess in which the rough ends of the
braided wire tubes are received The rings are anchored to the tubes
permanently by brazing, swaging or otherwise and/or by forcing the
outer ring axially over the armouring around the innimer ring The
armouring assembly is provided at each end with an internally screwed
nut 7 which is provided with an inward flange 8, the said nut being
slidden on to the armouring before the end attachment is completed.
With the end attachments fixed, the nuts are retained as part of the
armouring assembly, each being prevented by the engagement of the
flange with the aforesaid abutment wall 6 a from displacement off the

armouring.
f The inner tube 9 is of resilient material, e.g, of suitable
thermoplastic synthetic material or a rubber and may be reinforced by
a fabric, e g, cotton, layer 10 The end fittings of this tube each
consist of a ferrule A o and an insert B which may be separate
components as in the example illustrated or may be integral with or
joined to one another.
The internal peripheral wall of the ferrule tapers inwards at 11 to a
central bore 12 bn and the external peripheral surface of the ferrule
is curved at the outer end to form a sealing face 13 An annular groove
14 is formed in the external periphery of the ferrule and one side of
this groove may taper gradually as shown at 15 The ferrule is swaged
or contracted around the end of the inner tube and the insert so that
its finished diameter is substantially the same as the external
diameter of the tube The inner tube with its sealed end fittings pro
70 vides a simple low or medium pressure hose unit This unit is
assembled within the armouring and its end fittings and the end
fittings of the armouring anchored together so that the inner tube is
closely surrounded a 75 by the armouring in the complete assembly.
The end fittings of the inner tube and the end of the armouring are
coupled by a spring ring 16 which is forced over the sealing face 13
into the groove 14 and abuts the 8 u radial wall of the recess 5 The
screw 17 is screwed into the nut 7, and has a radial wall 18 Its inner
periphery tapers at 19 to a bore 19 a, the tapering portion 19
providing an appropriately smooth or machined face 85 to cooperate
with the sealing face 13 of the ferrule A When the screw and nut are
screwed together with the flange 8 abutting the abutment face 6 a, the
co-operating sealing -faces 13 and 19 are brought into 90 sealing
engagement, and the armouring closely sheaths the hose unit and is
held against removal therefrom by anchorage to the end fittings of
such unit The unit is prevented from movement in either direction 95
When the screws 17 are detached the inner unit can be displaced
endwise to a small extent sufficient to enable the locking ring to be
removed and the anchorages released and the armouring and the hose
units are 100 then free for separation.
The clamping component 17 may be constructed for coupling to other
apparatus in any suitable way, in the form shown being provided with a
reduced boss 20 which is 105 grooved to receive a ring 21 axially
retaining on the boss a rotatable union nut 22, e g, in the manner
described and claimed in our Patent No 540,490.
The screw clamping components may be 110 milled or knurled at 23, 24
for facilitating screwing them together.
The end attachments of the inner tube, instead of incorporating an
inwvardly swaged ferrule, may comprise an externally conical 115 or

tapering insert and an outer ferrule, the insert being forced into the
resilient tube so as to press the resilient material thereof outwards
firmly against the inside of the ferrule and if desired into an
annular or 12, helical groove or grooves therein, so that the
attachments are sealed to the resilient tube and the tube can be
inserted as a unit with the attachments without breaking this seal.
The ferrule may be let into an annular 125 recess in the wall of the
resilient tube and held to the insert and its external diameter may
correspond substantially to that of such tube.
The end fittings of the inner tube in the 1:30 in which the end
fittings each comprise an insert and a ferrule between which the end
of the tube is gripped and sealed, the external diameter of the
ferrule not exceeding the internal diameter of the armouring.
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* GB784742 (A)
Description: GB784742 (A) ? 1957-10-16
Improvements in electron tubes
A high quality text as facsimile in your desired language may be available
amongst the following family members:
CH333341 (A) FR1119605 (A) US2867747 (A)
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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.
Inventor: CLAYTON ELLSWORTHMURDOCK 72 i 1742 Date of Application and
filing Complete Specification: Aug 9, 1954.
No 23084/54.
Index at acceptance:-Classes 39 ( 1), D( 9 C: 9 D: 9 F: 9 G: 9 H: IOD:
11: 12 E: 16 A 2: 17 A 3: 46 A); and 83 ( 4), 54.
International Classification:-B 23 k H Olj.
Improvements in Electron Tubes We, EITEL-MCCULLOUGH, INC, a
Corporation organised and existing under the laws of the State of
California, United States of America, and having a place of business
at San Bruno, State of California, United States of America, 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 electron-tubes and more especially (though
not exclusively) to tubes of the velocity modulated type, having
cavity resonators.
The invention provides an electron-tube comprising an evacuated
envelope, an annular metal section and an annular ceramic section
adjacent thereto which sections constitute a part of the envelope,
flexible vacuum-tight sealing means between the adjacent parts of the
sections, and an annular metal element having the form of a short
length of tube which element extends in a generally axial direction
between the adjacent parts of the sections whereby to take axial
thrust between them but does not provide a seal between said sections,
the crosssection of said element being such as to permit deformation
thereof on differential thermal expansion of the sections in a
direction perpendicular to the axis thereof.
The features of the present invention are intended to be particularly
useful in externally tunable klystrons of the type disclosed in U S A
Patent Specification No 2,619,611, issued November 25th, 1952.
This specification shows an electron-tube having cavity resonator
portions, which form part of the evacuated envelope, these resonator
portions comprising metal end walls and a ceramic cylinder extending
between them; these elements are also present in constructions
according to the invention, the present invention providing inter alia
an improved arrangement for sealing the ceramic cthe end walls.

A preferred embodiment of the invention will now be described with
reference to the accompanying drawing in which:Figure 1 is a side
elevational view of part 50 of a three-resonator klystron; Figure 2 is
an axial sectional view of the same, and Figure 3 is an enlarged
fragmentary view showing the construction of a cavity resona 55 tor
portion.
The tube illustrated is particularly designed as an amplifier in the
UHF region having a power rating of several kilowatts CW Figures 1 and
2 show the evacuated 60 tube per se apart from the external structure.
In the final use of such a tube suitable external resonator portions
are applied as described in the above mentioned patent specification,
one of such external resonator por 65 tions being indicated by the
dotted lines 1 in Figure 1.
The tube comprises an elongated generally cylindrical envelope having
an electron gun 2 at one end and a collector electrode 3 at 70 the
other end The electron beam from the gun to the collector passes
through a tube made up of aligned metal sections 4, 6, 7, and 8
extending axially of the envelope and having gaps 9, 11 and 12
therebetween Such 75 gaps are bridged by cavity resonator portions
forming part of the tube envelope and generally designated 13, 14 and
16.
Electron gun 2 includes a disk shaped cathode 17 and a surrounding
focusing elec 80 trode 18, the cathode being heated by a filament 19;
all these elements are supported by a glass stem 21 forming part of an
end of the evacuated envelope Cathode 17 is preferably of a material
such as tantalum 85 heated by electron bombardment from the filament,
all in accordance with conventional practice.
The electron gun is housed in a cupshaped metal section 22 of the
envelope, 90 which section is of iron and functions both as an anode
for the gun and as a pole piece for a suitable external focusing
magnet.
Stem 21 is supported on the pole piece 22.
An aperture 23 in the iron pole piece 22 is aligned with the cathode
and is coaxial with the tube formed by the sections 4, 6, 7, 8.
Collector 3 at the opposite end of the envelope to the electron gun
comprises a hollow metal electrode 24 supported from a disk-shaped
metal section 26 of the envelope.
A glass envelope section 27 sealed between flanges 28 provides a
supporting connection between the collector electrode and the envelope
section 26 An aperture 29 in the metal section 26 is aligned with the
collector electrode and is coaxial with the drift tube The metal
section 26 is a disk of iron and also functions as a pole piece for
the external focusing magnet.
With the above described structure an electron beam from gun 2 is

accelerated by a positive potential on the pole piece 22 acting as
anode and passes through the tubesections 4, 6, 7, 8, past the
interaction spaces provided by gaps 9, 11 and 12, and finally
terminates on the collector electrode 3, the beam being directed down
the tube sections by an external magnet associated with iron pole
pieces 22 and 26 The three cavity resonators comprising portions 13,
14 and 16, coacting with the interaction spaces at gaps 9, 11 and 12,
serve as the frequency determining elements of the device In the tube
illustrated, which functions as an amplifier, the input signal for
modulating the electron stream is fed into the first resonator
comprising the portion 13, and the radio frequency output is taken
from the third resonator comprising the portion 16, as is usual for
three-cavity type klystrons.
As previously mentioned herein, the particular kind of tube shown is
adapted for external tuning by the use of suitable external resonator
portions, one of which is indicated by the dotted lines 1 in Figure 1:
each complete resonator comprises a portion forming part of the
envelope, such as 16, and a cooperating external portion, such as 1
The use of such external resonator portions for tuning over a wide
band of frequencies is possible, of course, because of the sealed-off
nature of the resonator portions 13, 14 and 16 which comprise part of
the evacuated envelope.
Continuing with the description of Figures
1 and 2, the end tube section 4 is brazed to the pole piece 22, and
the other end section 8 is brazed to the section 26 The intermediate
tube sections 6 and 7, as has been said, are axially aligned with the
end sections 4 and 8, and these several sections form parts of the
side walls of the evacuated envelope.
The resonator portions 13, 14 and 16, which are disposed transversely
of the envelope axis, are mounted on the tube sections and form
additional side wall portions of the evacuated envelope In other
words, the resonator portions provide vacuum-tight walls bridging the
gaps between the tube sections.
Input resonator portion 13 comprises 70 parallel disk-shaped metal end
walls 31 and 32 brazed to the tube sections 4 and 6, these end walls
also being preferably of copper.
A cylinder 33 of insulating mateijal is sealed between such end walls
In the interest of 75 mechanical strength and electrical properties
the cylinder 33 is of a ceramic material, such as the alumina or
zircon type ceramic bodies.
Cylinder 33 is supported by axially extending flanges 34, preferably
of copper, brazed 80 to the opposing surfaces of side walls 31 and 32
The ceramic is metallically bonded to the copper flanges by known
ceramic-tometal bonding techniques, such as by first metalising the

ends of the ceramic by the 85 molybdenum powder sintering process and
then brazing the metalised ends to the metal flanges with silver
solder or the like.
Since the ceramic materials have a lower coefficient of thermal
expansion than metals 90 of good electrical conductivity, such as
copper, the flanges 34 are given a U-shape to provide folded back
inner lips 36 connected to the ceramic This provides a good mechanical
arrangement and also sufficient flex 95 ibility in the structure to
accommodate differences in expansion Another advantage of this
construction is that the rounded faces of the flanges, i e the bights
of the U's, face each other, and thereby provide desir 100 able corona
rings to reduce sparking between the resonator walls In combination
with the U-shaped flanges, metal spacing rings 38 are provided to
project from the end walls to abut the ends of the ceramic These rings
105 take axial thrust between the end walls and the ceramic and
prevent the flexible flanges from collapsing when the tube is
evacuated.
When differential thermal expansion occurs perpendicular to the axis
of the tube the 110 spacing rings deform slightly to accommodate this
expansion Thermal expansion and contraction axially of the tube
presents no problem since in normal use of the tube it is always held
so as to allow the slight move 115 ments involved.
The intermediate resonator portion 14 is of similar construction,
having end walls 39 and 41 with a ceramic cylinder 42; output
resonator portion 16 is of like construction, hav 120 ing end walls 43
and 44 with a ceramic cylinder 46 In each of the three resonators the
disc-like end walls have outer edges providing terminals with which
suitable contact fingers on the cooperating external resonator 125
portions may be engaged.
Provision is made in the tube illustrated for cooling the tube
comprising sections 4, 6, 7, 8, and associated parts, such cooling
being of special importance in a power tube of this 130 784,742 24
After evacuation of the envelope this tube is pinched off at tip 65.
In the specification of my copending Application for Letters Patent No
27,053/56 (Serial No 784,743) there is described and 70 claimed a
velocity modulated type electrontube, comprising an elongated
evacuated envelope, an electron gun at one end of the envelope and a
collector electrode at the other end, a straight tube extending
axially 75 of the envelope and forming side walls of the evacuated
envelope, said tube comprising spaced sections with gaps therebetween,
a plurality of cavity resonator portions disposed transversely of the
envelope axis at 80 the gaps, said resonator portions comprising metal
end walls mounted on adjacent tube sections and extending outwardly
from said sections, means providing vacuum tight walls across the

gaps, and a water jacket 85 surrounding the tube section between a
pair of adjacent resonator portions, and comprising a sleeve connected
between the adjacent end walls of the latter resonator portions.
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