ARRANGEMENTS FOR CONVERTING ROTARY MOTION TO LINEAR MOTION

Abstract: An arrangement for converting rotary motion of a camshaft (1) into linear motion of a reciprocable valve (9) employs a reciprocable cam (2) which is rotatable with the camshaft but is radially displaceable relative to the camshaft which extends through a slot-shaped aperture in the reciprocable cam. The profile of the reciprocable cam is held in engagement with a fixed reference roller (3) and the buchet (7) of valve (a) is held in engagement with output rings (4) in the cam. In the course of rotation of the camshaft, the cam lobe (21) causes radial displacement of the cam on the camshaft with attendant movement of the valve.

Description: -A "Arrangements for converting rotary motion to linear motion". THIS INVENTION relates to arrangements for converting rotary motion to linear motion, such arrangements finding application inter alia in effecting variable valve timing in internal combustion engines. However, the invention can be used in conjunction with any kind of 'cam', or lever operated device. Internal combustion engine design and development has, over the years, indicated that variable valve timing, i.e. the ability to alter the opening, duration of opening, closing and duration of closing, of both the intake and exhaust valves, would achieve considerable advantages in both power output, fuel saving and emission control. However, the continual use, by manufacturers, of 'solid' fixed cams, does not allow for valve control of the kind required to enable the internal combustion engine to reach its full potential. Various attempts have been made to find a method of variable valve control, but the complexities of the systems and their inability to withstand, say, 100,000 miles of average motoring, has, to date, prevented any serious application of any of the ideas postulated. Any variable valve system will, by implication, be more complex, more costly, and more susceptible to wear than the old fashioned 'solid' cam type of device, and the manufacture of such mechanisms will require a change of attitude on the part of the maufacturer, however, it is now quite clear that the internal combustion engine, if it is to continue as the basic prime mover, will have to begin to take advantage of the considerable benefits offered by variable valve timing. Arrangements according to the present invention, when used in internal combustion engines, would, it is assumed, be used in conjunction with some type way into most production motor vehicles and they will, in most cases, have the available capacity to handle the necessary control requirements imposed by this invention, therefore, this aspect of the device is not included in this description. According to the present invention, in one aspect thereof, there is provided an arrangement for converting motion of a first rotatable member into linear motion of a second linearly movable member, in which a follower member is rotatable with the first member whilst being capable of limited linear displacement relative to the first member in a direction transverse to the axis of rotation of the first member, and the follower member is disposed between a reference point and the second member with the follower member held in contact with the second member and a profile of the folfower member held in engagement with the reference point, whereby an rotation of the first member the follower imparts linear movement to the second member. Preferably, the first member extends through an aperture in the follower member which is elongated in the direction transverse to the axis of rotation and the cross-sectional shapes of the first member and follower member are such as to cause the follower member to rotate with the first member, whilst permitting displacement of the follower transversely of the axis of rotation. In accordance with a second embodiment of the invention, there is provided an arrangement • for converting rotary motion of a first rotatable member to linear motion of a search linearly movable member, in which a follower member is rotatable with the first member about its axis of rotation within a hollow cam member having an internal cam profile, the cam profile of the cam member is held in engagement with the follower member and the second member is held in engagement with the cam member, so that on rotation of the first member the cam member imparts a linear motion to the second member. Reciprocating cams as disclosed by the present invention are an innovative version of the old 'solid' cam approach, in that, the cam itself is able to reciprocate upon the camshaft (or Drive-Shaft). This is accom¬ plished by giving the Camshaft a 'squared' cross-section in order that it might drive the Cam, or Cams, but still enable them to slide backwards and forwards. This is achieved by having two parallel machined surfaces, upon which the cams are mounted in free-moving communication. The flat surfaces ensure a rotation of the Cam in qυestion,while the parallel nature of the surfaces ensure a sliding action, by the Cam, across the axis of the Camshaft. In order that the invention may be readily understood, embodiments thereof will now be described, by way of example, with reference to the accompanying drawings, in which: FIGURE I (sheet I) illustrates a first embodiment of the present invention by means of seven drawings A to G, drawing A being a partially sectioned first elevation, while drawings B to G are side elevations of the same arrangement with a camshaft or drive shaft in different angular positions; FIGURE 2 (sheet 2) illustrates a second embodiment of the invention by means of two drawings H and J and corresponding cross-sectional views on lines A, B and C of drawing H; FIGURE 3 (sheet 3) as illustrates a third embodiment of the invention by means of two drawings K and L and corresponding cross-sectional views on lines E and D of drawing K; FIGURE 4 (sheet 4) illustrates a fourth embodiment of the invention by means of drawings M and N and corresponding cross-sectional views on fines F and G, and a fifth embodiment by means of drawing P and corresponding cross-sectional views on lines H to N of drawing P; FIGURE 5 (sheet 5) illustrates by means of drawing Q a typical engine cylinder lead cross-section embodying an arrangement in accordance with the invention; and FIGURE 6 illustrates yet another embodiment of the invention. COMPONENT LISTING Camshaft ( I); Cam (2); Cam Lobe (2L); Reference Roller (3); Circular Output Ring (4); Circular Output Ring (4A);; Guide Plate (5); Guide Plate (5A); Rσlfer (6); Roller (6A); Spring Bucket (7); Valve Guide (8); Poppet Valve (9); Spring Seat (10); NOTE: The valve Return Spring is not included in any of the Drawings. Rotation is indicated as 'R', however, this can, of course, be either direction, but to simplify explanation it has been determined as indicated. AH bearing (sliding) surfaces and or devices are indicated as being 'solid' black areas etc. It will be seen, that the Reference Roller (3) is mounted directly above the vertical centre line of the valve. This Roller (3) is a free-running item and is located in some kind of holder, carrier or fixture. The complexities of cylinder-head design will dictate the type of mounting used, therefore no attempt has been made to show a method of location, other than to indicate that this item, in respect of the devices shown on sheet one, is fixed as indicated. The Reference Roller (3) is in continuous contact with the peripheral outer surface of the Reciprocating Cam (2/2L), however, unlike the more usual camshaft designs of the 'solid' type, the Cam (2/2L) is not in direct contact with the Valve Bucket. NOTE: This description is, it will be appreciated, concerned with Overhead type valves, however the principles will also apply to Side valve, Pushrod, Rocker and any other type of layout etc. As the Cam (2/2L) is not in contact with the Valve Bucket, it is provided with to Circular Output Rings (4 and 4A), these being placed either side of the Cam (2/2L) and shown as being of similar diameter as the Cam (2), however, it should be appreciated that these need not necessarily be of similar diameter to the Main Cam (2). The whole unit (assembly) (4/2/2L/4A) is provided (see Drawing 'B') with an internal pair of parallel surfaces, these matching with the parallel side surfaces machined, or formed, upon the main Camshaft (I). The Cam (2/2L) is held in sprung-loaded contact against the Refer¬ 10 ence Roller, by the applied Spring Tension maintained by the main Valve Return Spring (Not Shown) which would cause the Valve Bucket to press against the Output Ring surfaces, thereby pushing the Cam (2/2L) against the Reference Roller (3). '5 Therefore, if the Camshaft (I) is rotated, the Cam (2/2L) is also rotated, against the Reference Roller (3), and as the Lobe (2L) comes into contact with the Reference Roller (3) it is forced to move away, taking with it, the whole Cam assembly (4/2/2L/4A). As this is restricted in movement by the internal parallel surfaces, it can only move across the axis of the 20 Camshaft (1) thereby causing pressure to be applied to the Valve Bucket (7). The Output Rings (4 and 4A) transmitting the downward pressure to the Valve Bucket Rollers 6 and 6 A). These two Rollers are not essential, and might be replaced by normal " rubbing surfaces. It will be seen, from Drawing 'B', that when the Cam Lobe (2L) is diametrically opposite the Reference Roller and would be, in normal circumstances, in contact with the Valve Bucket (7), it is, in fact, not in 30 contact with the Bucket as clearance has been left between the Bucket (7) and the Lobe (2L). This ensures that the only Cam action generated is that between the Lobe (2A)and the fixed Location Reference Roller (3). The drawing O shows the Cam (2/2L) rotated to the point of 35 activation; i.e; the opening ramp of the Lobe (2L) is about to create eccentric pressure upon the Cam Assembly (4/2/2L/4A), the Valve, mean- while, remaining in the closed position as the Output Rings (4/4A) having maintained only circular contact with the Bucket Rollers (6 and 6 A). In Drawing 'E 1 , however, the continuing rotation of ( I ) has now caused the Cam action to move the Valve away from its closed position 'w' to a partially r ~ open position 'q'. Further rotation as shown by Drawing 'D' brings the Valve to its fully open position V, while continued rotation as indicated by Drawing 'F' shows the closing sequence partially completed with the Valve (9) returning to the closed situation. The point reached indicated 'u'. Drawing 'G' is one which shows the Cam Assembly (4/2/2L/4A) in the same ff » position as that indicated by Drawing 'E 1 , however, the datum through the Cam Lobe (2L) as shown in 'E' as being 'y* - 'y' remains constant while the datum of the parallel surfaces has been moved to 'z' - 'z 1 . This will allow a much greater mechanical advantage to be given to the Sliding Cam during opening movements, as the angle of the parallel surfaces are more in . r alignment with the intended directional travel of the Assembly, however, on the return stroke, there is a greater degree of mechanical disadvantage, but as the loadings are much less, as the Valve Spring in not under compression, this can be tolerated. 20 The idea of moving the axis of the parallel surface datum to accomodate a greater mechanical advantage during the opening sequences; i.e; when the valve spring is under compression, can be applied to any device described In this Specification and to any device contained in the Specifica¬ tion entitled, Annular Cams, Shafts & Followers, as these devices can r benefit from the same angular modification. The basic principles of operation can be seen from Drawing Sheet One, in that the Cam (2/2L) itself slides back and forth (up and down) across the axis of its drive-shaft (I), and in doing so, creates a Cam action to be ~~ applied to the Valve Bucket via the Bucket mounted Rollers (6 and 6A). It may be desirable to include a roller assembly inside the Cam; i.e; between the parallel sliding surfaces. These may be included if necessary. ^ The Shaft variation as included in 'G' may be included in any design herein included if necessary. The term 'Reference Roller'cαn apply to any form of fixed rubbing point or wheel etc. A single Output Ring can be used if required. - It should also be noted, that the bending movement created by the valve reacting on the cam mechansim is mainly absorbed by the fixed roller assembly, however, the torsional requirements will, it is assumed, remain unaltered, however, the 'bending' demands will result in less bearings being I Q required. Drawing Sheet Two:- Contains a further variation of the basic design, in that, provision is made for the Reference Roller to be moveable; i.e; its centre axial datum is able to be moved around a circular orbit concentric to 15 the centre of Shaft ( 1 ). There are many ways of constructing the device in which to enable the Reference Roller (3) to be relocated, and the embodiments contained herein are only included in order to offer examples of some of those ways, 0 however, the method used in Drawing 'H' and its cross-sections A/B/C, gives a realistic idea of one practical way of achieving reference variation. The layout is drawn, in order to represent, a two valve section of a four valve cylinder-head; i.e; one having two inlet and two outlet valves per 5 cylinder; the sizes indicated are for cylinders with a capacity of around 600cc. The layout has been deliberately drawn with the two valves (inlet or exhaust) situated in very close proximity; i.e; their centres shown as being only 1.50". This, it is felt, gives some idea of the abilities of the present invention, in that, despite added complication, it is still able to be packaged 0 within the confines of existing cylinder-head designs. A most important fact, however, if it Is used In cylinder-head designs which feature, say, only two, or three valves per cylinder, it is clear that ample room will be available, and for that reason, throughout this specification, the examples have been drawn to "worst case" parameters. 5 As the two valves shown in Drawing 'H' are identical, an operate in unison, the reference numbers will apply to both. It will be seen, that the Cam unit used for each of the valves is also identical. Whereas in Drawings 'A' and 'B', the Cam assembly used one Cam (2/2L) and two Output Rings (4 and 4A), in Drawing Η' it will be immediately apparent that there Is a reverse of this situation, in that there are now two Cams (2L and LL) operating against each Valve (9). Further¬ more, there is now only one Output Ring (4) per Valve. This requires a double faced Roller (3/3S/3A) being used for each of the Cam Assemblies, however, as in the diameters of the Output Ring and the circular section of each of the Cams is constant,- it would be possible to employ a wide single faced Roller in each case, or, if required, one very wide Roller serving both Cam Assemblies. The Main Camshaft ( I ) passes concentrically through bearing lo¬ cations on the inside of Sleeve-Shaft (I I). This being a fabricated item and being provided with eccentric lobes (17). The lobes (17) holding bearing devices suitable for the Roller units (3/3S/3A). The Eccentrics (17) are fixed to, or part of, Sleeve-Shaft (I I ) and, therefore, any rotational movement applied to Shaft (I I) will cause the Eccentrics (17) to describe a circular movement concentric to the centre datum of Sleeve-Shaft (I I), this being the same centre-line datum as for Shaft (I). It will be seen, from Cross-Section B that the Eccentrically mounted Roller Assemblies will have approximately 125 degrees of rotational travel in either direction, a total of 250 degrees of possible relocation. Assuming that there are several cylinders being served by Shafts (I) and (I I), then any adjustment made to either ■ of the Shafts will effect changes to all of the cylinders served by said shafts, however, if individual Cylinders are to be treated separately, or in various required combinations; i.e; one or more; then the Sleeve-Shaft and/or the Main-Shaft will have to be divided up into simaller units, each with its own drive and/or adjustment means, however, as Drawn, it is assumed that the one Shaft (I) and the one Sleeve-Shaft ( I I) will be serving all of, say the Intake Valves; or all of, say, the Outlet Valves. Therefore, any rotational movement of Shaft ( 1 ) will relate to all the valves served by Shaft ( I) and any rotational movement applied to Sleeve- Shaft ( I I ) will also apply to those same Valves. - Therefore, If we assume (as is done throughout this specification, though not an imposed requirement) that Shaft ( I ) is running at half Crankshaft speed (in the usual manner) and Shaft (1 1 ) is stationary, then the neutral, or mid-adjustment setting for the Roller (3/3S/3A) will always be TDC. (Top Dead Centre). 10 The angle of the parallel sliding surfaces will determine the timing of each Cam Assembly according to the radial positioning of the lobe in question; i.e; in just the same way as cam lobes are situated by degrees of arc, the radial datums of the parallel surfaces will determine the timing ■ _. position of each recipocating Cam Assembly (3/3S/3A). Therefore, if the Sleeve-Shaft ( I I ) is moved away from TDC by any amount, and/or in either direction, then the timing of the Cam actions upon their respective Valves will be either advanced or retarded, thereby 2Q changing the overlap and the amount of Cam effect. Furthermore, if, at the same time as the rotational positioning of the Roller Assemblies is altered, the Main Shaft ( I ) is subjected to a timing alteration (advance or retard) in relation to the Crankshaft, then any combination of Opening/Closing/ Advance/Retard/Over lap or complete close-down; i.e; cy- yc Under disablement; will be possible. This complete ability provides such benefits as cylinder, rather than engine management with throtlling by valve a realistic possibility. In order to appreciate how the Valve in question can be totally 'closed down', it is only necessary to consider the effect of rotating Sleeve-Shaft 30 ( I I ) through 90 degrees away from TDC, and it will be seen that the sliding Cam action will then be completely void, with the Output Ring (or Rings) simply sliding across the Bucket Mounted Rollers (as in Drawings A and B) or Rubbing Surface ( 16) without having any effect whatsoever. The 'Shoe', or -- Rubbing Surface is indicated in Section B as being item ( 16). Item ( 18) is a hole, or aperture, passing through the 'Shoe' in order to save weight. Items (12 and 12A) are the main Shaft Bearing housings. The means of rotating Sleeve-Shaft (I I), in this particular example, is shown as being a Worm (15) and Worm-Wheel (14) combination. It is considered that this method will offer the most sensible way of driving the multi-carrier Sleeve-Shaft assemblies, such as (I I ), as a 'locking' lead angle between the Worm and Worm-Wheel can be used, thereby, enabling any rotational positioning to be 'locked' into place once achieved. Worm ( 15) is provided with a drive-shaft (13) which would provide it with a means of being coupled to any suitable power source; e.g; an electric motor etc. 10 Other means of rotating Sleeve-Shaft (I I) can be included, if required; e.g; a normal spur-gear coupling or pulley etc., however, a means of locking the Sleeve- Shaft Assembly into place must also be included. In Drawing Η', it will be remembered that the two Valves depicted, are both identical in construction and in operation; i.e; both operating in unison, however, it is possible to consider that the two valves, while both sharing similar duties; i.e; inlet or outlet; can be operated independently; i.e; a separate means of adjusting the Roller Assembly to each valve can be 0 contemplated. The basic principles of operation, complete with certain component variation, can be clearly demonstrated by Drawings A: B: C: D: E: F: G: H; -,_ and the benefits of being able to realise the mechanisms concerned in a robust and practical manner is clearly evident; furthermore, the fact that the devices can be fitted into available space, rather than have to completely redesign the whole cylinder-head, offers the manufacturer a new dimension of power, emission control, fuel economy and overall control with only minimal component change. These devices will easily fit inside the 30 present Rocker-Boxes of existing engines etc. Drawing 'J' is a further modification of the basic layout, in that, the Roller (3) is mounted in an eccentric carrier ( 17) which is provided with a __ drive-gear (14) (Worm-Wheel or otherwise), and the Sleeve-Shaft for this particular twin valve combination is confined to the two valves in question; i.e; this means that, in spite of the fact that the two valves shown are operating in unison, their joint operation can be individually controlled. It will also be seen, that a single Cam (2/2L) is responsible for activating the two Output Rings (4 and 4A), however, the size availability for this particular embodiment allows for each ring to drive a separate valve. This type of embodiment allows, therefore, any pair of valves to be controlled separately from any other, and the same advance/retard/Close- Down etc., etc., is provided, together with Main-Shaft (I ) advance/retard etc. This being provided by some suitable Variable Timing Device (See Specifications AI/FMS/004I/VDU/84 and A I /FMS/0042/VTD/84). NOTE: Throughout this Specification, the Output Rings are shown as being completely circular, however, these items may, if required, be provided with other surface profiles; i.e; a cam lobe may be added. This would allow for compound cam operation etc. In Drawing 'J' the Reciprocating assembly was (4/2/2L/4A) and again, this was able to slide (reciprocate) across the axis of Shaft ( I) by way of internal parallel machined surfaces and/or rollers etc. The embodiments contained upon Sheet Two; i.e; Drawings 'H' and 'J', emphasize the considerable scope offered by this invention, in that, it becomes obvious that many variations open to the various components etc., can, If required, be used in conjunction with those indicated or certain of each as included In the specific layout, or layouts, in almost any combi¬ nation thereof. Drawing Sheet Three contains two basic layouts 'K' and 'L' and two cross-section drawings D and E, with E shown in two different positions. The designs indicated by Drawings 'K' and 'L' are concerned with the application of reciprocating techniques to Annular, or Internal Cams (See: Specification A I /FMS/0040/V/84 "ANNULAR CAMS, SHAFTS & FOLLOWERS"), and the resultant layouts offer considerable saving in complexity, while allowing for a very robust realisation of the principles. Drawing 'K' is a cut-away side elevation of a twin valve assembly, with a Main-Shaft (I) passing through the centre of the twin Annular-Cams. As both Cams are identical the reference numbers remain constant for both. Each Annular Cam is provided with an internal 'lobe', or profile (2P) which in these hypothetical examples, is shown as offering an opening, or active, section of some 124 degrees. The whole of the reciprocating element consists of (I 8/2P/2I /22/ 19). (18) = the basic circular Output Ring, with the Annular Cam constructed within its centre area; (2P) = the Cam profile of 124 degrees; (21 and 22) are face extensions which form the side walls for the parallel cross-slides; ( 19) = an end-stop, or travel govenor. This last item, though probably machined from the same piece of material as the rest of the component, could contain a cushion spring etc., if required. It will be seen, that the Main Shaft (I ) is not provided with the parallel (square section) machined surfaces, but is, instead, provided with two small radial extensions (25) in which are housed two Rollers (3). These are made to contact the internal, or Annular surfaces of the Cam Unit (18/2P). Concentrically mounted, in free-running communication around the Main-Shaft ( I) and to either side of the Annular-Cam units (I 8/2P/2 I/22/ I 9), there is a Worm-Wheel (14 and I4A) one serving each Annular Cam Assembly; and attached to, or part of, each Worm-Wheel (or Gear Wheel or Pulley etc) there is a 'square' section plate, the sides of which, are formed, or machined, so as to match with the internal parallel surfaces of the Annular-Cam assembly. Therefore, any rotary movement of the Worm- Wheel/Square Section (14/20) or (I 4A/20) will cause the Annular Cam Assembly to rotate also. Therefore, The Annular Cam Assembly has the ability to reciprocate and rotate. As the outer periphery surface of the Annular-Cam is perfectly circular, It serves as the necessary output ring, contacting the Bucket attached to the Valve/Valve-Spring Assembly. Section D shows a typical end-view cross-section of this hypothetical lαyout (showing one of the twin valves) and Section E shows a cross-section of the Square-Section (20) together with the Annular-Cam face extensions (21/22 and 1 ). The top drawing of E shows the Annular Cam in its mid point (neutral) situation, and the lower drawing of E shows the 90 degree situation, with negative cam effect; i.e; a 'disablement' situation. The indication PS_ is a possible inclusion of a Pressure Spring, Head mounted, in order to restrain the Annular Cam and provide some lateral control. This type of Head mounted springing can be applied to any point of the Output Ring surface in order to prevent the Annular Cam from being subjected to any form of hammer action etc. It will be seen, In these particular layouts, that the parallel section can be extremely robust and that the integrity of the main-shaft remains intact. In Plan-View 'L', it will be seen, that each of the Annular-Cam assemblies has been provided with its own Worm-Drive unit (15 and I5A), this is to allow each Annular-Cam to be adjusted separately, however, If it is required, both may be coupled so as to operate in unison, thereby cutting down the Worm-Drive units to only one. The Spacer unit (23/24/23A) can be fixed to the Main-Shaft (I) or be left as a free-running item. The outer surface Output-Rings can, if required, be provided with their own cam profiles etc. Furthermore, the Main-Shaft can be divided so as to provide a separate drive capability to either of the Roller Housings, thereby allowing for full Advance/Retard capability of both the drive shafts to each cam and each can itself. Sheet Four - contains three basic items; 'M'; 'N* and 'P'; drawing 'M' being a cut-away side elevation of a twin valve assembly, with drawing 'N' beiπg α plan view of that same assembly. Drawing *P' is a separate embodiment, and cross-sections F; G; H; J; K; L; M; and N are also included. fn previous embodiments, the main drive shaft (camshaft) has been shown to pass through the centre of the reciprocating cams, be they annular or otherwise, however, in embodiment 'M'/'N', it will be seen, that a lay- shaft (30) is provided in order that the main torsional drive is carried from valve assembly to valve assembly, without the need to pass through the reciprocating element. rσ If a single valve assembly is examined, it will be seen that there are two Hub units (25 and 26), each provided with two driving gears ( I 4A and 14). The Hub Units are also provided with Face Extensions, into which, are formed, or machined , a slot with parallel internal side faces. The Extensions (27 and 28) are similar to those formed on Annular Cam (18) as shown on Sheet Three. The reciprocating Cam Unit placed in free moving communication between the two driven hub units, comprises Square-Sections (29 and 29A); 0 Output Rings (4 and 4A) one to each Valve Shoe (16); Cam (2) and Cam-Lobe (2L). This whole unit is sectioned (J/K/L/H) and shown as 'solid 1 , however, if required, in order to cut down on weight, the entire unit could be hollow. The Cam (2/2L) is shown to be in contact with a 'fixed' Roller (3) or 5 contact reference point, however Section F indicates that this Roller (3) may be of the adjustable variety, moving through at least 90 degrees in either direction. Square Sections (29/29A) allow reciprocation but also, as in preivous o embodiments, ensure rotation of the unit in question. The Lay-Shaft (30) is provided with spur-gears, in pairs, (31 and 32) shown to be engaged with Hub Drive-Gears (14 and I4A). It will be noted that each Hub Unit could be driven with only one such gear combination if required, however, the Lay-Shaft could be replaced by two such Lay-Shafts, each driving a different Valve assembly, thereby enabling Shaft retard/advance to individual valves or valve combinations. The type of unit described by drawings 'M' and 'N' is very robust and simple to manufacture, furthermore, it allows considerable variation. Drawing *B' is a 'fixed' annular-cam design, In which the annular-cam can be rotated, and the reciprocating unit (29/4/ 1 /3/4A/29A) is driven by two driven hubs as in device 'M'/'N'. The Output-Rings (4 and 4A) are shown to be of similar diameter as that of the Annular Cam Assembly ( 18) - This enables the whole device to be place clear above the Valves themselves without having to be placed between the paired items. This allows for the 1.50" valve centres to be maintained. All of the various embodiments and components and assemblies, shown throughout this Specification, can be used in combination with one another. Drawing 'Q' shows a typical Cylinder-Head cross-section for a 4 valve • (per cylinder) engine. The Cylinder capacity, being approximately 600cc. The type of Reciprocating Cam device shown being similar to that depicted by 'K' and- 'L' on Sheet Three. ('K' being a side elevation and 'L' a Plan View). The side displacement of the Annular (Reciprocating) Cam at full negative set, as shown in the second drawing of Cross-Section E (Sheet Three), would be taken in the opposite direction for the right-hand valve unit. The benefits of the systems herein described, are well known, however, the reciprocating cam techniques are not confined to internal combustion engines, but can apply to many types of pulse timed mechanisms. Throughout this specification, the emphasis has been placed upon the parallel sliding/driving surfaces being machined into the shaft ( 1 ) itself, with the corresponding contact surfaces of the reciprocating unit, on the inside of the Cam or Follower etc., however, Figure 6 (Similar to the kind of arrangement already described by Drawing 'J 1 - Sheet Two) is intended as a bαsic design study which includes α 'cranked' Camshaft arrangement. This is a simple embodiment, in that the main shaft ( I) and the eccentric shaft (2) are indicated as being of a constant I" diameter, this enabling torsional integrity to remain very high indeed. The eccentric housings (3) serve two purposes; i.e; they reinforce the junction of the shaft members (1/2/ 1) and also provide the necessary square section, upon which the Cam Unit is to slide. The Shaft members ( 1 /2/ 1) can be machined from one piece, in this arrangement, as the Cam Unit will easily clear, if fed on from one end, and the Eccentric housings can be fixed in place last of all. This layout, therefore, demonstrates the ease of manufacture offered by these devices, in that, they can be partially, or wholly, fabricated and can be very easily assembled. This 'cranked' Camshaft approach will also provide an alternative means of constructing, or realising, the reciprocating follower devices as included in ANNULAR CAMS, SHAFTS & FOLLOWERS. The torsional loadings on the Camshafts shown throughout these Specifications, will not be as high as those imposed upon normal 'solid' type Camshafts, for as the shaft rotates, the Reciprocating Cam (or Follower) will slide across the axis of the shaft, thereby continually shortening the lever arm length between the tip of the Cam and the centre of the shaft. In normal, solid 'type Camshafts, this cannot happen, with the result that the leverage increases with rotation up to the point of maximum peak, there¬ fore, the torsional requirements for a normal type of Camshaft are necessarily very considerable, however, the fact that teh 'square' sections shown in the various embodiments contained in this specification and those referred to etc., are indicated as having reduced the torsional abilities of the Cam, or drive, shafts; in point of fact, there Is no need for the shaft diameters to be any larger than those indicated as the torsional and bending parameters are very much lower in these inventions.

Claims: r CLAIMS . I. An arrangement for converting motion of a first rotatable member into linear motion of a second linearly movable member, in which a follower member is rotatable with the first member whilst being capable of limited linear displacement relative to the first member in a direction transverse to the axis of rotation of the first member, and the follower member is disposed between a reference point and the second member with the follower member held in contact with the second member and a profile of the follower member held in engagement with the reference point, whereby on rotation of the first member the follower imparts linear movement to the second member. 2. An arrangement according to Claim I , in which the first member extends through an aperture in the follower member which is elongated in the direction transverse to the axis of rotation and the cross-sectional shapes of the first member and follower member are such as to cause the follower member to rotate with the first member, whilst permitting displacement of the follower transversely of the axis of rotation. 3. An arrangement according to claim I or 2, in which the first member is a shaft. 4. An arrangement according to Claim 3, in which the shaft has at least one flat surface extending parallel to the axis of rotation. » 5. An arrangement according to Claim 4, in which the shaft has a pair of fiat surfaces extending parallel to the axis of rotation and to one another. 6. An arrangement according to any one of claims 3 to 5, in which the first member is a camshaft. 7. An arrangement according to Claim 6, in which the second member is σ valve to be actu ted by the camshaft. 8. An arrangement according to Claim 7, in which the follower member has a valve-actuating cam profile and contact means which is normally contacted by an operating portion of the valve. 9. An arrangement according to Claim 8, in which the contact means comprises a pair of contact rings projecting from the follower member on axial Ty opposite sides of the cam profile. 10. An arrangement according to Claim 8 or 9, in which contact between the contact means of the follower member and the valve is established via roller means. 1 1. An arrangement according to any preceding claim, in which the reference point is the point of contact between a fixed reference roller and the follower member. 12. An arrangement according to any preceding claim, wherein the reference point is adjustable relative to the axis of rotation of the first member to adjust the extent of the linear movement of the second member. 13. An arrangement according to any preceding claim in which resilient means acting on the second member holds the second member in engage¬ ment with the follower member and the profile of the follower member in engagement with the reference point. 14. An arrangement for converting rotary motion of a first rotatable member to linear motion of a search linearly movable member, in which a follower member is rotatable with the first member about its axis of rotation within a hollow cam member having an interndl cam profile, the cam profile of the cam member is held in engagement with the follower member and the second member is held in engagement with the cam member, so that on rotation of the first member the cam member imparts a linear motion to the second member. 15. An arrangement according to Claim 14, in which the follower member carries a roller which engages the cam profile of the cam member. 16. An arrangement according to Claim 14 or 15, in which the first member is α camshaft and the second member is a valve to be actuated by the cam shaft. 17. An arrangement according to any one of claims 14 to 16, in which resilient means acting on the second member holds the second member and the cam member in engagement. 18. An arrangement for converting rotary motion of a first rotatable member into linear motion of a second linearly movable member, sub¬ stantially as hereinbefore described with reference to the accompanying drawings. 19. Any novel feature or combination of features herein described.

Inventors: STIDWORTHY FREDERICK MICHAEL, STIDWORTHY, FREDERICK, MICHAEL
Applicants: STIDWORTHY FREDERICK M, STIDWORTHY, FREDERICK, MICHAEL
Application year: 1985
Main classification: F01L1
IPC codes: F01L1, F01L13, F16H25