Automatic Transfer Applicator Increases Clothing Marking Efficiency

* GB785769 (A)
Description: GB785769 (A) ? 1957-11-06
Transfer applicator
Description of GB785769 (A)
,Z _ lc, s,
PATENT -SPECIFICATION
785,769 Date of Application and filing Complete Specification: Aug 2,
1955.
C.
No 22132155.
1 AV 1 Complete Specification Published: Nov 6, 1957.
Index at acceptance:-Class 100 ( 2)3, Ul.
international Classification:-Bln.
COMPLETE SPECIFICATION
Transfer Applicator T i" ws'rr Trt RT Kr It L-v L, a Citizen of
nlumijer of transfers accomplished by one i' t in ^ -en time; however,
the PATENTS ACT, 194 g 2 Pi C Ip Ic J'AT Io I, NO 78 R 769 a N sd in
the of in of the Patents Act, 1049, the Specification has been amended
In the Olw Ing manner: Page 3, line im, after iicomprisingi# insert
"w" Page 3, line 121, after "elements, insert "onefor i i Other during
pressing action, it ing (leme or i Page 3, line 127, for "the pressing
action Of Said elemen Itsft read "thke novemet Of said One element
towards the Other elemjent" eit Page 4, lines 8 9, delete Psald
Dressing elements Comprise a pair or elements, I Rl E PATERT O'RI Wt-n
12th Atay, 2958 DB 04625/1 ( 4)/3612 150 5/58 R Trall e al or a
combination of these from a strip of paper to the article by applying
heat and pressure against the paper while it is in contact with the
article to be marked This transfer may be accomplished by lusing a
domestic iron or by using other types of equipment.
Generally, the transfer or label to be applied to an article of
clothing is first printed inversely at spaced intervals along a strip
of paper or tape When used, a printed section of the tape is held on
top of the article and the heating element is applied to the back of
the tape; then, the next printed section is used to markl the next

article in a similar manner and so on.
Recent Iv, a device has been used which consists of a heating element
supported by a reciprocating arm so that, in order to mark an article
the operator need only position the article and the tape appropriately
beneath the heating element This process has materially increased the
lPrice 3/6 l ciotning, e _ easily operated by an inexperienced
operator with less fatigue than has here-70 tofore been occasioned.
Another object of my invention is to provide an automatic machine for
marking articles of clothing which will be actuated only when the
article of clothing is in its 75 proper position under the heating
element section of the machine.
Another object of my invention is to provide a machine for
transferring markings to an article of clothing, which 80 machine is
inexpensive to manufacture, durable in construction, efficient and
inexpensive in operation.
My invention will become apparent from the following disclosure when
taken in con 85 junction with the accompanying drawings in which like
figures of reference designate corresponding parts throughout the
several views, and wherein:
Fig 1 is a perspective view of a machine 90 PATENT SPECIFICATION
785576 s d 1 B y Date of Application and filing Complete y
Specification: Aug 2, 1955.
Complete Specification Published: Nov 6, 1957.
Index at acceptance:-Class 100 ( 2), U 1 O International
Classification:-Bln.
Transfer Applicator I, J Os P 11 EDWARD Ki Ei,P, a Citizen of the
United States of America, whose address is P O Box 235, Acworth,
Georgia, United States of America, 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 he particularly described in and by
the following statement:-
This invention relates to a transfer applicator and more particularly
to an automatic machine for applying transfers to selected articles
and in particular to articles of -earing apparel.
It has been found desirable in the manufacture of articles of wearing
apparel such as socks, stockings, hose and other like articles to mark
the size and the manufacturer 's name oi' trade-mark on each artiele
produced In order to accomplish this, it has been standard practice in
the trade to transfer letters, designs, colours or a combination of
these from a strip of paper to the article by applying heat and
pressure against the paper while it is in contact with the article to
be marked This transfer may be accomplished by using a domestic iron
or by using other tvpes of equipment.

( 4 enerally, the transfer or label to be applied to an article of
clothing is first printed inversely at spaced intervals along a strip
of paper or tape When used a printed section of the tape is held on
top of the article and the heating element is applied to the back of
the tape; then, the next printed section is used to mark the next
article in a similar manner and so on.
Recently, a device has been used which consists of a heating element
supported by a reciprocating arm so that, in order to mark an article
the operator need only position the article and the tape appropriately
beneath the heating element This process has materially increased the
lPrice 3/6 l No 22132155.
number of transfers accomplished by one operator in a given time;
however, the continual handling and adjusting of the article and the
tape to the proper position is very tiring to an operator 50
Accordingly, it is an object of my invention to provide a device which
will alleviate the difficulties described above and facilitate the
handling and marking of articles of clothing 55 Another object of my
invention is to provide a machine which will increase the number of
articles which may be marked by a single operator in a given time.
Another object of my invention is to 60 provide a machine for applying
transfers to articles which when the articles are successively placed
on the machine will auttomatically mark and stack these articles 65
Another object of my invention is to provide a machine for marking
articles of clothing, as described above, which is easily operated by
an inexperienced operator with less fatigue than has here-770 tofore
been occasioned.
Another object of my invention is to provide an automatic machine for
marking articles of clothing which will be actuated only when the
article of clothing is in its 75 proper position under the heating
element section of the machine.
Another object of my invention is to provide a machine for
transferring markings to an article of clothing, which 80 machine is
inexpensive to manufacture, durable in construction, efficient and
inexpensive in operation.
Mv invention will become apparent from the following disclosure when
taken in con 85 junction with the accompanying drawings in which like
figures of reference designate corresponding parts throughout the
several views, and wherein:
Fig 1 is a perspective view of a machine 90 4 S ' 785,769 constructed
in accordance with my invention.
Fig 2 is a cross-sectional view taken along line 2-2 of Fig 1.
Fig 3 is a side vliew of the machine shown in Fig 1.
Fig 4 is a view of a detail showing the pulley and ratchet driving
mechanism of the machine illustrated in Fig 1.

Fig 5 is a view of a detail showing the operation of the interlock
system.
Referring now in detail to the embodiment chosen for purpose of
illustration, and to Figs 1 and 2 in particular, numeral 10 denotes
generally a rectangular box-like easing which is open, as shown in Fig
1, at its top Adjacent this open top are positioned spaced roller
shafts 11, 11 ' retained by journals 12 mounted on brackets 13 in Fig
1 Fixed concentrically and centrally of shafts 11, 11 ', respectively,
are solid cylindrical feed rollers 14, 14 ', which are provided with
peripheral grooves adjacent their ends to receive spaced continuous
belts 15, 15 ' which extend parallel to each other betwveen the two
rollers to convey articles to be markied across the top of casing 10.
As shown in Fig 2, a reel supporting pan 16 is mounted within casing
10 along an end thereof adjacent roller 14 ' Rollers 17 are mounted
transversely between the sides of pan 16 and are spaced on an are to
support reel 1 S thereon Arm 19 extends up from one edge of pan 16 and
is provided with a pivot pin on -which is mounted for rotation a
roller 20 which acts as a guide for the paper markiing tape 21
unreeled from reel 18 As seen in Figs.
401 and 2, a window 22 is provided within the end of easing 10
adjacent pan 16, through which reel 18 may be inserted and then
mounted to rest freely on rollers 17 within pan 16 When reel 18 is
mounted properly on rollers 17 within pan 16, tape 21 leading from
reel 18 is passed over roller 20 and then over rollers 14 ' and 14 so
that tape 21 is spaced between parallel belts 15, 15 ' and in the same
plane therewith Tape 21 is provided with certain desired markings or
labels 23 at spaced intervals along the top surface of the tape 21 so
that when heat is applied to the back of the paper tape, the printed
material or label thereon may be transferred as desired.
As illustrated in Fig 2, an arma 24 is pivotally mounted on the end
wvall of easing 10 adjacent roller 14 Arm 24 supports pressure roller
2 a which rides against the lower portion of roller 14, and a spring
26 is connected to arin 24 and to he easing 10 to urae roller 25
against roller 14 Afiter passing over roller 14, tape 21 is fed
between roller 14 and roller 235 and dow 7-n into the void lower
section of easing 10: therefore, when roller 14 is rotated, tape 21
will be unireeled from reel 18 and pulled along in the same plane with
helts 13, 15 ' 70 Positioned somewhat centrally tranlsversely -within
casing 10 is heating, element, supporting b)vracket 27 which is fixed
to the sides of casing 10 in a horizontal position Bracket 27 is
provided 75 with an aperture in its central por tion, through wvhiclh
is passed an uprighlt rod 28 which is journaled for vertical motion
within sleeve 29 w-hieh is fixed to the lower side of bracket 27 80
Mounted on the upper end of rod 28 so as to be positioned between

helts 15 15 ' is a conventional rectangular-shaped electric heating
element 30 which is activated through electrical cables (not shown, At
85 the lower end of rod 2 S is a transverse pivot piii 31 which is
fixed to rod 29 and rides wvithin a slot within one end or lever arm
32 The other end of lever arm 32 is fixed to shaft " 3, which shaft
passes 90 through easin 10 anid is engaged by lever.
34 on the otutside of casinag 10 It will b-e apparent therefore that
when lever 34 is moved up and down, heatilng element:30 will be moved
away from or toward tapeg 95 21 Latches 35 and 36 are provided on
casino'10 adjacent lever '34 to act as a catch for the lever 34 and
therefore allow proper positioning of heating element 30, either
adjacent tape 21 as shown by solid 100 lines in Fig 2 or away from
tape 21 as shown b)y the broken lines in Fig 2.
As illustrated in Fig 2 a brace '37 is mounted uprightl within easing
10 and supports transverse axle 38 Axle 38 is 105 journaled for
rotation within hrace 37 and extends through an appropriate aperture
in a side wall of casing 10 Pulley 39 is concentrically fixed to axle
38 between brace 37 and the wall of easing 10 and isllo driven by a
continuous belt 40 which is driven from a -earhead rmotor 41 mounted
on bracket 42 transversely within casing Also fixed concenitrieally to
the axle 3 S is rocker disc 403 which acltates conlee 115 ting rod 44
and tilts platform 45 which 1 is hinged to easing 10 by piano hinge
46.
Fixed concentrically to axle 3 S outside of easing 10 is a circular
disc 47 having a cam 4 S fixed to its inside face as illustrated 120
by) broken lines in Fi 3.
Referring now l in particular to Fis 3, 4 and a piv ot pin 49 is fixed
to the outer face of dise 47 'id "eent the pei iplheryl thereof and
rtt'mchcd tn pivot pin 49,s a 125 flexii)le calle Q hich looi 7 is
around a solid cylinder 1 ro Mt'itob pos'tbmed Mn shaft 11 Calle ' O
rides -ii 17 in heliefical 'eoes on cyliadea S l f '_l Fio 4, and its
end is fixed to e linder 1 by screw 5 a 2 130 785,769 A second cable
53 is fixed to cylinder 51; the outer end of cable 53 extends down and
is fixed to spring 53 which in turn is fixed to easing 10, as
illustrated in Fig 3 A cylindrical flange 56 made integrally with
cylinder 51, as shown in Fig 4, retains pawl 57 pivotally mounted on
its face adjacent the periphery thereof Pawl 57 drives ratchet 58
which is fixed concentrically to shaft 11 Therefore, as disc 47
rotates to pull cable 50, pawl 57 acts against ratchet 58 to rotate
shaft 11 As disc 47 continues its evele of rotation, spring 55 acts
through cable 53 to rewind cable 50 on cylinder 51, thus allowing pawl
57 to pass over ratchet 58 and therefore not rotate shaft 11.
Mounted for vertical motion within aligned journals 59, 59 ' on easing
10, is standard 60 which is positioned above cam 48 so that the lower

end of the standard will ride against the cam Fixed to the upper end
of standard 60 is a presser plate supporting arm 61 which is retained
in place by a set screw (not shown) Arm 61 extends at right angles
from standard 60 and supports presser plate 62 in a position over
heating element 30 Presser plate 62 is faced with a resilient material
63 on its bottom surface; this resilient material may be rubber,
neoprene or a sponge material.
Guide staff 64 extends from the top edge of easing 10 and through an
aperture in arm 61 so that as arm 61 is moved up and down by _ the
reciprocating action of standard 60, presser plate 62 will remain in
the same vertical plane A coil spring has one end fixed to arm 61 and
the other end of the spring is fixed to casing 10 so that standard 60
at all times is urged against cam 48 An interlock pin 66 depends from
arm 61 and is so positioned that it is above the edge of casing 10 and
as standard 60 moves down, the pin will normally pass through a
drilled recess 67 passing partially dowsn through the wall of easing
10.
As illustrated in Fig 5, the interlock system, which is a means by
which interlock pin 66 is blocked from entering recess 67, consists
generally of an upstanding brace fixed to the upper edge, of casing 10
which pivotally retains an interlock arm that extends outwardly and
downwardly over tape 21 A lever arm 70 is fixed to interlock arm 69 at
a position adjacent brace 68 and is pivotally fixed at its end to
shutter bar 71 which extends as illustrated in Fig 5 to a position
where shutter 6072 on shutter bar 71 can selectively block the
entrance of interlock pin 66 into recess 67.
From the foregoing description, it will be obvious that when a reel of
marking tape is positioned in pan 16 and the tape extends over rollers
14, 14 ' and motor 41 started, an operator may place articles to be
marked over each of the transfers 23 as they first pass over roller 14
' and these articles will rest on and be carried along 70 by belts
1,5, 15 ' under interlock arm 69 to a position beneath presser plate
62 It will be apparent from Figs 2, 3 and 5 that an article positioned
beneath presser plate 62 will lift this interlock arm 69 so that 75
shutter 72 will uncover recess 67 and therefore not interfere with the
passage of interlock pin 66 or the operation of presser plate 62 When
an article is positioned beneath presser plate 62, disc 47 is at such
80 a position of its cycle that shaft 11 will not be rotated and
therefore tape 21 and belts 15, 15 ' will be stopped With continued
rotation of disc 47, the recess portion of cam 48 will position itself
so 8 s that standard 60 drops into this recess and therefore causes
presser plate 62 to press against the article positioned thereunder
causing the article and the transfer tape to be pressed against
heating element 90 With continued rotation of disc 47, presser plate

62 is lifted and the article will be carried by belts 15, 15 ' and
deposited on platform 45 My invention is so arranged that as each
article is 95 deposited on platform 45, the platform will tilt up as
illustrated in Fig 2 and thus stack the articles in any suitable
container (not shown) placed adjacent easing 10 below platform 45 100
It will be apparent that if no article is placed over a certain
transfer 2, as this transfer passes over the heating element the
interlock arm 69 will not be lifted, because the necessary thickness
of an 105 article to be marked is missing, and the downward movement
of presser plate 62 will be interrupted by shutter 72 blocking recess
67 and therefore blocking the downward movement of interlock pin 66
110 It will be obvious to those skilled in the art that many
variations may be made in the single embodiment disclosed for purpose
of illustration without departing from the scope of my invention as
defined 115 by the appended claims.
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* 5.8.23.4; 93p
* GB785770 (A)
Description: GB785770 (A) ? 1957-11-06
Improvements relating to thread twisting spindles having thread-tensioning
devices
A high quality text as facsimile in your desired language may be available
amongst the following family members:
CH331804 (A) DE1010879 (B) FR1125843 (A) NL89764 (C)
US2836377 (A)
CH331804 (A) DE1010879 (B) FR1125843 (A) NL89764 (C)
US2836377 (A) less

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The EPO does not accept any responsibility for the accuracy of data
and information originating from other authorities than the EPO; in
particular, the EPO does not guarantee that they are complete,
up-to-date or fit for specific purposes.
PATENT SPECIFICATION
785,770 Date of Application and filing Complete Specification: Aug 26,
1955.
Application made in Germany on Oct 9, 1954.
Index at acceptance:-Class 120 ( 2), D 2 C 5 (D:0:X).
International Classification:-DO 2 d.
Improvements relating to Thread Twisting Spindles having
Thread-tensioning Devices We, BARMER MASCHINENFABRIK
AKTIENGESELLSCHAFT, a Body Corporate organised under the Laws of
Germany, of WuppertalOberbarmen, Germany, 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 invention relates to thread twisting spindles having
thread-tensioning devices and especially to multi-twist twisting
spindles in which the thread travels through a tensioning device of
the opposed disc type in passing through the middle of the spindle.
It is known to provide the thread run-in sections of twisting spindles
with thread tensioning devices having disc surfaces arranged in the
direction of the holes through which the thread passes, the discs
usually being urged together by spring pressure.
Such devices have the disadvantage that the thread will after a short
time produce grooves in the discs, even when the discs are made of
extremely hard material, and these grooves tend to damage the threads
subsequently passing through Furthermore, the springs do not always
ensure constant bearing pressures, since they are subject to fatigue
phenomena.
Magnetically operated discs have already been constructed Where the
inexpensive and reliable permanent magnets have been used for this
purpose, it has previously been necessary to arrange the discs in a
horizontal position It has not, in fact, always been possible for the
magnetic discs to be reliably supported and guided in a vertical

plane, solely by the relatively weak forces of the permanent magnet
Strong electromagnets can be used for this purpose, but they cannot be
fitted in the limited space of the thread runin sections of
multi-twist twisting spindles.
Horizontally mounted discs in which thread coming from above passes
around the rim of an upper disc and is thereafter guided through
lPrice 3/6 l a central hole in a lower disc, have the disadvantage
that the thread is subjected to too high a degree of abrasion owing to
the strongly arcuate deviation.
Furthermore, tensioning devices are known 50 which have discs and are
rotatably mounted on journals, the thread being guided eccentrically
between the discs and imparting movement to the device as a whole The
rotation of the discs prevents grooves being formed in 55 them by the
threads so that the damage to the threads consequent on the formation
of grooves and a relaxing ofthe tensioning action are also prevented
and the wear of the discs increased Such a tensioning device re 60
quires a guideway arranged close in front of and following the discs
and a considerable initial tension in the entering thread, so that the
rotating discs do not cause the thread to be guided out of the
tensioning range as the 65 device would then become quite ineffective.
However, it is not always possible for the entering thread to be given
a relatively high initial tension, especially when unwinding
vertically with multi-twist twisting spindles 70 An object of the
present invention is to provide a reliable tensioning device of the
opposed disc type in which thread can be guided without great abrasion
between vertically disposed discs which, for reasons of 75 space and
symmetry, are subject to the bearing pressure of permanent magnets and
which are rotatably mounted in order to avoid premature wear on the
tensioning surfaces of the discs and damage to the thread by 80
abrasion, and which, moreover, do not, although they are rotatable,
guide the thread out of the tensioning range even with extremely weak
or greatly fluctuating initial tensions 85 The invention provides a
thread twisting spindle having a thread run-in section with a thread
inlet hole, and a thread-tensioning device which is mounted in the
section eccentrically of the hole and includes a disc 90 c SC 1, Jc
Jos Up No 24600155.
785,770 which is caused by the travel of thread through the device to
rotate with respect to another disc and a permanent magnet acting on
the device to urge the discs together and spaced from it by removable
spacers Regulation of the thread tension is made possible by the
spacers which are removable so that they can be changed at will These
spacers can be assembled, jointly with the permanent magnet, in a
pot-shaped part which is in turn mounted in a blind hole extending
transversely of the direction of travel of the thread and formed in

the thread run-in section, the part being held by means of a closure
plug.
The pot-shaped part is made of a material.
for example polystyrene, which is nonmagnetic in order not to
interfere with the operation of the permanent magnet and is also
preferably transparent so that the spacers are visible A compression
spring acting against the permanent magnet or against the spacers
ensures that the pot-shaped part is always brought into the same
position in relation to the thread passage, that is to say, the
pot-shaped part is always forced against a step in the blind hole The
spacers and the permanent magnet in the pot-shaped part can be changed
according to the required thread tension The -compression spring can
however be dispensed with if the overall length of the permanent
magnet with the spacers is such that either the permanent magnet or
the spacers bear on the closure plug.
A bushing is provided centrally in the base of the pot-shaped part to
receive a journal of the non-magnetic rotatable disc in such manner
that the disc bears against the small bushing with the smallest
possible degree of surface friction The second magnetic disc, which is
urged against the non-magnetic disc under the action of the permanent
magnet, is rotatable, but cannot tilt at its periphery in the blind
hole The two discs are set in rotation by the eccentrically travelling
thread.
However, since they are subject to very different bearing frictions
owing to the different types of mounting, the non-magnetic disc
mounted in the journal will rotate at a substantially higher speed
than the magnetic disc with its greater peripheral friction.
Owing to the different speeds of rotation of the two discs which are
caused by the travelling thread, it is possible for the thread to be
held constantly between the two discs If the discs were to rotate at
the same speed, the thread travelling through with the low initial
tension which is usually provided with vertical withdrawal, especially
with fine threads, would be forced by the rotating discs out of the
tensioning zone owing to the adhesive effect of the dressing on the
thread so that it would no longer be possible to produce a uniform and
controllable tensioning action.
The retaining effect of the uniformly rotating discs on the travelling
thread therefore occurs as soon as the two discs move in relation to
one another Thus it is provided when one of the discs is stationary
and only the other is rotating so that, as a special case.
it is also possible to dispense with the non 70 magnetic disc and to
guide and tension the thread between the magnetic disc and the base of
the pot-like part.
Openings are provided in the thread run-in section at the level of the

discs and extend 75 in depth to the position of the discs so as to
form windows which make it possible easily to supervise and clean the
tensioning system.
Two embodiments of the invention are shown by way of example in the
accompany 80 ing drawings in which:Fig 1 is a vertical section on the
line C-D of Fig 2 through a thread run-in section of a multi-twist
twisting spindle with a tensioning device; 85 Fig 2 is a vertical
section through the same thread run-in section, but turned through 99,
in the direction of travel of the thread, Fig 3 is a cross-section, on
the line A-B of Fig 1, through the thread runi-iin section 90 with the
tensioning device exposed: and Fig 4 shows a modified thread run-in
section.
As shown in the drawings, a thread 1 is introduced into a thread inlet
hole 3 of a 95 thread run-in section 2 and passes without change of
direction between the tensioning surfaces of a magnetic tensioning
disc 8 and a non-magnetic tensioning disc 9 The discs 8, 9 are
arranged in a blind hole 4 in the thread loo run-in section 2
transversely and somewhat eccentrically of the thread passage hole 3
in such manner that the thread 1 constantly imparts a rotational
movement to the discs 8 9 as it travels along so that grooves or the
like 10 a will not be formed in the surfaces of the discs.
A permanent magnet 11, of a kind known per se, places both discs 8 and
9 under pressure due to the attraction of the magnetic disc 8, it
being possible to regulate this pressure by 110 the selective fitting
of removable non-magnetic spacers 12 which can be interchanged with
others The magnetic disc 8 is rotatably mounted in the blind hole 4
which guides the periphery of the disc and is of such depth that 11,5
the disc is secured against tilting A potshaped part 13 has in its
base 14 a central bushing 15 which receives a journal 10 on the
non-magnetic disc 9 In order to assist the rotation of the device when
the thread 12 X) travelling through it is ultra-fine, the nonmagnetic
disc 9 is made of a light-weight material, being preferably
manufactured by the injection method from synthetic linear
superpolyamides Such material also pre 125 vents too high a degree of
abrasion of the thread Owing to the different friction of the two
discs 8 and 9, they rotate at different speeds of rotation when the
thread passes through; the magnetic disc 8 revolves sub 130 785,770
stantially more slowly than the journalmounted non-magnetic disc 9
owing to its greater peripheral friction.
The permanent magnet 11 and the nonmagnetic spacers or washers 12 are
disposed in the transparent non-magnetic pot-shaped part 13, which is
in turn arranged in the blind hole 4 in such manner that it bears
against a step 5 of the blind hole 4 and is held by a closure plug 16
adapted to be screwed into a screw-thread 6 of the thread run-in

section 2.
The head of the plug 16 is received in a recess 7 The closure plug 16
has a blind hole 17 into which the pot-shaped part 13 and the
permanent magnet 11 or its spacers 12 are adapted to project, and a
compression spring 18 urges the pot-shaped part 13 against the step or
shoulder 5 of the blind hole 4 so as to ensure that the part 13 always
has the same position in the thread run-in section.
Openings 19 are provided in the thread run-in section 2 at the level
of the discs 8 and 9 and form observation windows in the blind hole 4,
which are also useful for the cleaning of the device.
Instead of fitting the disc 9, it is also possible for the base 14 of
the pot-shaped part 13 to serve as a tensioning disc as shown in Fig 4
The pot-shaped part 13 rests in the blind hole 4 so that the magnetic
disc 8 is the only rotatable disc.
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* GB785771 (A)
Description: GB785771 (A) ? 1957-11-06
Improved device for hydraulic governing of engines
Inventors: JAN RYDH SCHNITTGER and ERNST BERTIL ANDERSSON Date of
Application and filing Complete Specification Oct 3, 19555.
No 28129155.
Complete Specification Published Nov 6, 1957.
785771 Index at Acceptance:-Class 135, P( 1 F: 9 A 4: 9 A 6: 16 E 5:
24 KX).
International Classification: -GO 5 c.

Improved Device for Hydraulic Governing of Engines, We, SVENSKA
TURBINFAB Rix S AKTIEBOLAGBT Lj UNGSTR 6 M, of Finspong, Sweden, a
Swedish 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:-
The present invention has reference to the governing of various kinds
of engines, such as steam, gas and water turbines Hereinafter, for the
sake of simplicity, the invention will be described as applied to a
steam turbine.
Modern steam turbines are characterized by more and more reduced
acceleration times (due to reduced moments of inertia) and increased
difficulties in maintaining the clearances at low values (especially
in respect of the admission of steam at high temperatures and the
provision of reheating conduits) Still there remains as a primary
working condition that the ordinary governing equipment of the steam
turbine should be able to control the speed of the turbine upon a
momentary disconnection of the total maximum electrical load (that is
the electromechanical moment) Usually, the emergency stop valve of a
turbine effects a total stopping of the turbine when the increasing
turbine speed resulting from the load being suddenly cut off, attains
a value amounting to 10 % above the normal speed The rapid closure
action of the governing device according to the invention prevents the
turbine from attaining such a 10 % speed increase, and, consequently,
the emergency stop valve will not be thrown into gear.
For the above said reasons it is of great importance to effect rapid
closing operations of the throttle at an increased speed The reverse
case, that is to say, rapid opening operations, is only a problem of
stability.
The invention relates to a device for hydraulic governing of engines
such as steam, gas or water turbines, which by means of a servo motor
for operating the inlet valve of the engine includes an inner slide
controlled by a centrifugal governor driven by the engine and lPrice 3
s 6 d l a surrounding outer slide controlled by a resetting mechanism
operated by the servo motor and in which said slides constitute a
valve mechanism for controlling the flow of 50 fluid to and from the
servomotor for operating the inlet valve of the engine.
The invention is characterised by the fact that said inner slide is
formed with at least three axially spaced valve closure surfaces 55
each adapted to cooperate with an individual one of three seating
surfaces on the outer slide, one of said valve closure surfaces
exposing its seating surface upon a reduction of the speed of the
engine as and for admitting fluid to the 60 servomotor, and the

remaining valve closure surfaces exposing their seating surfaces upon
an increase of the speed of the engine for discharging fluid from the
servomotor in order to effect a more rapid adjustment of the speed 65
downwardly than upwardly.
In the accompanying drawing a portion of a regulating device according
to the invention is shown by way of example.
The device shown comprises an inner slide 70 1 and an outer slide 2
Both of said slides are movable axially with relation to each other.
The displacement of the inner slide is effected by means of a
centrifugal governor (not shown) which is connected to the rod 3 When
the 75 speed decreases the inner slide 1 is moved upwardly and when
the speed increases it is moved downwardly The outer slide 2 is
connected by means of an arm 4 to a resetting mechanism (not shown) by
means of which the 80 slide 2 may be displaced axially The slides are
surrounded along a portion of their length by a stationary housing 5
Said housing is provided with two connecting branches 51 and 52.
Through the connecting branch 51 oil under 85 pressure is admitted in
the direction of the arrow 6 from a high pressure pump (not shown),
and through the connecting branch 51 oil may be passed in the
direction of the arrow 7 to a servomotor (not shown) in order 90 to
increase the speed of the engine, or discharged from said servomotor
in the direction 785,771 of the arrow 8 for reducing the speed of the
engine The oil thus discharged from the servomotor in the direction of
the arrow 8 further passes via openings 9 and 10 in the outer slide 2
back to an oil tank (not shown).
If the speed of the turbine sinks owing to increase of load, the inner
slide 1 will be raised by the centrifugal governor connected to the
rod 3 As a result, a gap will momentarily appear between the two
slides at 11, thereby allowing oil under pressure to pass from the
high pressure pump through Said gap to the servomotor, causing it to
positively operate the steam regulating valve to admit more steam to
the turbine The governing action being completed, the outer slide 2
will be restored to normal i e relative to the slide 1 by the action
of the resetting mechanism so as to again close the momentarily
exposed gap at 11.
Upon an increase of the speed the inner slide 1 will be displaced
downwardly, thereby momentarily exposing gaps between the two slides
at 12 and 13 Because of the tight fitting between the guide flange 14
of the outer slide and the piston-like middle portion 15 of the inner
slide the oil entering through the connecting branch 51 is prevented
from reaching the connecting branch 52, whereas oil is allowed to pass
from the servo motor via the connecting branch 52 into the housing 5
and thence through the gaps 12 and 13 and the openings 9 and 10 of the
outer slide back to the oil tank This causes the steam regulating

valve to close, and this closing operation takes place twice as rapid
as the opening operation due to a reduced speed This is due to the
fact that the gap area exposed due to an increased speed is twice as
large as the gap area exposed as result of a decreasing speed.
While the piston-like portions of the inner slide acting as valve
bodies are shown equally wide, it is to be noted that they may be
different diameters, thereby allowing a dimensioning of the gaps to
suit any desired condi 45 tions.
As already stated in the preamble of this specification, the invention
secures a governing operation twice as rapid in reducing the speed as
it does in increasing it This effect 50 permits a better control of
the overspeed of the turbine resulting from a momentary disconnection
of the electrical load of the turbine, without requiring any essential
complication of the structure of the governing device 55
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* GB785772 (A)
Description: GB785772 (A) ? 1957-11-06
Aircraft control surface operating mechanism
P 2 ATENT SPECIFICATION
Inventor: RIICHARD HERIS'Cf EL WEILAND 785772 Date of Application and
filing Complete Specification: Oct 21, 1955.
No 30184/55.
Index at acceptance:-Classes 4, C( 7 A 1: 7 83: 8 G 1 B); and 135, P(
5: 9 A 4: 16 E 2: 24 H: 26).
International Classification:-B 64 d G 05 d.

ICOMPLETE SP El CIFJIC Af I'ON Aircraft Control Surface Operating
Mechanism We, BOEING AIRPLANE 'COMPANY, 'a corporation duly organized
under the laws of the State of Delaware, United States of America, of
3805, South 'Oliver, Wichita, State of Kansas, United 'States of
America, do hereby declare the invention, for which we pray that n
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 generally to aircraft and more particularly to
improvements in mounting control airfoils on fixed airfoils and in
operating means for control airfoils.
In aircraft designed to fly at supersonic speeds extremely thin
section supporting land controlling airfoils are considered a
necessity.
Deflection of the control airfoils of an airplane flying at supersonic
speeds requires the application of a relatively large force due to the
extreme speed of the airstream into which the airfoil must be
deflected, and the consequent resistance of the airfoil to such
deflection The extreme thinness of the wing at the hinge axis of the
control airfoil which is of the order of 1 % of the maximum chord
length of the comhined airfoils dictates that the airfoil deflecting
force be applied through a relatively short moment arm, else there
would be 'a considerable aerodynamic drag penalty due to the
projection of parts of the deflecting mechanism into the airstream
Furthermore, when the design is such that the deflecting force is
applied at only one end, or even at both ends, of the hinge axis of
the control airfoil, its internal structure must be of great strength
to withstand the bending loads created by deflection of the airfoil
into' the airstream.
The primary object of this invenfion is to provide a control airfoil
deflecting or operating mechanism which is capable of being wholly
contained within the contours of an extremely thin airfoil section,
and which evenly distributes the deflecting moment along the entire
length of the control airfoil hinge axis lPrice 3 s 6 d l thereby
practically eliminating any tendency for the deflected airfoil to be
distorted by applied airstream loads, and thus permitting the use of a
minimum of internal airfold structure to provide adequate strength.
The invention, together with other objects, will be more clearly
understood when the following description is read in connection with
the accompanying drawings, in which: Fig 1 is a plan view of an
actuator unit embodying the invention installed in an airplane wing
and hingedly connecting control airfoil thereto, the wing and control
airfoil being shown only fragmentarily; Fig 2 is a vertical
longitudinal sectional view of the Fig 1 ' actuator unit, and is taken

along the line 2-2 of Fig 1; Fig 3 is a 'horizontal longitudinal
sectional view through the actuator unit illustrating j Aetails in the
construction of 'a preferred' form of hydraulic control valve;' Fig 4
is 'a fragmentary side view of a valve element constituting 'a part of
the Fig 3 control valve, and shows further construction details; Fig 5
' is a schematic view illustrating the operation of a preferred form
of hydraulic follow-up linkage between the control valve land the
movable airfoil;' Fig 6 is a diagrammatic plan view of an airplane
wing showing a plurality of the actutator units of the invention,
installed therein to separately move two control airfoils; Fig,7 is a
fragmentary vertical longitudinal sectional view of an actuator unit
showing a modified construction for transmitting movement from the
actuator pistons to the control airfoil; Fig '8 ' is a fragmentary
perspective view further illustrating the modified construction shown
in Fig 7; Fig 9 is a fragmentary perspective view of la third means
for transmitting movement from the actuator pistons to the control
airfoil; and Fig 10 is an enlarged fragmentary longiSO s O tudinal
sectional view through one 'of the cylinders and piston assemblies
shown in Fig 2.
GENERAL DESCRIPTION
Referring te the drawing, and more especially to Figs 1 i and 2
thereof, the invention generally comprises a spanwise elongated
actuator unit rigidly supported between wing ribs adjacent the
trailing edge of the wing The junit includes hinge fixtures for
connecting the leading edge of ithe control airfoil thereto It is
contemplated that a plurality of such units will be arranged end to
end along the entire axis of the airfoil to be actuated, as clearly
shown in Fig 6.
Each actuator unit includes an upper and a lower row of closely spaced
fore and aft disposed pistons, the two rows lying in planes on
opposite sides of the hinge axis but wholly between the upper and
lower surfaces of the wing Means are provided to transmit movement
from each row of pistons to a transversely extending plate
constituting a part of the control airfoil leading edge Pressure and
return ducts connect the various piston cylinders to a single pilot
controlled valve so that the pistons in one row may simultaneously be
moved outward to transmit an airfoil deflecting force to said plate on
one side of the hinge line, while the pistons on the other side of the
hinge line are permitted movement in the opposite direction under back
pressure which resists such airfoil movement.
A follow-up linkage connects the movable element of the valve to the
leading edge of the movable airfoil so that the movable element of the
valve is automatically returned to a neutral position by the time the
airfoil completes its pilot directed movement in any direction.

DETAILS OF CONSTRUCTEONFigures 1 and 2 of the drawings illustrate an
actuator unit embodying the invention installed in the trailing edge
of a wing 15, the upper wing skin being cut away in Fig 1 lto disclose
the installation The actuator unit includes an elongated cylinder
block 1,6 to the opposite ends of which are attached rearwardly
projecting hinge fixtures 17 and 18 The cylinder block and the hinge
fixtures are secured rigidly between the aft ends of a pair of
cordwise disposed wing ribs 19 and 20 ' by means of bolts 21 The
leading edge of a control airfoil 22 includes a spar 23 a forward
surface of which rigidly carries properly spaced hinge devises 24 and
25 The hinge joint is completed 'by hinge bolts 219 passing through
the devises 24 'and 25 and through the hinge fixtures 17 and 18,
respectively As previously mentioned it is contemplated that a
plurality of these units will be placed end to end parallel to the
hinge axis to properly support the leading edge of the control
airfoil, as clearly shown in Fig '6.
As a means of preventing the flow of air from the lower side of the
wing to the upper side, or vice versa, through the gap that normally
is present between a fixed and a control airfoil, 'the above hinge
joint preferably includes upper and lower skin panels 26 and 27 at the
extreme trailing edge of the fixed 70 airfoil These skin panels 26 and
27 are preferably flexible and their aft edges project rearwardly
beyond the fixed structure of the wing a short distance, as clearly
shown in Fig 2 Similarly the extreme forward edges 75 of the skin
panels which cover the movable airfoil 2 '2 project forwardly beyond
'the fixed structure of the control airfoil, and are interposed
between the edges of the two panels 26 and 27 The air gap between the
two air 80 foils is thus completely closed and remains closed and
virtually sealed during movement of the control airfoil 22.
Referring now 'to the details of construction of the actuator itself,
the cylinder blocks 1,6 85 include an upper row of counterbored
cylin-ders 2,8, the 'axes of which lie in a plane which is spaced
above the hinge axis 29 Similarly, the cylinder block includes a lower
row of counterbored cylinders 30, the axes of which 90 tle in a plane
spaced below the hinge axis 29.
As clearly shown in Fig 1 the cylinders are closely spaced along the
hinge axis Each of the cylinders is provided with a floating piston
31, all of which are identical Referring to 95 (Fig 10 it will be seen
that each piston includes a longitudinally bored guide stem 32, the
bore of which communicates with 'a cross-bore 33 adjacent the piston
proper The piston is provided with an annular groove 34 in which is
100 seated a conventional flexible 0-ring 35 and a pair of backup
rings 3 '6 'and 3,7 to reduce the tendency of the 0-ring 35 to be
extruded between the piston and the cylinder wall under pressure The

aft end of the piston 105 is bored and the bore is provided with a
self-lubricating bearing insert 38 and forms a ball joint socket for
the spherical head 39 of a push rod 40 The aft end of the piston is
provided with a rearwardly projecting short 110 collar 41 which is
swaged slightly to retain the spherical head 39 The push rod projects
through a central bore 141 in a combination cylinder cap and push rod
guide 42 which is held in position by means of studs 43 The 115 bore
141 is concentric with the longitudinal axis of the piston 31, but is
larger in diameter than the push rod 40 to permit limited universal
movement for the push rod.
As can be clearly seen in Fig 2 the leading 120 edge surface of the
spar 23 of the control airfoil is provided with a heavy metal plate 44
which extends spanvise between each pair of hinge clevises 24 and 25
The forward surface of plate 44 is provided with two hinge 125 wise
extending rows of recessed push rod seats of hyperbolic section, the
seat openings being of slightly larger diameter than the received ends
of the push rods 40 The seats are properly spaced and positioned to
receive the aft 130 785 J 72 ports 5 '8 and 59, which respectively
communicate wiith ducts 46 and 47 in the cylinder block 'by means of
registering ducts 60 and 61 in the valve casing It will be noted that
duct 46 communicates with a header duct 62 70 in the cylinder block
16, and that the header 62 communicates iith the counterbore of each
upper row cylinder 28 Similarly, duct 47 communicates with a header
duct 63 which communicates with the counterbore of each 75 lower row
cylinder 30.
Near its opposite ends, land spaced outward respectively from the
distributing ports 58 and 59, the valve casing has pressure fluid
return ports '64 and '65 which communicate with a 80 return conduit 66
by means of ducts 67 and 68.
Referring particularly to Figs 3 and 4, it will be seen that the
central valve head 52 is provided at its opposite ends with fluid 85
metering slots 169, and 70, greater in depth at their outer ends than
at their inner ends, as indicated by the broken lines in Fig 3 At
their inner ends only, valve heads 51 and 53 are provided with similar
fluid metering slots 90 71 and 72, which 'are narrower than slots 69
and 70 and therefore provide a lesser fluid flow area.
When the slidable valve element 50 is in neutral position the inner
ends of slots 69 and 95 communicate minutely with port 55, as shown in
Fig 3 'Similarly, the smaller ends of slots 71 ' and 72 in heads 51
and 53 communicate minutely with return ports 65 and 64 A continuous
but very minute flow of pres 100 sure fluid is therefore provided from
feed port to distributing ports 58 ' and 59 land thence to return
ports 64 'and '65 Since the slots 71 and 72 are smaller than slots 69
and 70, :a continuous fluid pressure is therefore main 105 tained on

the pistons in both rows of cylinders.
This is an important feature of this invention, because the difference
in' flow area provided by the mentioned slots also serves to maintain
a back pressure on the pistons in either row 110 while the pistons in
the other row are being moved outward to deflect the airfoil Flutter
of the 'control airfoil is thus prevented while it is in any
stationary position of deflection or is in neutral, as well as during
the actual 115 deflecting movement.
Again referring to Fig 1, the valve operatlng linkage includes a
control rod '73 of sufficient length to service whatever number of
lactuator units are installed X deflect the par 120 ticular control
airfoil, in this case four units.
Rod '73 extends parallel to the hinge line and is reciprocable by
means of a pilot controlled member 74, illustrated as a simple lever
pivotally mounted at 75 on 'a fixed pivot The lower 125 end of lever
74 is pivotally connected to, rod 73 at 76.
A link 77 has one end pivotally connected at 78 to a sleeve 791 which
is adjustable lengthwise on rod 73 ' by means of nuts 180 and 81 130
ends of the push rods, one row of seats being above the hinge line 29
and the other row below that hinge line The seats are designated by
the numeral 45 With the arrangement described it will be seen that the
control airfoil 22 may be disconnected from the fixed airfoil iby the
simple removal of the hinge bolts 29 As the aft ends of the push rods
leave the seats 45 in the control airfoil, the rods gravitate to the
lower surface of;the bore 41 in the guides 42 Due to the shape of the
seats it is a very simple matter to re-install the control airfoil on
the fixed airfoil, the aft ends of the push rods 40 simply centering
themselves in the respective seats.
The forward ends of the counterbores of the respective cylinders 28
and 30 'are connected by means of ducts 46 and 417 with a control
valve 48 With the arrangement thus described it will: be seen that if
the pistons 31 in ithe upper row of cylinder 28 are forced aft
simultaneously and the pistons in the lower row of cylinders 30 are
permitted to travel in the opposite direction simultaneously, the
'control airfoil 22 will be forced to move clockwise (in Fig 2) about
its hinge axis 29 Also that if the forward movement of the pistons in
the row of cylinders 30 is resisted by hydraulic beack pressure during
this movement the control airfoil will be prevented from "fluttering"
due to airstream loads The hydraulic system for controlling such
movement will now be described.
VALVE AND FOLLOW-UP CONSTRUCTIONWhile any hydraulic valve of suitable
design may be used to control the above described actuator unit, a
valve of preferred construction is illustrated in 'Figs 2 to 5
inclusive It is preferred because it is capable of maintaining a

continuous hydraulic pressure on all the pistons in both rows
regardless of their relative positions in the cylinders, and is also
capable of maintaining a continuous back pressure on either row of
pistons while the pressure fluid is being forced into the return line
from their respective cylinders by outward movement of the other row
of pistons.
The valve casing is secured in a suitable manner, 'as by studs 49, to
the forward edge of cylinder block 16 The valve includes a
reciprocable element 50 '(Fig 3) which carries three spaced enlarged
diameter pistons or valve heads 5,1, 52, and 53 which snugly fit and
are slidable in a longitudinal bore 54 in the casing.
Intermediate the ends of the bore 54 iand concentric therewith, the
casing is provided with 'an enlarged diameter fluid pressure feed port
55 which ommunicates with a fluid pressure supply line 56 ' by means
of la duct 517 Port 55 is lesser in length than the central valve head
52.
lOn opposite sides of the port 55 and spaced therefrom are a pair of
similar concentric enlarged diameter pressure fluid distributing
7185,7,72 The outer end of link 77 is pivotally connected at 82 to the
valve element 50 by means of a clevis 83.
Intermediate its ends link 77 is pivotally connected at 84 to one end
of a short link 85, the other end of which is pivotally connected at
86 to one arm of a bell crank 87.
Bell crank 87 is mounted on a fixed pivot 88, and its other arm is
pivotally connected at 89 to one end of a link 90 The other end of
link is pivotally connected at 91 to the leading edge of the movable
airfoil 22 at a point well to one side of the hinge line 29, in this
case below the hinge line so that link 90 is forced to move
longitudinally as the airfoil moves in either direction about its
axis.
Linkage such as above described is duplicated for each actuator unit
installed It will thus be understood that the valve elements 50 of all
actuator units are simultaneously moved in the same sense by the
single rod 73, and that all valve elements 50 are likewise
simultaneously moved in the same sense by the respective linkage
assemblies when the control surface is deflected in either direction.
OPERATION Referring to Fig 5, as lever 74 is moved counterclockwise,
link 77 is initially moved in the same sense about its pivot 84, which
pivot initially serves as a fixed pivot due to resistance of the
control airfoil to deflection.
Counterclockwise movement of link 77 forces valve element 50 to the
right in Fig 5.
Slot 69 in valve head 52 affords free flow of pressure fluid from feed
port 55 into distributing port 59 and thence through the duct 47 and

header 63 into the lower row of cylinders in each actuator unit All
lower row push rods 40 are consequently moved outward by their
respective pistons 31, and the control airfoil 22 is forced to move
upward (counterclockwise in Fig 2) about its hinge axis 29.
Simultaneously plate 44 forces the upper row of push rods 40 to move
in the opposite direction, upper row pistons 31 moving with their
respective push rods, forcing liquid in the upper row cylinders out
into header 62, duct 46, distributing port 58 and through slot 72 and
duct 67 into the return line 66 There is a fluid pressure resistance
to such upward movement of the control airfoil, however, because slot
72 provides less fluid flow area than slot 69, this will be clearly
understood by those familiar with this art.
As Bhe control airfoil is deflected upward, its leading edge spar 23
moves from the position shown in 'Fig 5, a distance indicated by the
lines 92 and 93 During such movement of the control airfoil link 90
forces bell crank i 8 i 7 to pivot to the dotted line position
indicated, and link 7,7 is thereby moved -to the dotted line position
shown, returning valve element 50 to its neutral position, as shown
in' Fig 3 The return of the valve to neutral 'is thus automatic, and
occurs without any additional movement of lever 74 by the pilot.
Actually the movement occurs and is completed at just about:the time
the pilot ceases to move lever 74 The valve is thus always in
condition to direct movement of the control 70 airfoil in either
direction about its axis, within limits, of course To limit control
airfoil travel fixed stops 94, 95, 96 and 9,7 (Fig 1) are provided
Stops 94 and 95 serve to limit the travel of rod 73, while stops 96
and 97 limit 75 the travel of the aft end of link 77.
in addition to the objects and advantages of the invention previously
mentioned, it should 'be noted that the actuator unit described
provides a minimum length of liquid 80 column between the pistons and
the control valve 50, which materially increases rigidity.
Also that metering of the liquid is accomplished on the return side of
the control valve Which assures that all push rods no;t only re 85
main in continuous contact with the control airfoil plate 44, but
exert a continuous pressure or thrust 'against that plate, even when
the push rods are retracting The control airfoil is thug prevented
from "fluttering" due 90 to variable pressures on its opposite
surfaces.
Additionally it should be observed that since hydraulic pressure 'is
always exerted on only -one side of each piston, the C-ring 35 and its
back-up rings 3 '6 and 37 are continuously 95 maintained at the aft
end of the piston groove in which they are seated, even, when the
piston is moving outward in its cylinder This greatly reduces wear on
the O-ring and provides long leak free life for the system 100

Referring now to certain modified details in construction, Figs 7 and
8 illustrate a means for better distributing the push rod thrust along
the forward plate of the control airfoil.
/TO this end the outer or aft ends of the res 105 pective push rods 98
are flattened us at 99 and are anchored by means of pins or bolts 1.00
in the channel of a channel member 101.
This channel member is elongated spanwise and its aft edge is adapted
to seat in a spanwise 110 extending larger groove 102 in the plate
103, which is secured to the leading edge of control airfoil 22 This
distribution of the thrust through the channel member to the plate
reduces the per square unit load on the con 115 tacted plate area by
approximately 77 %', as proven by actual tests This reduces friction,
galling of contacting surfaces, etc.
Fig 7 also illustrates a different type of combination cylinder cap
and push rod guide 120 104 It includes a cylinder plug 105 having a
central bore 106 larger in diameter than the push rod 98, and a
counterbore 107 A dust plate 108 seats in counterbore 107, and since
the plate is smaller in diameter, it has limited 125 movement in all
directions normal to the counterbore axis Dust plate 108 has a central
perforation which tightly receives push rod 98.
The plate is held on its seat in the counterbore by a flat washer 109
secured by bolts 110, 130 7 '85,772 a portion of the trailing edge of
the fixed airfoil and the other of said rigid members constituting a
portion of the leading edge of the movable airfoil, and the hinge
joint including a series of spanwise spaced aligned 70 fulcrums
projecting from lone of said rigid members towards the other, and
similarly spaced means along said other rigid member engaging said
fulcrums to complete a generally spianwise disposed hinge joint
between the 75 two airfoils.
7 An operating mechanism as set forth in any of claims 2 to 6, in
which said actuators include a plurality of banks of hydraulic
cylinders rigidly supported by one of said air 80 foils, one row
located on one side of said hinge axis and one row located on, ithe
opposite side thereof, and each cylinder having a piston projecting
therefrom into abutting contact with the adjacent edge of the other
airfoil, the two 85 rows of pistons contacting 'said other airfoil
along lines which lie on opposite slides of said hinge axis.
18 An operating mechanism as set forth in claim 7, including means for
introducing hyd 90 raulic fluid under pressure into one row of said
cylinders to project their respective plungers outward while affording
return of fluid from the other row of icylinders and retraction of
their respective plungers a like dis 95 tance.
9 An operating mechanism as set forth in claim 8,:and means for
maintaining a continuous outward hydraulic pressure on all of said

pistons, and consequent firm abutting 100 pressure on the adjacent
edge of the airfoil which the pistons contact, regardless, of the
relative piston positions or direction of travel.
An operating mechanism as set forth in claim 18, and means for
simultaneously con 105 trolling the introduction of fluid into one row
of said cylinders and the return of fluid from the other row of
cylinders to maintain positive abutting contact of (the pistons in
both rows against the adjacent edge of ithe airfoil which 110 they
contact to positively prevent flutter of the movable airfoil' about
its hinge axis.
11 An operating mechanism as set forth in claim 8, 9 or 10, in which
each piston includes a push rod having on'e end seated in a seat 115
formed in that 'end of the piston facing the hinge joint and having
its opposite end seated in a seat in the adjacent edge of said rigid
member of said other airfoil.
12 An operating mechanism' as set forth in 120 claim 11, in which said
seats in said rigid member are generally concave and at least one
cross sectional direction and are greater in dimension in said
direction than the respective ends of the corresponding push rods
which 125 they seat.
13 An operating mechanism, as set forth in claim 11, including guides
located intermediate the ends of said push rods and supported by one
of said rigid members, there being one 130 which also serve to hold
the entire assembly in, position on the cylinder block 16 'The central
perforation in washer 109 is larger in diameter than the push rod 98
but smaller in diameter than the outside diameter of dust plate 108.
Fig 9 illustrates a modified design for the outer end of la push rod
It includes an integral T-'bar 111 adapted to extend spanwise and seat
in the groove 102 This design also better serves to distribute the
push rod thrust spanwise along plate 103, with results similar to
those provided by the f Ieig 7 arrangement.
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Description: GB785773 (A) ? 1957-11-06
Automatic brake adjuster for brake lining wear
78,5773 4 ' d Date of Application and filing Complete Specification:
Nov 16, 1955.
-z w) o No 32751155.
Application made in United States of America on June 17, 1955.
Index at Acceptance:-Class 103 ( 1), E 2 N 2 (A 2 A: D 2 A: D 6 A: E
5: K 1).
International Classification:-FO 6 d.
Automatic Brake Adjuster for Brake Lining Wear.
We, THE GOODYEAR TIRE & RUBBER COMPANY, a corporation organized under
the Laws of the State of Ohio, United States of America, with offices
at 1144 East Market Street, Akron, Ohio, 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 automatic brake adjustors, and especially to
improvements in automatic brake adjustors provided in braking means
for automatically compensating for wear on brake linings.
This invention relates to brakes and particularly to the automatic
adjustment pin or other means provided in brakes of the type which
have an automatic adjustment pin or the like for controlling the
positioning of brake lining means in a brake and permitting automatic
compensation in the brake as the brake lining means are worn away in
use.
One problem that arises in brakes having automatic brake adjustor
means present therein is that when the brake linings become worn and
are replaced with new brake linings, the positions of the automatic
adjustment pins must be changed in view of the thick, new brake
linings in the brake Also, the dismantling of the brake is complicated
when one must remove the adjustment pin in making any brake repairs
These automatic adjustment pins may comprise a pin substantially
fixedly positioned in the brake by some type of friction means which
allows movement of the adjustment pin along its axis as wear occurs It

is very difficult to force these adjustment pins backwardly through
the friction motion retarding means provided therefor, nor is it easy
to otherwise remove the adjustment pins so that the servicing-of the
brakes having the adjustment pins therein becomes a more complicated
operation than in types of brakes not having such lPrice 3 s 6 d l
automatic adjustment pins present therein.
The general object of the present invention is to provide a new and
improved type of an automatic brake adjustor for use in brakes of the
class described wherein the adjustor is 50 characterized by its ready
removability from the remainder of the brake assembly.
Another object of the invention is to provide a tubular member in an
automatic brake adjustment structure, which tubular 55 member is
positioned on a support core that can be removed from the brake
assembly to facilitate brake relining and servicing operations.
A further object of the invention is to 60 provide a removable
sub-assembly for automatic adjustment of the brake release position as
brake lining wear occurs.
In order that the invention may be more clearly understood, reference
will now be 65 made to the accompanying drawings wherein an embodiment
is shown for purposes of illustration and, wherein:
Fig 1 is a vertical section of a brake embodying the principles of the
invention; 70 Fig 2 is a fragmentary elevation of the brake-of Fig 1;
and Fig 3 is an enlarged detail section of the automatic adjustment
means of the invention.
When referring to corresponding parts 75 shown in the drawings and
referred to in the specification, corresponding numerals are used to
facilitate comparison between such equivalent parts.
The invention consists of a braking device, 80 including a brake
lining positioning member, an adjustment pin secured to and extending
from the brake lining positioning member, a sleeve on the adjustment
pin, friction means for engaging the sleeve to retard movement of 85
the adjustment pin, and means for releasably securing the sleeve to
the pin so that upon release the pin can be removed from the sleeve
without disturbing the engagement of the friction means with the
sleeve 90 785,773 _ The brake of the invention is indicated as a
whole' by the numeral 1 and the drawings show the details of such
brake This brake 1 includes a suitable brake housing 2 having a
separate end member 3 suitably secured thereto, as by bolts 4, to
define a peripheral opening in the brake housing in which a plurality
of 'brake discs 5 are received for limited movement along the axis of
the brake housing These brake discs 5 are adapted to be engaged and
carried by a suitable wheel (not shown) by engagement with splines 6
in the periphery of the brake discs An annular brake pressure plate,
or brake lining positioning member 7, is provided in the brake and has

an annular control piston 8 secured thereto and extending therefrom.
The annular control piston 8 is received in a chamber 9 shaped
complementary thereto in which the control piston 8 is snugly received
for sliding action therein Actual braking action is produced by a
conventional control member (not shown), such as a brake pedal or arm
operated by the pilot of the aircraft with which the brake 1 of the
invention is associated, or by the operator of the apparatus on which
the housing 2 is positioned Such actuation of a brake pedal or other
member will cause hydraulic pressure to be set up in a conventional
hydraulic system connected thereto, which pressure is transmitted to
the brake 1 by means of a conduit 10 secured to the brake housing by a
fitting 11 The hydraulic pressure fluid flows through a port 12 to the
chamber 9 to set up braking movement on the annular control piston 8
Conventional 0-ring gaskets 13 are provided for sealing the control
piston in the chamber 9.
A brake lining 14 is secured to the brake pressure plate 7 and moves
therewith, whereas a similar brake lining 15 is secured to the housing
member 3 Other brake lining and carrier means 16 are non-rotatably
positioned intermediate adjacent faces of the brake discs 5 Thus the
introduction of hydraulic fluid under pressure to the chamber 9 will
cause axial movement of the control piston 8 along the brake 1 and
force the brake lining means and brake discs into tight braking
engagement with each other -to produce the desired brake action on the
wheel to which the brake discs 5 are secured.
As an important element of the present invention, an automatic
adjustment device or assembly is provided for use with the brake 1,
and such means include an automatic adjustment pin 17 secured to and
movable with the brake pressure plate pivot In this instance, such
automatic adjustment pin 17 comprises a conventional bolt, the head 18
of which is seated in a complementary shaped recess provided in one
face of the brake pressure plate The automatic adjustment pin 17 has a
nut 19 on one end thereof which may be retained in position by a lock
wire 20, or other conventional lock means.
Another special feature of the automatic adjustment pin 17 is that a
sleeve or tube 21 is carried thereby and held thereon snugly 70
against any relative longitudinal movement thereto by abutting one end
of the sleeve 21 against the brake pressure plate 7 and the other end
against the nut 19 The actual friction means for engaging the
automatic 75 adjustment pin 17 actually engage the sleeve 21, and
comprise friction or grip means 22 that tightly engages the periphery
of the sleeve 21 A spacer sleeve 23 bears against the axial outer end
of such friction means, and 80 has a sufficiently tight fit on the
sleeve 21 to maintain its position thereon under any force exerted by
the spring 28, hereinafter described, -but to be slidable along sleeve

21 under pressure of the hydraulic fluid in cham 85 ber 9 when
clearance space between members 24 and 26 is taken up during brake
application before full braking is attained Spacer sleeve 23 has a
flange 24 extending therefrom at its axially outer end, and the
friction means 90 22 contacts or seats against a radially inwardly
extending flange 25 provided on a positioning or locating sleeve 26
for its retarding action The axially inner end of the locating sleeve
26 bears on a removable cup 95 shaped member 27 that seats on the
brake housing 2 The locating sleeve 26 encompasses the friction means
22 In use, the sleeve 21 and adjustment pin 17 move as a unit with the
brake pressure plate 7 so that, as brake 100 lining wear occurs, such
brake pressure plate, or brake lining carrying member, will be moved
farther and farther axially of the brake 1 towards the end member 3 of
the brake.
As such wear occurs, the friction means 22 105 will be moved against
the cup-shaped member 27 to abut thereon and be held in position while
the automatic adjustment pin moves inwardly of the brake and effects
an adjustment in the positioning of the brake means 110 both when
operative and when released.
In order to provide the desired clearance in the brake upon release of
the braking forces, a conventional coil spring 28 is carried by the
locating sleeve 26 and has one end 115 abutting against the cup-shaped
member 27.
The opposite end of the spring 28 seats against the flange 24 of the
spacer sleeve 23 so that upon release of the hydraulic braking forces,
such spring 28, having been com 120 pressed during the braking
movement of the automatic adjustment pin 17 and associated means,
moves the automatic adjustment pin 17 and the brake pressure plate 7
axially outwardly of the brake slightly to provide the 125 required
operating clearance.
A conventional cover 29 -is engaged with the brake housing 2 and is
shown in somewhat exaggerated axial clearance relationship to the
flange 24 of the spacer sleeve In all events, 130 ment pin, and means
for releasably securing the sleeve to the pin so that upon release the
pin can be removed from the sleeve without 50 disturbing the
engagement of the friction means with the sleeve.
2 Braking device according to claim 1, including means engaging the
adjustment pin to provide operating clearance in the brake 55 when
released.
3 Braking device according to claim 2, wherein the means engaging the
adjustment pin comprises spring means for moving the pin and the brake
lining positioning member 60 to an inoperative released position when
the brake is not actuated.
4 Braking device according to any preceding claim, including means

operatively associated with the brake lining positioning 65 member for
controlling braking action thereof.
Braking device according to claim 4, wherein the means for controlling
braking action comprises piston means and cylinder 70 means.
6 Braking device according to any preceding claim, wherein the
adjustment pin limits movement of the brake lining positioning member
connected thereto and 75 moving therewith, the sleeve being based
against the brake lining positioning member.
7 Braking device according to any preceding claim, wherein the sleeve
on the adjustment pin is held against movement 80 along the axis
thereof to form a unit with the adjustment pin.
8 Braking device according to claim 7, wherein the sleeve is removably
secured to the adjustment pin 85 9 Braking device according to any
preceding claim, wherein the friction means is adapted to retard axial
movement of the sleeve but to permit such movement when a
predetermined pressure is exceeded 90 Braking device substantially as
illustrated by the accompanying drawings and as described with
reference thereto.
MARKS & CLERK.
the spring 28 urges the spacer sleeve 23 and associated means axially
outwardly of the brake 1 until the flange strikes the inner surface of
the cover 29, when the brake is released.
When relining or servicing the brake of the invention, the nut 19 is
removed from the automatic adjustment pin 17 so that it can be readily
removed from the brake and the relationship between the sleeve 21 and
friction means 22 is not affected in any manner by removal of the
automatic adjustment pin means or its carrier support from the
apparatus Likewise, the sleeve 21 and associated means are readily
repositioned in the apparatus as the automatic adjustment pin may
easily be reassembled in and secured to the sleeve 21 and no further
assembly or adjustment of the adjustment pin is required.
It also will be noticed that the friction means 22, spacer sleeve 23
and other associated parts, can be positioned on the sleeve 21 prior
to engagement of such sleeve by the automatic adjustment pin 17, and
the subassembly can be tested to be sure that it is assembled properly
and that it operates in a satisfactory manner.
In view of the foregoing it will be seen that the objects of the
invention have been achieved as a novel type of an automatic
adjustment pin has been provided in the brake and the servicing and
assembly thereof has been facilitated and simplified.
While one complete embodiment of the invention has been disclosed
herein, it will be appreciated that modification of this particular
embodiment of the invention may be resorted to without departing from
the scope of the invention as defined in the appended claims.

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