GB2197426A - Thrust vector machine - Google Patents

Abstract

A thrust vector machine, for providing a useable 'unidirectional thrust' from a centrifugal force system, comprises two linked and diametrically separated weight masses rotated about a common centre of rotation and connected to rotation means to produce a differential in the radii of rotation of the two weight masses and consequently an eccentric rotation where the maximum eccentricity is always in the same direction to produce centrifugal forces which predominate in one direction, for application in propulsion on land, on or under water or in air or outer space. For practical applications it is necessary to combine a number of such machines. <IMAGE>

Description

SPECIFICATION Thrust vector machine DESCRIPTION This invention relates to a means for producing a useable 'unidirectional thrust' from a centrifugal force system, which has potential for application in propulsive systems applied to movement on land, sea, in the air and space.

BACKGROUND: With only a few exceptions, engineering effort has in general been directed towards the design of rotating machine systems in which all centrifugal forces are carefully counterbalanced about the axis of rotation. This practice has to a large extent resulted in the very considerable centrifugal forces inherent in a rotating system remaining virtually untapped.

To date centrifugal systems have been put to work in limited areas of application ie centrifuges, centrifugal clutches and governors, flywheel systems for energy storage; but only limited attention has been given to the potential as a thrust engine.

BRIEF DESCRIPTION OF THE DRA WINGS AND DIAGRAMS Figure 1 is an isometric view showing the essential embodiment of a THRUST VECTOR MODULE, which is the principle sub-assembly for a THRUST VECTOR MACHINE, the subject of this invention.

Figure 2 is an isometric view of an alternative embodiment for the THRUST VECTOR MODULE shown in Fig. 1.

Figure 3 is a part cross-sectional view showing the essential elements for an embodiment of a means for 'thrust vector' steering.

Figure 4 is a schematic arrangement of THRUST VECTOR MODULES for 'one' embodiment of a THRUST VECTOR MACHINE.

Figure 5 is a schematic arrangement of THRUST VECTOR MODULES for a 'second' embodiment of a THRUST VECTOR MACHINE.

Figure 6 is a line diagram showing the essential elements of a THRUST VECTOR MO DULE in diagramatic form.

Figure 7 is a chart of the basic parameters for calculating the output for a THRUST VEC TOR MODULE.

Figure 8 IS a chart of predicted results for a particular example of THRUST VECTOR MO DULE design.

DESCRIPTION OF THE INVENTION Referring now to the drawings and in particular Fig. 1 the THRUST VECTOR MODULE which is comprised of the following: two concentrated weight masses, depicted as short heavy metal cylinders, the function of which is to provide a source of inertial mass 1; two precision ground metal rods with hardened surfaces, the function of which is to provide rigid connections between each of the two weight masses 2; two bearing blocks, each of which houses two suitably spaced linear bearings and are secured rigidly to the rotation input shaft 3; a high strength radius control link, featuring at each end a precision ground and hardened bearing shaft each of which extends in the opposite direction to the other and perpendicular to the link, its function is to control the radial movement of the weight masses during rotation 4; a roller bearing is fitted to each end of the 'radius control link' to ensure good rotation under load 5; two linear bearings, the function of which is to enable low friction linear movement of the connecting rods during rotation 6; a rotation input shaft, whose function is to provide a connection between a rotation source which could be Internal-combustion engine, Stirling cycle engine, or electric motor and the THRUST VECTOR MODULE 7; the THRUST VECTOR MODULE module mechanism housing, a part cross section to show the fixed pivot point for one end of the 'radius control link' 8; the offset between the fixed pivot at one end of the 'radius control link' and the centre of rotaion, which is the parameter controlling the percentage of thrust force that can be extracted 0.

It is recognised that there are other embodiments that could provide the essentials just described for a THRUST VECTOR MODULE Fig. 1. Such an alternative embodiment is depicted in Fig. 2 where all the essential elements are catered for with a different design approach. The embodiment depicted in Fig. 2 uses the central section of a rimmed flywheel wherein the remaining segments of the rim provide the concentrated weight masses and the inner web the function of the connecting rods. A pattern of grooved rollers 6, the bearing plates for which are securely fastened to the rotation input shaft 7, allows linear movement of the inner edges of a siot in the connecting web. The remaining elements are as described for Fig. 1.

There are likely to be bccasions when it is desirable to have some direct mechanical means of changing the direction of the thrust output. This functional facility requires the ability to rotate the fixed pivot point for the radius control link about the normal centre of THRUST VECTOR MODULE rotatiOn. An embodiment of such a means is depicted in Fig.

3 wherein the fixed pivot point for the 'radius control link' is situated in a rotatable hub 29 and this hub in turn can move the fixed pivot point for one end of the radius control link 4 radially about the normal centre rotation by angular movement of a steering arm 26. The rotatable hub is set in main mechanism housing 21, with bearing rollers 28, between the rim of the hub and the aperture in the housing. A short shaft on the radius control link 4 is mounted in a roller bearing 27, which in turn is set in the hub 29 The resultant force vector output from a THRUST VECTOR MODULE is one whose angle changes with rotation, producing a vector with both forward and side force components. It is therefore necessary to combine an even number of modules in order to counterbalance the unwanted side components in order to produce a true unidirectional thrust vector.The most straightforward combination of THRUST VECTOR MODULES is a side by side configuration, wherein each of the two modules are rotated in phase with each other but in opposite directions. Fig. 4 depicts the embodiment of this THRUST VECTOR MACHINE configuration in schematic form wherein two THRUST VECTOR MODULES 20 are mounted side by side, in a common housing 21 and driven in opposite directions through a pulley and drive belt system 22, by the drive motor and gearhead 23, 24. A more complex configuration involves stacking an even number of THRUST VECTOR MODULES one upon the other and rotating all the modules in phase but with half the number rotating in the opposite direction to the other half of the total number of modules.Fig. 5 depicts an embodiment of this configuration of a THRUST VEC TOR MACHINE in schematic for wherein four THRUST VECTOR MODULES are mounted in a stacked configuration within a common multilevel mechanism housing 21 and two modules are driven in an opposite direction to that of the other two through a drive belt and pulley system 22 by the gearhead, motor and shaft system 23, 24, 25.

OPERA TION The Linkage Diagram Fig. 6 depicts in diagramatic form the concept for a THRUST VECTOR MODULE. The basic elements are two fixed pivot axes (the fixed pivot axis for one end of the radius control link Fig. 1), a moving pivot axis (the pivot point for the other end of the radius control link which is set in one of the two concentrated weight masses Fig. 1), a link connecting one of the fixed pivot axes and the moving pivot (the radius control link Fig. 1), a sliding link which connects the two concentrated weight masses M1,M2 (the connecting rods mounted in linear bearings Fig. 1), a rotation input (the rotation input shaft and bearing block combination Fig.

1). Al, A2 are the effective radii of rotation for the concentrated weight masses M1, M2 at any instantaneous position of the sliding link during rotation.

Under rotation the non-sliding link will force the sliding link to move through the centre of rotation in one direction for one half of a revolution and then reverse the direction for the second half of a revolution. This has the effect of changing the relative radii of rotation for each of the weight masses M1, M2. The position of the fixed pivot axis for the nonsliding link, relative to the axis of rotation for the sliding link ensures that the longest radius of rotation always occurs in the same direction. Since the masses M1, M2 are on a common connection, the angular velocity is the same in each case and the centrifugal force produced by each weight mass is then a function of its radius of rotation. The centrifugal forces produced by each weight mass act in diametrically opposed directions.The usable force is the difference between the two diametrically opposed forces and this difference will always prevail in the same 180 degrees of rotation. The direction in which this usable force prevails is along a line from the axis of rotation in the direction of and through the fixed pivot axis for the non-sliding link. The magnitude of the usable force is a function of the distance between the fixed pivot axis for the non-sliding link and the axis of rotation.

The usable force is the mean of force vectors that are generated throughout 180 degrees of rotation, vectors that have side as well as forward components. To produce a true undirectional thrust force these side components have to be balanced out. As illustrated in Fig. 4 and Fig. 5 and detailed earlier in this description, this counterbalancing can be achieved by rotation of an even number of THRUST VECTOR MODULES in phase with each other, but with half the number rotating in the opposite direction to that of the other half. The most suitable configuration to use for a THRUST VECTOR MACHINE would depend upon the application. For large forward or lifting thrust drive applications, the configuration depicted in Fig. 5 is considered to be more appropriate.For applications requiring a smaller more compact directly steerable thrust unit, such as might be required for small leisure type boats, the configuration depicted in Fig. 6 is more appropriate and is more suited to the steering means already described and depicted in Fig. 3.

Rotation can be produced by any of generally accepted rotating engines. Diesel and petrol engines can provide efficient drive where large thrusts are required and fine control is not a prerequisite. The Stirling cycle engine could provide effective rotation drive input for applications where an air breathing engine could not operate. For applications where steering is effected by producing precise thrust vectors from one or more THRUST VECTOR MACHINES, then thyristor circuit controlled DC motors offer the most appropriate solution.

The equations for centrifugal force can be reduced to the form of a CONSTANT factor multiplied by the WEIGHT of the rotating mass multplied by the RADIUS of rotation multiplied by the SQUARE OF THE REVOLU TIONS PER MINUTE, with reference to Fig. 7.

For A THRUST VECTOR MODULE these basic equations will be: O to 180 degrees FORCE (kg)=.0011 19(M2A2-M1A1) (RPM squared) 180 to 360 degrees FORCE (kg)=.O01 1 19(M1A1-M2) (RPM squared) Fig. 8 illustrates predicted results for a particular set of design parameters. The first graph gives the magnitude of the usable thrust vector force through 90 degrees at 2000 revolutions per minute. The second graph illustrates the magnitude of the average thrust vector force for an increase in revolutions per minute.

Claims (6)

1. A machine means wherein two linked and diametrically separated weight masses are rotated about a common centre of rotation.

Wherein the same weight masses are connected to the rotation means in a manner which produces a differential in the radii of rotation of the same two weight masses.

Wherein the manner in which the radii are caused to differ produces an eccentric rotation where the maximum eccentricity is always in the same direction relative to a datum in any 360 degree rotation. Wherein the purpose of this directed eccentric rotation is to produce resultant centrifugal forces which predominate in one direction for application in propulsion on land, propulsion on or under water, for lift and propulsion in air and outer space. The configuration elements of this claim are illustrated in the Linkage Diagram Fig. 6.

2. A machine means such as that described in claim 1 wherein the centre-point of a linkage between two weight masses is allowed to move through the axis of rotation for the purpose of producing centrifugal forces which predominate in one direction for any 360 degrees of rotation. Two embodiments of such a means are illustrated in Figs. 1 and 2.

3. A machine means such as that described in claim 1, wherein a linkage between a centre-point of one of the weight masses and a point on the machine support structure, which coincides with a point on the line along which the maximum eccentricity occurs, the purpose of such a linkage being to change the differential in the radii of rotation for the two weight masses during rotation. Wherein the purpose of this machine means is to produce resultant centrifugal forces which predominate in one direction for any 360 degrees of rotation. An embodiment of such a means is illustrated in Fig. 1.

4. A machine means wherein the connect point on the machine structure, which coincides with a point on the line along which the maximum eccentricity occurs for the linkage described in claim 3, can be rotated about the centre of rotation of the weight masses for the purpose of changing the direction in which the resulting centrifugal forces produced by the means described in claims 1,2,3 will predominate. An embodiment of such a means is illustrated in Fig. 3.

5. A machine wherein the means described in claims 1,2 3 or 1,2,and 4 are combined to create a functional unit (a THRUST VECTOR MODULE) the purpose of which is to produce resultant centrifugal forces which predominate in one direction for any 360 degree rotation.

6. A machine means wherein an even number of the functional unit (a THRUST VEC TOR MODULE) described in claim 5 are combined to create an application level functional unit (a THRUST VECTOR MACHINE). Wherein half the number of THRUST VECTOR MO DULES in the combination have an internal rotation that is in phase and in an opposite direction to that of the other THRUST VECTOR MODULES in the combination. Wherein the purpose of rotating the internal elements of an equal number of THRUST VECTOR MODULES in phase but in opposite directions is to balance out the side components of the resultant centrifugal forces, generated by the modules in the combination during rotation, to produce a unidirectional force or thrust vector for application in propulsion on land, propulsion on and under water, for lift and propulsion in air and outer space. Two embodiments of such a means are illustrated in schematic form in Figs. 4 and 5.