5511 5515.output

* GB785919 (A)

Description: GB785919 (A) ? 1957-11-06

Improvements in or relating to internal combustion engines with two or morecylinders

Description of GB785919 (A)

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

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

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

controls the outlet from the cylinder, whereas the mixture intake is through the transfer ports 13. The 6-cylinder arrangement diagrammatically illustrated in Figure 4 is obtained essen 75 tially by trebling the arrangement according to Figure 2. In Figure 1, at 11 a pump unit is indicated which can be used in the other embodiments also It comprises a coolant pump, a lubricat 80 ing oil pump and a return pump for returning the lubricant into the lubricant container This pump unit is connected to the drive of the rotary valve through an intermediate shaft 5 formed as a downward extension of the rotary 85 valve shaft.

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* GB785920 (A)

Description: GB785920 (A) ? 1957-11-06

Improvements in or relating to copying machines


We, THE BIRMINGHAM SMALL ARMS COM- PANY LIMITED, a British Company, of Small Heath Works, Birmingham 11, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: - This invention relates to copying machines in which a tool effecting its cutting by relative reciprocation between the tool and the work is positioned hydraulically in accordance with the position of a tracer that is caused to follow a former in corresponding relative reciprocation between the tracer and the former The invention is

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

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

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

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

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

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

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

continue to respond to the tracer 30 on the return stroke, they remain clear of the work by the amount of the gap throughout that stroke, but are immediately dropped to the work when the piston 89 is raised at the end of each return stroke.


* GB785921 (A)

Description: GB785921 (A) ? 1957-11-06

Improvements in valves for gas containers


PATENT SPECIFICATION 72 Inventor:-FREDERICK DERRICK OLIVER. Date of filing Complete Specification: Feb 17, 1956. s M 1 Application Date: Feb 18, 1955 No 4911 5 o 5. Complete Specification Publi 8 hed: Nov 6, 1957. Index at Aeceptance:-C S 135, VD( 4 X 601: 9 F 11 E:11 X: 20 X), VW 1 C 5 D. International Classification:-FO 6 k. COMPLETE SPECIFICATION. Improvements in Valves for Gas Containers. We, CALOR GAS (DISTRIBUTING) COMPANY LIMITED, a British Company, of Poland House, 161-167 Oxford Street, London, W.1, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described, in and by the following statement:- This invention relates to valves for gas containers and more particularly to valves for attachment to gas storage cylinders for use in controlling the discharge of gas from such cylinders to a burner or

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

knurled control knob or the like 17 which is secured to the outer end of the valve pin by locking nut 18, the portion 19 of the valve pin being of square or rectangular section so as to prevent relative rotation of said valve pin 12 and said control knob The said control 15,921 65. s O ' r_ 11 '. 785,921 knob 17 is provided at its outer end with an axial recess which houses the locking nut 18 and said recess is normally closed by a blanking disc 20 which snaps into an annular groove 21 in the control knob This blanking disc 20 cannot be removed from its seating without buckling or fracturing said disc so that the valve assembly cannot be dismantled by unauthorised persons without leaving evidence that dismantling has taken place The shank portion 11 of the valve pin 12 is slidable in a guide plug 22 secured in a recess in the valve housing by a grub screw 23 Between the plug 22 and the bottom of the recess in which it is secured is a rubber or other resilient buffer sealing washer 24 which forms a resilient stop against which engages the upper or outer of two annular flanges 25, formed on the valve pin between the shank and screw portions 11, 15 respectively When the valve is opened to its maximum limit By this means the valve is prevented from being friction locked in the open position. The provision of the two valve pin guide flanges 25 limits side thrust on the guide plug 22 and permits the upper and lower ends of the valve pin to float freely in free fit bores, thus eliminating the high degree of concentricity normally required between the bearings of rotary pin-like members. Between the two annular guide flanges 25 is a sealing ring 26 which permits lubricant to be trapped between said sealing ring and the sealing washer 24 whereby lubrication of the bore by scavenging action is ensured. The valve control knob 17 and the body 1 of the valve are each provided with an eyelet or the like 27 and 28 respectively to enable a sealing element, such as a length of wire, to be used to connect the two parts when the valve is screwed into a newly filled gas storage cylinder so that the valve cannot be opened without breaking said sealing element.


* GB785922 (A)

Description: GB785922 (A) ? 1957-11-06

Improvements in or relating to machines for roughing shoe parts


PATENT SPECIFICATION Index at Acceptance:-Classes 31 ( 1), H 3; and 80 ( 4), F 5 B. International Classification-C 1 jib F 06 p. COMPLETE SPECIFICATION. Improvements in or relating to Machines for Roughing Shoe Parts. We, THE BRITISH UNITED SHOE MACHINERY COMPANY LIMITED, of Union Works, Belgrave Road, in the City of Leicester, a British Company registered under the Companies Acts 1862-1898, do hereby declare the invention (a communication from United Shoe Machinery Corporation, of Flemington, in the State of New Jersey, United States of America, a Corporation duly organised under the laws of the said State of New Jersey, and having a place of business at 140 Federal Street, Boston, Commonwealth of Massachusetts, United States of America), for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: - This invention is concerned with improvements in or relating to machines for roughing shoe parts (the term "shoe" being used herein generically as including outer footwear generally) and is to be regarded as constituting an improvement in or modification of the invention of British Letters Patent No. 687,260. There is hereinafter described one convenient machine, provided by the invention and illustrative thereof, which illustrative machine (like the machine described in the Specification of the aforesaid patent) has a toothed roughing tool or cutter which is particularly suitable for roughing the margins of the flesh sides of leather outsoles supported flesh side up, in the machine, preparatory to the attachment of the outsoles to shoes by cement. The machine described in the Specification aforementioned comprises a

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

like that of the machine described in the aforementioned Specification, comprises a cylindrical member concentric with and surrounded by a work support comprising a pair of concentric workpiece supporting sleeves which are yieldable axially independently of each other. In contrast, however, with the machine described in the aforementioned Specification the roughing tool of the illustrative machine is movable horizontally into different operating positions with relation to the work support in such a manner as to vary the distance inwardly of the edge of the sole to which the tool roughens the sole Means are also provided in the illustrative machine for limiting the axial yielding movement away from the roughing tool, of the inner workpiece supporting sleeve relatively to the outer one. When this limit is reached the two sleeves yield together, and thus obviate the possibility of the inner sleeve standing above the outer sleeve and obstructing the insertion of a workpiece Means are also provided for adjusting the resistance of the workpiece supporting sleeves to yielding away from the roughing tool and consequently for adjusting the pressure with which the workpiece is held against the roughing tool To facilitate insertion of workpieces upper and lower workpiece guiding members, outside the supporting sleeves, are provided, the upper member comprising an arcuate abutment which is fixed to a cover of the machine and which surrounds a portion of the roughing tool This abutment has a workpiece-guiding face substantially in alignment with cutting edge portions of the roughing tool The lower guiding member comprises an arcuate rest which surrounds an outer portion of the outer workpiecesupporting sleeve and has a guiding face substantially in alignment with the workengaging face of the outer sleeve These guiding members together form a passage through which the workpiece may be conveniently presented to the roughing tool. In order that the above and others of the various objects of the invention may become more clear, there will now be given a detailed description, with reference to the drawings accompanying the Provisional Specification, of the illustrative machine above referred to It is to be clearly understood however that the particular illustrative machine is selected for description merely by way of exemplification of the invention and not by way of limitation thereof. The several features of the invention will 70 be found set out respectively as appended

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* GB785923 (A)

Description: GB785923 (A) ? 1957-11-06

Means for mounting a liquid fuel injection pump on an internal combustionengine


We, C A V LIMITED, of Warple Way, Acton, London, W 3, a British Company, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:- This invention has for its object to provide in a simple and convenient form, a means for mounting a liquid fuel injection pump on an internal combustion engine. A means in accordance with the invention comprises a hollow bracket having an opening in its rear face and in one of its sides, a pair of interengaging toothed wheels contained within the bracket, one of which wheels is adapted for spline connection with the driving spindle of the pump, and the other of which is adapted for engagement with a driving toothed wheel on the engine. The invention also comprises the combination of a means as defined in the preceding paragraph and a pump one end of the body part of which is adapted to be secured to an open side of the bracket. In the accompanying drawings Figures 1 and 2 are respectively sectional side and end views illustrating a pump mounting means in accordance with the invention. Referring to the drawings, the hollow bracket a is provided with a flat rear face adapted to be secured to the exterior of the body part of an engine b over an aperture which exposes a gear wheel c on, for example, the cam shaft of the engine, and in the said face of the bracket is formed an aperture through which can extend into engagement

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


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