5361 5365.output

* 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. COMPLETE SPECIFICATION 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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* GB785770 (A)

Description: GB785770 (A) ? 1957-11-06

Improvements relating to thread twisting spindles having thread-tensioningdevices


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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. Complete Specification Published: Nov 6, 1957. Index at acceptance:-Class 120 ( 2), D 2 C 5 (D:0:X). International Classification:-DO 2 d. COMPLETE SPECIFICATION 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.


* GB785771 (A)

Description: GB785771 (A) ? 1957-11-06

Improved device for hydraulic governing of engines


PATENT SPECIFICATION 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.

COMPLETE SPECIFICATION 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


* 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. Complete Specification Published: Nov 6, 1957. 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 CONSTRUCTEON Figures 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 CONSTRUCTION While 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.


* GB785773 (A)

Description: GB785773 (A) ? 1957-11-06

Automatic brake adjuster for brake lining wear


PATENT SPECIFICATION 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. Complete Specification Published: Nov 6, 1957. 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. COMPLETE SPECIFICATION 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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