4566 4570.output

* GB784973 (A)

Description: GB784973 (A) ? 1957-10-23

Harvester for root crops

Description of GB784973 (A)

COMPLETE SPECIFICATION Harvester for Root Crops We, JAMES MCPHEE, of 420, Hilton Drive, Aberdeen, WILLIAM EDWARD GARDER, of 83, Hilton Street, Aberdeen, and DANIEL CALDER, of 3, Burns Crescent, Whitburn, West Lothian, all of British 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 :- The subject of this invention is a harvester for root crops, particularly potatoes. For simplicity, the crops in question are hereinafter referred to as"potatoes". The primary object of the invention is to provide for ready separation of stones from the harvested potatoes. A further object is to provide for grading of the potatoes. A harvester according to the invention incorporates a jigging screen (or screens) mounted on a frame, means for conveying harvested potatoes to the screen (or screens) a chute (or chutes) leading from one end of the screen (or screens) to a loading station, and a nozzle (or nozzles) under the chute (or chutes) and serving to direct a jet of air under pressure to the exit from the chute (or each chute). A harvester according to the invention is illustrated in the accompanying drawings in which :- Fig. 1 is a side elevation of the harvester; Fig. 2 is a plan view with some parts omitted; Fig. 3 is a fragmentary elevation of a part of the harvester, drawn to a larger scale than the preceding Figures. Referring to the drawings, 1,2 denote a pair of superposed jigging screens mounted for joint jigging movement between stanchions 3 of

spring material upstanding from a frame 4. The mesh of the screen 1 is greater than that of the screen 2. 5,6 denote chutes each leading from one end of the respective screen 1 or 2 to the upper end of a loading station constituted by the mouths of open-topped bags 8,9 held in position on a platform 7 by clips 10,11 and each associated with and spaced from one of the chutes 5'or 6. The clips 10,11 are adjustably carried by the frame 4. 12 (Fig. 3) denotes a nozzle secured to the underface of the chute 5, connected to the storage tank 13 fed by an air compressor 14, and adapted to direct a jet of compressed air to the exit from the chute 5. It is to be understood that, a similar nozzle is secured to the underface of the chute 6. 15 denotes an elevator provided at its lower end with a plough 16 and mounted on the frame 4. The elevator 15 is operatively connected by a driving band (not illustrated) to the power drive of a tractor. Located adjacent to the elevator 15 is an inclined endless belt conveyor 18 trained around end rollers 19,20 journalled in the frame 4 for rotation about horizontal axes. The roller 20 is mounted on a shaft 21 carrying a pulley 22, a belt (not illustrated) is trained around the pulley 22 and an output pulley (not illustrated) of an engine 17 mounted in the frame 4. The engine 17 is adapted also to drive the compressor 14. A pair of eccentric discs 23 on opposite sides of the conveyor 18 are mounted on the shaft 21. Eccentric straps 24 encircling the discs 23 are each coupled by a connecting rod 25 to the screen assembly 1,2. The frame 4 serves as a chassis for the harvester and is mounted on ground wheels 26. In practice, when it is desired to harvest potatoes, the harvester is coupled to the tractor and the engine 17 is actuated to operate the elevator 18, the screens 1,2 and the compressor 14. During travel of the harvester over the ground, the plough 16 penetrates the soil. Potatoes, earth and stones are ejected by the plough 16 on to the elevator 15 which is so constructed that, during travel of the potatoes on the elevator, the earth falls through the elevator to the ground. The potatoes and the stones are then discharged from the elevator 15 on to the conveyer 18 which conveys the potatoes and the stones to the upper screen 1. Jigging of the screens 1,2, causes potatoes and stones of smaller dimensions than the mesh of the screen 1 to pass through the screen 1 on to the screen 2. The potatoes and the stones then pass to the chutes 5,6 whence the potatoes and the stones pass to the exits from the chutes 5,6. The force of the jets of air issuing from the nozzles 12 is sufficient to impel the potatoes, but insufficient to impel the stones, to the bags 8,9, the stones falling to the ground

through the spaces between the bags 8, 9 and the adjacent ends of the chutes 5,6. What we claim is :- 1. A harvester for root crops, incorporating a jigging screen (or screens) mounted on a frame, means for conveying harvested crop to the screen (or screens), a chute (or chutes) leading from one end of the screen (or screens) to a loading station, and a nozzle (or nozzles) located under the chute (or chutes), and serving to direct a jet of air under pressure to the exit from the chute (or each chute).

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* GB784974 (A)

Description: GB784974 (A) ? 1957-10-23

Improvements relating to valve gear


PATENT SPECIFICATION Date of Application and filing Complete Specification: March 13, 1956. Application made in Germany on March 23, 1955. Complete Specification Published: Oct 23, 1957. 784,974 No 7847/56. Index at acceptance:-Class 7 ( 6), B 2 P 2 (D:K 3:P), B 2 P( 12:13), B 2 Q 3 C. International Classification:-FO 2 f. COMPLETE SPECIFICATION Improvements relating to Valve Gear We, DAIMLER-BENZ AKTIENGESELLSCHAFT, of Stuttgart-Untert Urkheim, Germany, a Company organised under the Laws of 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 valve gear for poppet valves, more particularly valve gear for internal combustion engines, in which a cam co-operates with a tappet head so arranged on the valve stem that relative rotation between the valve stem and tappet head about the longitudinal axis of the valve is possible, and consists essentially in that the tappet head is not only held against displacement in a direction transverse to the valve stem by engagement with the valve stem itself but is also prevented from rotary movement about the axis of the valve stem by parts having sliding engagement with one another. As compared to known constructions, in which the tappet head slides in a tappet guide on the frame side, the construction according to the invention has the advantage that such a guide can be omitted, which is of especial significance as regards weight saving, for example in racing engines, and that tappet heads having a non-plane or curved sliding surface co-operating with the cam, are prevented from having rotary movement about the axis of the valve stem by the said slideguide engagement. It is proposed according to the invention in the case of valves in which the closing movement is accelerated by a lever engaging beneath a shoulder on the valve stem, and pushing the tappet head against the cam causing acceleration of the opening movement, for the said lever and the tappet head to have a sliding engagement with one another for the purpose of preventing rotary movement of the tappet head about the axis of the lPrice valve stem This method provides security against rotation with the help of constructional elements otherwise present, and with minimum expenditure. It is proposed in detail, for this purpose, to 50 arrange for a projection on the tappet head to engage between fork arms of the said lever which fork arms embrace the valve stem and engage beneath the shoulder aforesaid. Spacing washers may be advantageously 55 arranged between the tappet head and the face of the shoulder on which the tappet head rests, the tappet head preferably being recessed so that it overlaps the peripheral edge of the shoulder The valve clearance is ad 60 justed by inserting spacing washers of different thickness, as required The tappet head can furthermore have a central hole for engaging with a pin-shaped part extending from the valve stem above the shoulder 65 A constructional example of the invention is illustrated in the accompanying drawing, wherein:Fig 1 is a vertical sectional elevation of a valve gear according to the invention; and 70 Fig 2 is an elevation as seen from the right-hand side of Fig 1. In the drawing a valve stem 1 produced as a body of rotation has its

top portion 2 reduced to a smaller diameter The part 2 is 75 surmounted by a shoulder 3 above which rises a pin-shaped extension 4 of the stem 1. A tappet head 5 is provided with a central hole to fit the pin 4 and is hollowed out beneath so as not only to seat itself upon the flat 80 surface of the shoulder 3 but so as also to overlap the peripheral edge of such shoulder 3 The axial distance between the top surface of the tappet head 5 and the valve disc 6 is adjustable by inserting washers 7 of appro 85 priate thickness between the tappet head 5 and the shoulder 3 A camshaft 8 with cam 9 is provided for accelerating the opening movement and retarding the closing movement of the valve the top surface of the 90 784,974 tappet head 5 which is engaged by the cam 9 being curved in this example A shaft 10 with a lever arm 11 terminating in fork arms 12 and 13, is provided for accelerating the closing movement and retarding the opening movement The fork arms 12 and 13 when descending engage in corresponding cut-outs 14 in the valve guide bush 15 The tappet head 5 has a depending projection 16 having a sliding engagement between the fork arms 12 and 13, so that the tappet head cannot turn although the stem 1 is rotatably engaged in it. The valve is opened during the acceleration period directly by action of the cam 9, which pushes the valve stem 1 downwards by pressing upon the tappet head 5 Retardation during the opening period and acceleration during the closing period occur with the help of the shaft 10, which carries out an oscillating movement, and when moving clockwise (Fig 1) pushes the valve stem l upwards by reason of the fork arms 12, and 13 of the lever arm 11 engaging beneath the shoulder 3. The movements of the shaft 8 and 10 must be accurately matched to one another by a mechanism not illustrated. The invention is not limited to the constructional example illustrated.


* GB784975 (A)

Description: GB784975 (A) ? 1957-10-23

Apparatus for preventing release of contaminants from the exhaust of aninternal combustion engine


PATENT SPECIFICATION 784,975 Date of Application and filing Complete Specification: March 19, 1956 No 8530156. Complete Specification Published: Oct 23, 1957. Index at acceptance:-Classes 7 ( 2), B 2 W; and 7 ( 6), B 2 B( 2:5:13 C:13 C:13 H:15). International Classification:-FO 2 f, F 06 b. COMPLETE SPECIFICATION Apparatus for Preventing Release of Contaminants from the Exhaust of an Internal Combustion Engine I, FRED EDWARD MCKINLEY, of 14,503, it may afford a long and trouble-free service Garfield Avenue, Paramount, State of Cali life. fornia, United States of America, a Citizen It is yet another object to provide apparatus of the United States of America, do hereby of this nature that is foolproof and entirely declare the invention for which I pray that automatic in operation 50 a patent may be granted to me, and the A further object is to provide apparatus of method by which it is to be performed, to be the aforedescribed nature which does not in particularly described in and by the following any way affect the operation of the engine statement: during other than deceleration conditions. The present invention relates generally to Another object is to provide apparatus of 55 the field of internal combustion engines and the aforedescribed nature which is compact in more particularly to a novel apparatus for size and light in weight. preventing the release of contaminants from These and other objects and advantages of the exhaust thereof the present invention will become apparent It is well known that the exhaust gases from the following detailed description, when 60 issuing from the internal combustion engines taken in conjunction with the appended of automotive vehicles constitute a prime drawings, wherein:source of the so-called " smog" which exists Fig 1 is a partially diagrammetric side in and around the principal population elevational view of a preferred

form of centres of the country The harmful effects apparatus embodying the present invention 65 of this smog upon both animate and in mounted upon a conventional automotive animate objects is likewise very well known vehicle internal combustion engine; and Although many forms of apparatus for pre Fig 2 is a view similar to Fig 1 but showing venting the release of contaminants from the the parts of the apparatus during deceleration exhaust gases of such engines have been of said engine 70 heretofore-proposed, such devices have for Referring to the drawings, a preferred form various reasons proven to be unsatisfactory of apparatus embodying the present invention and accordingly are not now in general usage is shown mounted upon the side of an internal It is a major object of the present invention combustion engine having an intake manifold to provide an effective apparatus for prevent I, an exhaust manifold E, and a carburettor C 75 ing the release of contaminants from the ex The exhaust manifold I is connected to a tail haust of an internal combustion engine pipe T The carburettor C is controlled by Another object of the invention is to provide means of an accelerator pedal A The an apparatus of the aforedescribed nature engine also includes a conventional electrical which may be readily installed upon the generator G 80 engine of any conventional automotive Interposed between the intake manifold I vehicle and the lower end of the carburettor C is a It is another object of the invention to generally T-shaped fitting, generally designaprovide apparatus of the aforedescribed ted 8, having a vertical leg 10 and a horizontal nature which includes means for re-cycling leg 12 A second T-fitting, generally desig 85 exhaust gas through the intake manifold of nated 14, is interposed between the exhaust the engine during deceleration manifold E and the tail pipe T The horiAnother object is to provide apparatus of zontal leg 16 on the second T-fitting 14 is the aforedescribed nature that is simple in connected to the horizontal leg 12 of the designand rugged of construction whereby fitting 8 by means of a curved pipe 18 This 90 784,975 pipe 18 permits exhaust gas to be re-cycled through the intake manifold I A combustible mixture or fuel shut-off valve 20 is mounted in the upper portion of the vertical leg 10 of the fitting 8 A re-cycling valve 22 is likewise mounted in the horizontal leg 12 of the fitting 14. Referring now to Fig 2, during deceleration of the engine the fuel shut-off valve 20 will be arranged in a closed position while the recycling valve 22 will be opened With this arrangement, during operating conditions of the engine other than deceleration, the carburettor C will be in free communication with the intake manifold I, while the re-cycling valve 22 will prevent the flow of re-cycled exhaust gases into the intake manifold I. During deceleration of the engine, however, the fuel shut-off valve 20

will prevent the flow of fuel from the carburettor C to the intake manifold I At the same time the re-cycling valve 22 will be opened so as to permit exhaust gases to be re-cycled from the exhaust manifold E into the intake manifold I. More particularly, both the fuel shut-off valve 20 and the re-cycling valve 22 may be of the butterfly type Other types of valves, however, may also prove satisfactory The fuel shut-off valve 20 is pivotally supported within the vertical leg 10 of the fitting 8 by means of a horizontal shaft 24 The recycling valve 22 is pivotally supported within the horizontal leg 12 of the fitting 14 by a second horizontal shaft 26 The fuel shut-off valve shaft 24 is keyed to the mid-portion of a generally V-shaped link 28 The re-cycling valve shaft 26 is keyed to one end of a lever 30. The free end of the lever 30 and one leg of the V-shaped link 28 are interconnected by a rigid bar 32 The other end of the V-shaped link 28 is pivotally connected to the plunger 34 of an electric solenoid 36 Both the fuel shut-off valve 20 and the re-cycling valve 22 are normally biased by means of a tension spring 38, the valve 20 towards an open position and the valve 22 towards closed position, said spring 38 having one of its ends secured to the free end of the lever 30 The opposite end of the spring 38 is secured to a bracket 40 which is affixed to the engine. During operative conditions of the engine other than deceleration, the solenoid 36 will not be energized Referring to Fig 2, at such time as the solenoid is energized, however, its plunger 34 will be partially retracted so as to effect clockwise rotation of the V-shaped link 28 and hence of both the fuel shut-off valve 20 and the re-cycling valve 22 Preferably, one terminal 41 of the solenoid 36 will be connected to earth by means of a lead 42 A second lead 44 connects the other terminal 46 of the solenoid to the output terminal 48 of a microswitch 50. This microswitch 50 is fixed to the vehicle's floor board 52 by means of a bracket 54. The input terminal 56 of the microswitch 50 is connected to one side of a circuit breaker 58 by a lead 60 The opposite side of the circuit breaker 58 is connected to one terminal 62 of the generator G The opposite terminal 70 64 of the generator G is connected to earth by a lead 66. The accelerator pedal A is connected to the carburettor C by suitable linkage This linkage includes a horizontally extending rod 68 75 Secured to the rear portion of this rod 68 is a bumper member 70 The upper end of this bumper member 70 includes a set screw 72. The front end of the set screw 72 is engageable with an actuator button 74 which pro 89 trudes from the rear of the microswitch 50 when

the accelerator pedal A is released At such time as the accelerator pedal A is depressed, however, the set screw 72 will be withdrawn from contact with the micro 8 i switch button 74 This condition is represented by Fig 1 Referring now to Fig 2 at such time as the driver's foot pressure is released from the accelerator pedal A the bumper member's set screw 72 will engage 93 the microswitch button 74 so as to move the parts of the microswitch to an i on " position. The circuit breaker 58 should be so adjusted that unless the generator G is producing a predetermined amount of electric current, the 95 circuit between the generator G and the input terminal 56 of the microswitch 50 will be broken With this arrangement, during idling conditions of the engine, the generator G will not produce sufficient current to main 100 tain the circuit between the generator and the input terminal 56 closed During deceleration conditions of the engine, however, the vehicle's wheels will effect rotation of the engine at a speed which causes the generator 105 to produce sufficient current as to maintain the circuit between the generator and the microswitch input terminal 56 closed. In operation, and referring to Fig 1, assuming the vehicle's driver is exerting down 110 ward pressure upon the accelerator pedal A, the bumper member 70 will be retracted from the microswitch button 74 Accordingly no electric current may pass between the generator C and the solenoid 36 The spring 38 will 115 at this time be maintaining the fuel shut-off valve 20 in an open position, and the recycling valve 22 in a closed position Referring now to Fig 2, and assuming that the vehicle is undergoing forward motion, when 120 the driver releases the accelerator pedal A, the bumper member 70 will engage and depress the microswitch button 74 At this time, assuming the generator G is producing sufficient electric current to maintain the 125 circuit breaker 58 in a closed position, current will flow from the generator through the circuit breaker 58, the microswitch 50 and then to the electric solenoid 36 so as to energize the latter The solenoid's plunger 34 130 784,975 will then retract so as to urge the fuel shut-off valve 20 to a closed position and the recycling valve 22 to an open position At this time, the flow of fuel from the carburettor C into the intake manifold I will cease Concurrently, exhaust gases will be free to recycle from the exhaust manifold F into the intake manifold I Under these conditions, the contaminants usually produced by conventional engines during deceleration due to the existence of an excess of fuel within the combustion chambers cannot be produced. Additionally, the intake manifold I will be maintained in a heated and dry condition by the re-cycled exhaust gases Accordingly, when the fuel shut-off valve is again opened, the fuel flowing into the intake manifold will be sufficiently vaporized as to undergo immediate

combustion The introduction of exhaust gas within the intake manifold I below the fuel shut-off valve 20 also prevents the fuel from being drawn around the periphery of the fuel shut-off valve due to the high vacuum created within the intake manifold during deceleration of the engine. It will be apparent that various modifications and changes may be made with respect to the foregoing description, without departing from the scope of the following claims.


* GB784976 (A)

Description: GB784976 (A) ? 1957-10-23

Improvements in or relating to cylinder surfacing tools


PATENT SPECIFICATION 784 976IN Date of Application and filing Complete Specification March 23, 1956. No.9194/56. Application made in United States of America on April 12, 1955. Complete Specification Published Oct 23, 1957. Index at Acceptance: -Class 60, D(IH 12: 1 J: 2 A 10: 2 A 16). International Classification: -B 24 b. COMPLETE SPECIFICATION Improvements in or relating to Cylinder Surfacing Tools We, AMMCO TOOLS, I Nc, a Corporation organised under the laws of the State of Illinois, United States of America, of Main Offices, North Chicago, Illinois, 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:- The present invention relates to improvements in or relating to cylinder surfacing tools also known as cylinder hones, and has to do more particularly with a cylinder surfacing tool of the type embodying a plurality of abrasive elements arranged for expansion and contraction. It is an object of the present invention to provide a rotatable cylinder surfacing tool of simple and inexpensive construction which is both rugged and durable and which permits the abrasive elements to be expanded and contracted over a large range whilst being maintained substantially parallel to each other. According to the present invention there is provided a rotatable cylinder surfacing tool comprising a body, a plurality of surfacing units each including an abrasive element, rigid means pivotally mounting the units on the body in an equally spaced circumferential arrangement about said body for radial expanding and contracting movements and positively maintaining the units parallel with the axis of rotation of the tool in all positions of the units within their range of movement, means for inter-connecting the units for movement in unison, and resilient means yieldingly exerting a force urging the units in an expanding direction which force is substantially constant in all positions of expansion of the units. In order that the invention may be well understood, a preferred embodiment thereof by way of example only will now be described with reference to the accompanying drawings in which:Fig 1 is an elevational view of the cylinder surfacing tool in fully expanded position; Fig 2 is an elevational view of the tool lPrice 3 s 6 d l nearly fully contracted and disposed in a cylinder, as in a surfacing operation; Fig 3 is a bottom view of the tool in expanded condition; Fig 4 is a top view of a portion of the tool; Fig 5 is an elevational view of the body of the tool; Fig 6 is a sectional view taken on line 6-6 of Fig 1; Fig 7 is a longitudinal sectional view of an assembled surfacing unit; Fig 8 is an exploded perspective view of the parts of a surfacing unit; Fig 9 is a diagrammatic illustration of a linkage arrangement utilized in the tool; and Fig 10 is similar to Fig 9 with the linkage in a different position. The tool illustrated in the drawings includes a central supporting element which takes the form of a body 12 having a bore 13 extending longitudinally and axially therethrough The bore 13 is internally threaded at 14 in its upper end for reception of a suitable driving element, as, for example, a flexible shaft (not shown) The body 12 has a plurality of wings 18 extending radially outwardly, corresponding to the number of surfacing units 19 (hereinafter described more in

detail), which is preferably three, and arranged for supporting, or at least partially supporting, the surfacing units Each wing 18 is provided with downwardly extending and laterally opposed ears 20 having aligned apertures 22 a, for receiving a pin 22 for pivotally mounting the surfacing units and forming a pivot axis 221 The ears are connected as by a top element 24, and the space between the ears of each pair opens through to the bore 13 as shown at 25 in the sectional part of the view of Fig 1 The body 12 also has a downwardly extending portion provided with lugs 28 corresponding respectively with the wings 18 but at positions substantially diametrically opposite thereto Each surfacing unit 19 is pivotally mounted on links 32 and 34 constituting parallel linkage for radial swinging movement with the units maintained parallel with the axis of rotation of the tool. Pins 29 in apertures 29 a pivotally mount the Paifce A 5 w. 7 g 4,976 appropriate ends of the links 34 in the lugs 28, forming axes 291 which are disposed in a plane below the plane of the axes 22 '. The link 32 of the linkage for each unit takes the form of a channel and constitutes a rigid main supporting arm 31 in the outer end of which a pivot pin 33 pivotally mounts the surfacing unit, forming a pivot axis 331 The link 32 at its inner end is pivotally mounted on the pin 22, and at this location it is of substantial width having wide spaced points in transverse direction, i e, adjacent opposite ends of the pin 22 Accordingly, the necessary strength and stability is provided for withstanding the substantial stresses imposed on it in the rotation of the tool Extending beyond the inner pivot axis 221 is a short arm or lever 36 formed as an extension of the arm 31 and extending through the opening or slot 25 in the body into the bore 13 The lever 36 is disposed at a predetermined angle relative to the arm 31, namely, in this instance 113 301, for a purpose brought out fully hereinafter The lever 36 is formed as an extension of a corresponding flange of the channel of the arm 31; the three extensions or levers 36 are arranged in overlapping relation tangential to a base circle as shown in Fig 6 whereby they may be extended a substantial distance into the bore, and past the central axis thereof. The link 34 is pivoted at its outer end by means of a pivot pin 37 in an extended end of a rigid arm 39 of the surfacing unit, forming a pivot axis 371 The links 32 and 34 are of course of the same length, and the respective pivot axes on the opposite ends are positioned for maintaining the surfacing units parallel with the axis of rotation. The surfacing units are yieldingly biased outwardly by means of a compression spring surrounding a spring guide 42 which is in the form of a rod reciprocably mounted in the bore 13 of the body A suitable spring retainer 44 is fitted on the lower end of the rod, and the

spring is confined and compressed between the retainer and the under surface of the body. The upper end of the rod has a pair of head members or flanges 46 and 48 guided in the bore 13 and spaced apart for receiving the so inner ends of the extensions 36 on the arms 32. Upon movement of the rod 42 in either direction, the surfacing units are positively swung in or out, but they are biased outwardly by the spring 40 If one or more of the surfacing units are forceably swung inwardly, the remaining units are swung inwardly also, through their mutual positive connection between the head elements 46 and 48 A washer 49 of rubber-like material is interposed between the lower head element 46 and the inturned flange 51 at the lower end of the body, to provide a resilient limit stop for the units in their outward movement. Each surfacing unit 19 includes a carrier 50 which takes the form of a channel having a web 54 with straight transverse end edges 56, and side flanges 58 Substantially midway of the carrier the flanges are provided with apertures 33 a for receiving the pin 33 mentioned above One of the flanges at its lower end has 70 an integral and grid extension thereof forming the arm 39 mentioned above The pivot axes 331 and 371 and the pivotal axes 221 and 291 form a parallelogram of the lines interconnecting them A substantial distance, in radial 75 direction, exists between the axes 33 ' and 371. This distance is equal to and determined by the diametric distance between the axes 22 ' and 29 '. The expanded and collapsed positions of the 80 surfacing tool are shown in Figs 1 and 2 respectively, for which it will be seen that the expansion is unusually great For example, in one specific embodiment, the diameter is about k" in expanded position and about 2 A-" in 85 contracted position In contracted position the links 32 and 34 are entirely within the axial projection of the body and only a small portion of the surfacing units extend radially beyond that projection, it being required that some 90 extension be provided in order to effect a surfacing operation with the body also disposed in the cylinder to the surfaces The wide spacing between the pivot axes 221 and 29 ' is substantially equal to the diameter of the 95 body, since the axes are substantially at the periphery of the body The fact that these axes are within the axial projection of the body enables the links to be contracted or collapsed within that projection The wide spacing 100 between the pivot axes 221 and 291 makes possible a great expansion of the surfacing units while maintaining unusual stability in the device. Mounted on each carrier 50 is an abrasive 105 unit 52 which includes a channel-shaped mounting member 71 and an abrasive element or stone 72

The channel is formed of spring material, such as steel, and includes a web 68 and side flanges 70, and at the ends of the web 110 are extensions 74 bent out of the plane of the web in the direction of the flanges and turned under, forming yieldable gripping elements or hooks The abrasive unit is attached to the carrier by engaging the gripping elements 74 115 over the end edges 56 of the carrier web The flanges 70 engage the flanges 58 of the carrier and prevent displacement from the carrier in the transverse directions The abrasive element or stone 72 is mounted on the outer 120 surface of the mounting channel 71 by suitable means, such as by cement The abrasive unit can be mounted on and detached from the carrier simply by snapping it onto and off of the carrier 125 The links 32 are of maximum width relative to the width of the surfacing units to the end of stabilizing the units against cocking or turning movement about vertical axes, i e, axes parallel with the axis of rotation of the tool 130 PR cos O F 1, where P is force which it is r cos al desired be exerted on the stone by the arm 31, 65 R is the effective length of the arm 31, and r is the effective length of the lever 36 The spring rate is so selected as to produce a force F 2 on the lever 36 when the link is in minimum diameter position which force is computed in 70 PR accordance with the formula F r cos 2 Where, as in the preferred form of the inven-. tion, the lever swings through equal angles a, and a, on opposite sides of the perpendicular plane w, the force F 2 may be computed by 75 F, the formula: F=- We have found that cos 0 where the spring is so stressed and the spring rate is such as to exert a substantially equal force P on the stone in both the minimum diameter position and in the maximum diameter 80 position, it will also exert a substantially equal force on the stone in all positions between the ni-nimum diameter position and the maximum diameter position. Although the preferred angle between the 85 lever 36 and arm 31 is as stated above, namely ' plus one-half of the angle of the swing, the angle may be varied somewhat from the preferred magnitude It may be increased or decreased somewhat and the pressure of the 90 surfacing units on the cylinder wall may nevertheless be maintained constant, by providing appropriate variation in other elements of the structure, as in the expanding spring 40 In the structure above described, the spring is 95 compressed to such an extent that approximately 32 % of the compression of the spring is utilized in expanding the units from minimum diameter position to maximum diameter position As an example of the application of 100 variation of values, the angle mentioned may be increased or decreased approximately 10 % from the magnitude given, i e, be made 103- or 12312 where the angle of swing is 47 and uniform pressure by the surfacing units on the 105 cylinder wall nevertheless be maintained if, in the former case, approximately 19 % of the

compression of the spring is utilized, and in the latter case, approximately 41 5 % of the compression is utilized 110 If, instead of 470, the angle of swing of the arm is 60 , or approximately at the practical maximum indicated above, the desired angle between the arm and lever is 900 plus onehalf the angle of swing, or 120 In this case, 115 the spring is so constructed and arranged, in order that constant pressure will be exerted by the units, that 50 % of its compression would be utilized; similar to the conditions outlined above, in this instance also considerable latitude 120 is permitted in variation of magnitude of the angle selected between the arm and the lever, To this end also the links 34 are arranged so as to be in tension responsive to the intended direction of rotation of the tool These links are offset from the axis of rotation, as they must be because of the spring 40 and spring guide, and are arranged tangentially to a base circle concentric with the axis of rotation. The direction of offset is such that they are disposed in a leading attitude relative to the direction of rotation of the tool which is clockwise as viewed from the top of Fig 1 and counterclockvwiise as viewed in Fig 3 In this direction of rotation the links 34 are in tension and they prevent the surfacing units from cocking or turning as mentioned. The angular relation between each arm 31 and the corresponding lever 36, their location relative to the axis of the tool, and the spring rate and initial loading of the spring 40 are so chosen as to produce substantially uniform surfacing pressure throughout the range of expansion of the tool. For convenience in description, reference is made to the diagrams of Fig 9 which represents a link in its expanded or maximum diameter position, and Fig 10 which represents the link in its contracted or minimum diameter position. The tool is so constructed that each link 32, including the arm 31 and lever 36, swings through an angle ( 0) between minimum diameter and maximum diameter positions, which preferably is approximately 470, but which angle may be any angle within the range of approximately 30 ' and approximately 60 X If the angle O is such that in its maximum diameter position the arm stands at an angle of substantially more than 60 from the tool axis, the tool may bind when moved axially in the cylinder Where the angle O is less than 300 it will ordinarily be found more efficient to employ another type of tool. We have found that it is preferable to construct the link 32 so that the arm 31 and the lever 36 extend at an angle of 90 plus of the angle ( 0) through which the link swings between the minimum and maximum diameter positions and to so mount the link that it moves through equal angles (xl and 22) on either side of a plane W perpendicular to

the axis of the tool In other words, in the preferred construction the angle a, is equal to the angle a Thus in the preferred form of the invention the angle between the arm 31 and the lever 36 is 11342 470 (i e, 900 + as mentioned above). 2 To the end of providing a substantially uniform force (P) on each stone when the link is in both the minimum diameter position and the maximum diameter position, a spring 40 is provided, which is initially stressed to provide a force F, on the lever when the tool is in maximum diameter position which force F, is computed in accordance with the formula 784,976 and a spring having different characteristics is selected For example, if the angle mentioned is 10 greater than the preferred value, or 1300, the spring arrangement is such that approximately 59 2 % of its compression is used, and if it is 100 less, or 1100, approximately 39 % of its compression is used. The surfacing units are positively maintained in parallelism with the axis of rotation of the tool in all positions within their range of movement, through the rigidity of the parallel links. The links 32 and 34 are spaced apart a maximum distance at a position intermediate their range of movement, a condition occurring at a position adjacent the mid-point of the range. This relation enables maximum stability of the tool in fully expanded position consistent with maximum compactness of the links within the axial projection of the body in contracted position. The links are interconnected so that they all move in unison and the tool is more effectively centered in the cylinder being surfaced. Substantially uniform pressure is imposed on the upper and lower ends of the surfacing units This is particularly effective, as compared with previous forms of surfacing tool, where the drive element for the tool must be disposed at an angle to the cylinder More nearly uniform pressure of the surfacing units on the cylinder in such cases is made possible by the present device A limited amount of play is provided between the surfacing units, links and body, to adjust for minor variations in the surface of the cylinder. As will be seen from the foregoing the tool of the present invention has numerous advantages An unusually wide range of movement is provided The widely spaced points of support provide great rigidity The tool is simple and rugged; it is inexpensive, requiring a minimum of machining operations and having a relatively large number of stamped or folded parts. The mutual connection or interlock between the various linkages is an advantage, particularly in view of the fact that the tool is of great diameter in its expanded position It would be impossible for the user to hold the tool in one hand and with the other hand reach completely around the surfacing units in an expanded condition, and on the other

hand it may not be convenient for the user to use both hands for collapsing the surfacing units But because of the interlock mentioned, the user need only grasp one of the surfacing units and move it inwardly and this movement positively swings all of the other units inwardly so that he can easily insert the tool into the cylinder to be worked on.


* GB784977 (A)

Description: GB784977 (A) ? 1957-10-23

Improvements in or relating to the propulsion of water-craft


PATENT SPECIFICATION Date of Application and filing Complete Specification: March 27, 1956. 784,977 No 9497156. &' K '/ Complete Specification Published: Oct23, 1957. Index at acceptance:-Class 114, C 23 B. International Classification:-B 63 h. COMPLETE SPECIFICATION Improvements in or relating to the Propulsion of Water-craft I, ROBERT HERRINGTON NICHOL, a British Subject, of 110, Chertsey Road, Twickenham, Middlesex, do hereby declare the invention, for which I pray that a patent may be granted to me, and the method by which it is to be performed, to be particularly described in and by the following statement:- The present invention relates to the propulsion of water-craft and has for its object to provide a simple and inexpensive propulsion system, which nevertheless operates with a high degree of mechanical

efficiency, a relatively small power being required to develop a reasonably high speed of propulsion. The invention consists in a propulsion system for water-craft comprising a freepassage water-duct extending longitudinally of the craft, with forward inlet and rearward outlet ends below water level, and powerdriven means e g a pump for rearwardly directing a water jet into said water duct to cause emission of a column of water from the rear end of the duct to propel the craft. The water-jet from the pump is injected into the wide end of a conical nozzle member, the narrow end of which is extended by a tube or pipe passing out of the rear end of the vessel below the water level Extending forwardly from the wide end of the nozzle member, on opposite sides of the jet pipe, may be a pair of tubular ducts of relatively large diameter, which terminate in inlet openings on opposite sides of the prow of the vessel, below the waterline These ducts will supply water direct to the nozzle member and they also act as reservoirs for the supply of water to the inlet side of the pump through pipes branched into the ducts at a short distance from their inlet ends and merging together at their other ends adjacent to the pump through a forked or V-shaped tubular junction member connected to the suction pipe of the pump. When the propulsion system is operating, l 1 water will pass into the nozzle member due to the relative motion of the vessel in relation to the surrounding water and its velocity will be increased by the suction produced in the nozzle member by the pump discharge there 50 through, so that a volume of water will be discharged through the jet tube at a relatively high velocity with a considerably greater volume than that supplied by the pump alone. In order that the invention may be clearly 55 understood, and readily carried into practice, it is illustrated, by way of example only, by the accompanying drawings, in which:Fig 1 is a longitudinal section of a boat showing the propulsion system in dia 60 grammatic form; and Fig 2 is a plan view. Referring to the drawings, amidships of the hull 1 is an internal combustion engine 2, which drives through a belt and pulley 65 system 3, the shaft of a centrifugal pump 4, to the discharge end of which is connected a pipe 5 running rearwardly to and terminating within a conical jet nozzle 6, the narrow end of which is -extended by a pipe 7 projecting 70 through the hull 1 beneath the counter 8 of the boat. On each side of the pipe 5 are connected to the wide end of the nozzle 6 the rear ends of a pair of wide ducts 9,9, running along 75 each side of the bottom of the boat to inlet openings on each side of the prow of the boat As shown, these ducts 9,9, may be slightly tapered in the rearward direction so as to be of somewhat greater diameter at 80

their forward ends than at their rearward ends. The suction side of the pump 4 is connected to a V or V-shaped inlet pipe 12, whose two branches are connected to suction pipes 10,10, which also run forwardly along 85 the bottom of the boat to points near the prow of the boat where they branch into the ducts 9,9, just short of their inlet ends. From the foregoing description it will be appreciated that when the engine 2 is running 90 784,977 and operating the pump 4, water is drawn into the pump from the openings at the forward end of the boat through the ducts 9,9, and the suction pipes 10,10, and after having a high velocity impressed on it by the pump, is discharged into the jet nozzle 6 During its passage through jet nozzle 6 additional water is also drawn in by injector action from the water-ducts 9,9, and is discharged through the nozzle pipe 7, together with the water from the pump, so that a relatively large volume of water travelling at a relatively high velocity is discharged rearwardly from the stern of the vessel to serve as a reaction jet, which propels the boat forwardly. The speed of the boat can be controlled by controlling the speed of the engine 2 andlor by a valve controlling the discharge of the pump 4.


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