JPS63502205A - A device that converts rotational motion into linear motion - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] A device that converts rotational motion into linear motion The present invention is particularly applicable to a circuit for implementing variable valve timing in an internal combustion engine. This invention relates to a device that converts rolling motion into linear motion. However, this invention can be applied to any cam or or with a lever actuator.

Over the years, the design and development of internal combustion engines has introduced variable valve timing, i.e. , by the ability to vary the opening, opening and closing duration, and closure duration of both the intake and exhaust valves. has been shown to yield significant benefits in power output, fuel savings and emissions control. are doing. However, with the continued use of fixed cams by manufacturers, the prescribed valve Even with control, the internal combustion engine cannot reach its full potential.

Various attempts have been made to find variable valve control methods, but the complexity of each device and the Due to the fact that it cannot withstand approximately 100゜000 miles as a level running, the idea of requiring it to this day is important applications are being blocked.

Variable valve systems are more complex, expensive, and wear-prone than traditional "solid" cam-type systems. However, it is clear that the manufacturing of such mechanisms requires a change of attitude on the part of the manufacturer. The obvious point is that internal combustion engines, when used as basic prime movers, have variable valve timing. The considerable device according to the invention obtained by are expected to be used with most production vehicles in a manner similar to In this case, the equipment is capable of handling the necessary control conditions imposed by this invention. This point of location is not included in the present invention.

According to one aspect of the invention, the movement of the first rotatable member is transferred to a second linear displacement. In a device that converts a moving member into linear motion, the follower member rotates together with the first member. while it is possible to direct the first member in a direction generally transverse to the axis of rotation of the first member. Linear displacement can be limited, and the follower member holds the follower member in contact with the second member and The profile of the follower member is engaged and held at the reference point and disposed between the reference point and the second member. The rotation of the first member causes the follower to apply linear movement to the second member. Provide a device that allows you to

Preferably, the first member is an elongated follower member generally transverse to the axis of rotation. The cross-sectional shape of the first member and the follower member is such that the follower member passes through the opening of the first part. The shape is such that the follower is displaced in the lateral direction of the rotation axis while rotating together with the material. .

According to a second embodiment of the invention, the linear moving unit searches for rotational movement of the first rotatable member. In a device for converting material into linear motion, the follower member has an inner cam profile. It is rotatable together with the first member about the rotational axis within the hollow cam that is attached to the cam member. The second member is engaged and held with the follower member, and the second member is held engaged with the cam member. The cam member applies linear motion to the second member by rotation of the first member. Provide equipment.

In the reciprocating cam disclosed by the present invention, the cam itself reciprocates on the camshaft (or drive shaft). This is an innovative modification of the conventional "Muripa cam" in that it can move in a double direction. This is achieved by driving one or more cams in cross section and being able to slide back and forth. It will be done. This is achieved by having a parallel machined surface on which the cam is attached in a movable and communicating manner. is achieved. The flat surface ensures the rotation of this cam, while the parallelism of the surface This ensures the sliding action of the cam across the axis of the camshaft.

In order to make the invention easier to understand, examples thereof are given below by way of illustration. This will be explained with reference to the accompanying drawings.

FIG. 1 (Sheet 1) illustrates a first embodiment of the invention by seven drawings A-G, Drawing A is a partial section 1. Drawing 2 (sheet 2) is the two drawings H and J and A of drawing H. 2 illustrates a second embodiment of the invention with corresponding cross-sectional views taken along lines SB and G; Figure 3 (Sheet 3) is divided into two drawings and broken at lines E and D in the drawing. A third embodiment of the invention is illustrated by means of corresponding cross-sectional views, Figure 4 (Sheet 4) is based on drawings M and corresponding cross-sectional views taken along N and F and G lines. The fourth embodiment is based on drawing P and a corresponding cross-sectional view taken along line H to N in drawing P. 5 examples are illustrated, FIG. 5 (sheet 5) shows, according to drawing Q, a typical engine implementing the device according to the invention. exemplify the cylinder lead cross section, and FIG. 6 illustrates another embodiment of the invention.

parts list Cam shaft 1, cam 2, cam lobe 2L, reference roller 3, circular output ring 4, circular output Force ring 4A, guide plate 5, guide plate 5A, roller 6, roller 6A, spring packet 7, Valve guide 8, Poppet valve 9, Spring seat 10° Note: The valve return spring is not shown in any of the drawings. is not included.

Rotation is indicated by R, which of course can be in either direction, but for the sake of simplicity. I made it like an instruction to make it simple.

All supporting (sliding) surfaces and/or devices are shown in black, etc.

The reference roller 3 is mounted directly on the vertical centerline of the valve. This low 53 is A rotatable part that is positioned in some type of holder, carrier, or fixture.

Due to the complexity of the cylinder head configuration, the mounting used requires a certain type, so the seal For the device shown in Figure 1, make sure that this part is secured as shown. Positioning methods other than those shown are shown.

The reference roller 3 is in continuous contact with the outer circumferential surface of the reciprocating cam (2/2L), but it is of a "peel" type. Unlike the normal camshaft configuration, the cam (2/2L) is in direct contact with the valve packet. . l: This explanation relates to overhead valves, but the principle applies to side valves and bush valves. This also applies to pads, lockers, and other devices.

Since the cam (2/2L) does not contact the valve packet, it is equipped with a circular output ring 4.4A. Well, these are placed on either side of the cam (2/2L) and have the same diameter as cam 2. However, these do not necessarily have to have the same diameter as the main cam 2. It is something.

The entire unit (assembly) (4/2/2L/4A) has an inner parallel surface ( (see drawing B), these cams (2/2L) press the valve packet against the output ring surface. τ reference by the applied spring tension maintained by the main valve return spring (not shown) By being held in spring contact with the roller, the cam (2/2L) is moved to the reference roller. Press the button 3.

Therefore, when the camshaft 1 rotates, the cam (2/2L) also rotates against the reference roller 3. When the lobe 2L contacts the reference roller 3, the entire cam assembly (4/2/ 2L/4A) and release it. , whose movement is restricted by the inner parallel plane. pressure is applied to the valve packet 7 by moving it across the axis of the camshaft 1. Add. Output ring 4.4A transmits downward pressure to valve packet roller 6.6A do.

These two rollers are not essential and may be replaced with normal rubbing surfaces.

As shown in drawing B, the cam lobe 2L is directly opposite to the reference roller, which is the normal situation. Therefore, even if the valve packet 7 comes into contact with the valve packet 7, there is virtually no contact between the packet 7 and the lobe 2L. There is a gap, so it does not come into contact with the packet. As a result, only the generated cam action This is ensured between the lobe 2A and the reference roller 3 in a fixed position.

Drawing C shows the cam (2/2 m) rotated to the operating point, i.e. the lobe 2L The opening ramp will create eccentric pressure on the cam assembly (4/2/2L/, 4A) On the other hand, the output ring (4/4A) only makes circular contact with the packet roller 6.6A. remains in the closed position. However, in drawing E, camshaft 1 During continuous rotation, the cam action moves the valve away from its closed position W to its partially open position 9. are doing. Further rotation as shown in the drawing will take the valve to its fully open position V, In the continuous rotation shown in drawing F, the valve closing seat where the return of the valve 9 to the closed position is partially completed. Indicates kens. The farthest point is indicated by V. Drawing G is at the same position as shown in drawing E. This is a drawing showing the cam assembly (4/2/2L/4A), with E as y-y. The reference line for the cam lobe 2L shown remains constant, and the reference line for the parallel plane is z-z − is moving. This allows the angle of the parallel planes to further align with the desired direction of the assembly. Since the directional movement is in line with the sliding cam during the opening movement, there is a considerable mechanical benefit to the sliding cam. However, on the return stroke, the load is considerably less, although there are considerable mechanical drawbacks. This is also acceptable since the valve spring is not compressed.

The idea of moving the parallel plane reference axis to obtain a large mechanical advantage during the opening sequence is to When the spring is compressed, the device described herein also includes an annular cam, Applicable to devices included in the specification under the names of shafts and followers, i.e. This is because the device benefits from the same tilt deformation.

The basic operating principle is shown in drawing sheet 1. In this way, a cam action is created on the valve packet via the packet mounting roller 6.6A. Melt.

It is desirable to insert a roller assembly inside the cam, that is, between the parallel sliding surfaces. Yes. These can be included if necessary.

If necessary, the axis type included in G can be included in the configuration described here.

The reference roller can be applied to any type of constant rubbing point or wheel or the like.

A single output ring can be used if required.

It should also be noted that the bending movement caused by the valve responding to the cam mechanism is primarily caused by the fixed roller arm. is absorbed by the assembly, the torsion condition remains unchanged, but the bending demands Less support is required.

Drawing sheet 2 contains another variant of the basic configuration, in which the reference roller is movably mounted. That is, its central axial reference plane is centered on a circular orbit eccentric to the center of axis 1. Can be moved.

There are many ways to configure the device, and these are just a few examples of the reference roller 3. However, the method used for drawing H and its cross sections A/B/C is one way to achieve the reference deformation. Demonstrates a realistic idea of practical methods.

The arrangement shown shows a two-valve section of a four-valve cylinder head, i.e. two valves per cylinder. A system with one inlet and two outlet valves, the size shown has a capacity of approximately 600 CG. This is for Linda. Note that the arrangement has two valves (intake or exhaust) located close together. They are intentionally shown, ie, their centers are shown as only 1.50''.

This gives some idea of the capabilities of the present invention, and despite the additional complexity However, it can still be incorporated into existing cylinder head configurations.　Also important The thing is that cylinder heads with only 2 or 3 valves per cylinder, for example It is clear that it will give you enough space if used for configuration, so this In the specification, "worst case" parameters are given in the examples.

The two valves shown in Drawing H are identical and therefore operate in unison and the reference numbers apply to both valves. use

The cam units used in each of these valves are also the same.

On the other hand, in drawings A and B, the cam assembly consists of one cam (2/2L) and two Output ring 4.4A is used, and it is clear at first glance that this situation is reversed in drawing H. There are two cams (2L, LL) that operate on the multi-valve 9. Furthermore, There is only one output ring 4 per valve. For this reason, each cam assembly uses A double-sided roller (3/3S/3A) is required, but the diameter of the output ring In each case, the circular cross-section of each cam is constant, and in each case a wide single-sided roller is used, if necessary. , one very wide roller can be used and both cam assemblies can be saved.

The main camshaft 1 concentrically passes through the inner bearing position of the sleeve shaft 11. This is a group It is a vertical part and includes an eccentric lobe 17. Loaf 17 is a roller unit (3 Holds a bearing device suitable for /3S/3A>.

Since the eccentric part 17 is fixed to the sleeve shaft 11 or a part thereof, it is not added to the shaft 11. The resulting rotational movement causes the eccentric portion 17 to form a circle concentric with the center reference line of the sleeve shaft 11. Draw a shape shift, which is the same centerline reference line as axis 1.

As shown in cross-sectional view 8, the eccentric mounting means that the roller assembly is approximately 12 mm in either direction. Performs a rotational movement of 5 degrees, a total of 250 degrees of expected relocation.

If several cylinders are actuated by axes 1 and 11, then one of the two wheels The adjustment made changes all the cylinders actuated by said shaft, but individually The rings may be processed separately or in various predetermined combinations, i.e. in one or more , the sleeve shaft and/or the main shaft each have their own drive and/or or) must be divided into smaller units with adjustment means, but the illustrated Thus, one shaft 1 and one sleeve shaft 11 are for example all intake valves, or e.g. For example, all outlet valves would be activated.

Therefore, the rotational movement of shaft 1 is related to all valves actuated by shaft 1; Rotational movement applied to valve shaft 11 also applies to those same valves.

Therefore (as is done throughout this specification, although not an imposed condition) axis 1 is If it is rotating at half crankshaft speed (in the usual way) and shaft 11 is fixed, then For example, the neutral or intermediate setting of the roller (3/3S/3A) is always at TDC (point above). Become.

Each cam assembly by radial positioning of the lobe by the angle of the parallel sliding surface. determine the timing of the 3/33/3 each reciprocating cam assembly (3/33/3 Therefore, the timing position of A> is set so that the sleeve shaft 11 is moved by a predetermined amount and/or As you move in either direction away from top dead center, a cam action is applied to each valve. When the timing of the cam is advanced or retarded, the cam effect overlaps and changes life. I can do it. Furthermore, at the same time as the rotational positioning of the roller assembly is changed, When main shaft 1 receives a timing change (advance or delay) from the crankshaft, it opens. Any combination of open/close/advance/delay/overlap or complete stop i.e. Linda becomes more likely to become incapacitated. With this complete capability, including valve throttling, Rather than engine management, it gives a realistic possibility of benefiting cylinders, etc. .

In order to evaluate how to completely seal the valve, rotate the sleeve shaft 11 by 90 degrees. All you need to do is consider the effect of moving it away from top dead center, and then the sliding cam action will be completed. completely gone, and one output ring (or rings) is left with no effect. (as in drawings A and B) across the packet mounting roller or rubbing surface 16. to slide. The shoe or rubbing surface is shown in section B by part 16.

Part 18 is a hole or opening that passes through the shoe to save weight. Parts 12.1 2A is the main shaft bearing housing.

In this particular embodiment, the means for rotating the sleeve shaft 11 includes a worm 15 and a worm. shown as a combination of arm wheels 14. This method is suitable for 11th grade calf This is a very rational way to drive the sleeve shaft assembly, and the worm and A fixed lead angle between the ohm wheels is used to fix the rotational position. Once obtained, the predetermined position can be set.

The worm 15 is provided with means for coupling to a suitable power source, e.g. an electric motor, etc. A drive shaft 13 is provided.

If necessary, other means for rotating the sleeve shaft 11, such as a normal spur gear coupling, can be used. locks the sleeve shaft assembly in place. It must also include the means.

In drawing H, the two valves shown are both identical in construction and operation, i.e. they are harmonized together. It will be recalled that two valves, both bearing similar duty, , that is, the inlet or outlet valve can be operated independently, i.e. Separate means of adjusting the controller assembly can be envisaged.

The basic principle of operation with complete deformation of parts is shown in drawings A, B, C, D, E, F, and G. , H and the benefits of realizing a robust mechanism, and the actual method is clear. Furthermore, the equipment requires a complete redesign of the entire cylinder head. Due to the fact that it fits into the available space rather than having to , provides manufacturers with new power levels, emissions controls, and fuel savings with minimal component replacement. Achieve economic efficiency and overall control. These devices are installed on existing engine lockers, etc. - Fits easily inside the box.

Drawing J is another variant of the basic arrangement, where the row 53 is the drive gear 14 (worm wheel etc.), and this The sleeve shaft for a particular double valve combination is confined to the two valves, i.e. Although the two valves shown operate in unison, their integrated operation is controlled individually. means to be

Also, two output rings 4.4A are operated by a single cam (2/2L), Due to the size obtained in this particular embodiment, a separate valve is actuated for each ring. .

This type of embodiment therefore allows any pair of valves to be controlled separately from each other and has the same forward movement. /delay/stop etc. are obtained together with advance/delay etc. of the main shaft 1. This is an appropriate variable obtained by a timing device (specification A1/F reference: In this specification, the output Although the ring is shown as a perfect circle, these parts may be replaced with other representations if desired. surface profile, i.e. cam lobes can be added. Ru. This results in a compound cam operation.

In drawing J, the reciprocating assembly is (4/2/2L/4A> and the inside Slide (reciprocating) across the axis of shaft 1 by parallel machined surfaces and/or rollers, etc. verb) can.

The embodiments contained in Sheet 2, drawings H and J, demonstrate the significant advantages provided by this invention. The range is emphasized and the many variations open to various parts are illustrated as necessary. along with the name of the parts included in a specific arrangement or most combinations thereof. It is clear that it can be used for

Drawing sheet 3 contains two basic configurations and L and two cross sections and E, which Here E is shown in two different positions.

The configuration shown in the drawings and at L relates to the application of reciprocating technology to annular or internal cams. See specification A1/FMS10040/V/84 “Annular cam, shaft and follower” ), the resulting arrangement reduces the complexity considerably, while making the principle very robust. Realized.

The drawing shows a cutaway side view of the twin valve assembly with the main shaft 1 passing through the center of the twin annular cam. It is. Since both cams are the same, a constant code is used for both cams.

Each annular cam, in a hypothetical embodiment, has an aperture or 124 degree active portion. It has an inner lobe or profile 2P shown to provide. Reciprocating motion The entire element consists of (18/2P/21/22/19). 18 is within the central area It is a basic circular output ring with an annular cam configured, and 2P is a 124 degree cam pro 21 and 22 are surface extensions forming the side walls of the parallel Ross slide. ・S, 19 is an end stop or a moving governor. This last part is Probably made of the same material as the rest of the component, but with a cushion if necessary. It may also contain

The main shaft 1 has two rows 53 accommodated instead of having parallel (square cross-section) machined surfaces. It has two small radial extensions 25. These are cam units (1B/2P ) or in contact with the annular surface.

A worm wheel 14.14A serving as each annular cam assembly is centered around the main shaft 1. An annular cam unit (18/2P/ 21/22/19’) and each warm home. fixed to the square section plate on or part of the eel (or gear wheel or bridge etc.) and the side surface of the plate is formed to coincide with the inner parallel surface of the annular cam assembly. or processed. Therefore, worm wheel/square surface (14/20 ) or (14A/20) rotational movement to rotate the annular cam assembly.

Therefore, the annular cam assembly has the ability to reciprocate and rotate.

The outer circumferential surface of the annular cam is completely circular so that it is secured to the valve/valve spring assembly. Acts as the required output ring touching the packet.

The cross section is a typical end cross section of the hypothetical configuration (showing one of the twin valves), and section E is an annular cross section. Drawing that is a cross-sectional view of the rectangular section 20 with the cam surface extensions (21/22/ and 19) The upper part of drawing E shows the annular cam in the midpoint (neutral) position, and the lower part of drawing E shows the negative cam effect. 90 degree position, that is, the disabled position. PS restrains the annular cam and horizontally A head-mounted pressure spring for directional control. This type of head installation The spring is attached to the output ring to prevent the annular cam from being subjected to any hammer action. Acts on any part of the surface.

In these particular arrangements, the parallel parts are very strong and the integrity of the main axis is It remains as it is.

In plan view, each annular cam assembly has its own worm drive unit 15. ．． 15A, each annular cam is adjusted separately, but if necessary, Worm drive unit by being coupled so that both work in harmony Reduce to just one.

The spacer unit (23/24/23A> is fixed to the main shaft 1 or is movable. Leave it there.

If necessary, the external output rings can have their own cam profiles, etc. Wear.

Furthermore, the spindle may provide separate drive to either roller housing. By dividing the drive shaft into two, each cam is given full advance/retard performance of both drive shafts. .

Drawing M is a cutaway side view of the water valve assembly, and Drawing N is a plan view of the same assembly.

Drawing P is another example in which cross sections F, G, HSJ, also include L, M and N. ing.

In the above embodiment, the main drive shaft (camshaft) passes through the center of the annular or other reciprocating cam. However, in Example M/N, a secondary shaft 3o is provided to drive the main torsional drive. from valve assembly to valve assembly without passing through reciprocating elements. It has become.

Looking at a single valve assembly, there are two valves each comprising two drive gears 14A, 14. It has hub units 25 and 26. These hub units also have parallel inner surfaces The surface extension has a slot formed or machined therein. Extension part 27. 28 is similar to the extension formed in the annular cam 18 shown in seat 3.

The reciprocating cam unit is provided in a movable communication manner between two driven hub units. , square cross section 29.29A, one output ring for each valve chute 16 4.4A.

It includes a cam 2 and a cam lobe 2L. This entire unit is divided into sections (J/ /L/)-1> is shown as peeled, but if necessary, the unit may be removed to reduce weight. The whole part may be hollow. .

The cam (2/2L) is shown in contact with fixed roller 3 or contact reference point. However, cross-sectional view F shows that this roller 3 moves at least 90 degrees in either direction. It is shown that it can be adjusted in various ways.

Although the rectangular cross section (29/29A) is reciprocated, as in the previous embodiment, this unit The rotation of the shaft is ensured.

The countershaft 30 has a pair (31,3 2) is equipped with a spur gear. In addition, each hub unit has such a gear combination 1 If required, the countershafts can each drive a different valve assembly. allows for key axis retardation/advancement of individual valves or valve combinations by Two such subaxes may be substituted.

Units of the type shown in drawings M and N are extremely robust, simple to manufacture and Furthermore, significant variations are possible.

Drawing B shows that the annular cam can rotate and the reciprocating unit 1- (29/4/1/3/4 A/29△) is driven by two driven hubs like a device with M/N, fixed An annular cam configuration is shown. Output ring 4.4A is annular force.

It is shown to have the same diameter as that of the system assembly 1B. With this, The entire assembly can be placed remotely above the valve itself without being placed between paired parts.

This maintains a 1.5" valve center.

All of the various embodiments, parts and assemblies shown in this specification are interconnected. Can be used together.

Drawing Q shows a cross-section of a typical cylinder head of a four-valve (per cylinder) engine. . The capacity of the cylinder is approximately 600cc. The reciprocating cam device of the type shown is To 3,! :Same as the device shown with L. (K is a side view, L is a top view ).

As shown in the second drawing of cross section E (sheet 3), the annular (reciprocating) shape in the full-width set ) The lateral displacement of the cam is carried out in the opposite direction for the right-hand valve unit.

The benefits of the device described here are well known and the reciprocating cam technology is limited to internal use. It can be applied to many types of pulse photography.

In this specification, a reciprocating unit-compatible contact surface and a sliding surface are machined on the shaft 1 itself. (similar to the type already described in Sheet 20 Drawing J) ゛ Figure 6 shows a plan for research on the basic configuration including a camshaft device with a crank.

This is a simple example, and the main shaft 1 and eccentric shaft 2 are shown as constant 1# diameters. This allows for extremely high torsional integrity. Eccentric housing Glue 3 has two purposes: to reinforce the joint of the shaft members (1/2/1), and The goal is to obtain the required square portion on which the cam unit slides.

This arrangement allows the cam unit to pass easily when fed from one end, so the shaft member (1/2/1) can be processed in one piece, and the eccentric housing is finally placed in the specified position. Fixed. Therefore, this arrangement facilitates manufacturing using these devices. , it can be manufactured in parts or in whole and is very easy to assemble. Wear.

This cranked camshaft proposal also includes annular cams, shafts and followers. provides another means of configuring or realizing a reciprocating follower device.

The torsional load on the camshaft shown in these Mei 18 is the same as that of a normal bare-type camshaft. The load imposed on the reciprocating cam (or follower) is not large as the shaft rotates. A) slides across the axis to align the lever between the cam tip and the center of the shaft. This is because the length of the beam is continuously shortened. With a normal exposed camshaft, Since the leverage increases with rotation up to the maximum peak point, Although the torsion conditions of a normal type camshaft are necessarily extremely important, .

The rectangular cross-sections shown in the various embodiments contained in and related parts may be is shown to reduce the torsional capacity of the drive shaft, and this fact suggests that the shaft diameter It is not necessary to make the diameter larger than the diameter shown, and in these inventions, the bending parameters are Extremely small.

ANNEX To τ knee E! NTERIJATIONAL SE entry CHR Three PORTs ON

Claims (1)

[Claims] 1. a device for converting motion of a first rotatable member into linear motion of a second linearly moving member; and the follower member is rotatable with the first member while being aligned with the axis of rotation of the first member. The linear displacement relative to the first member in the lateral direction can be limited, and the follower member is The follower member is held in contact with the second member and the profile of the follower member is related to the reference point. By being arranged between the reference point and the second member while maintaining the rotation of the first member, A device in which a follower imparts linear movement to a second member. 2. The first member has an elongated opening in the follower member transversely to the axis of rotation. The cross-sectional shape of the first member and the follower member extends through the follower member together with the first member. Claims include a shape in which the follower is displaced in the lateral direction of the rotational axis while being rotated. Apparatus according to Box 1. 3. 3. A device according to claim 1 or 2, wherein the first member is a shaft. 4. Claims: The shaft has at least one flat surface extending parallel to the axis of rotation. Device according to 3. 5. According to claim 4, the shaft has a pair of flat surfaces extending parallel to each other to the axis of rotation. device. 6. 6. A device according to any of claims 3 to 5, wherein the first member is a camshaft. 7. 7. A device according to claim 6, wherein the second member is a camshaft operated valve. 8'. The follower member is in contact with the valve actuating cam profile, which normally comes into contact with the actuating part of the valve. 8. Device according to claim 7, comprising contact means. 9. The contact means includes a pair of contacts extending from the follower member on both sides of the cam profile in the axial direction. 9. Device according to claim 8, comprising a touch ring. 10. The contact between the contact means of the follower member and the valve may be formed via roller means. Apparatus according to requirement range 8 or 9. 11. The reference point is a contact point between the fixed reference roller and the follower member. Equipment by either. 12. The reference point is the axis of rotation of the first member in order to adjust the limits of linear movement of the second member. A device according to any of the preceding claims, which is adjustable to. 13. Resilient means acting on the second member retains the second member in engagement with the follower member and According to any of the above claims, the mouth fill of the follower member is engaged and held with the reference point. Device. 14. converting the rotational motion of the first rotatable member into linear motion of the search linearly moving member; In the device, the follower member rotates within a hollow cam having an inner cam profile and an axis of rotation. The cam profile of the cam member is rotatable with the first member about the follower. The second member is held in engagement with the cam member, and the second member is held in engagement with the cam member so as to rotate the first member. A device in which the cam member imparts linear motion to the second member. 15. The follower member supports a roller that engages a cam profile of the cam member. Apparatus according to claim 14. 16. The first member is a camshaft and the second member is a valve operated by the camshaft. Apparatus according to the desired scope 14 or 15. 17. The elastic means acting on the second member engages and holds the second member and the cam member. Apparatus according to any of ranges 14 to 16. 18. The rotational movement of the first rotating member substantially as described above with reference to the accompanying drawings is A device that converts a linearly movable member into linear motion. 19. Novel features or combinations of features described herein.