This invention relates to a transmission for use in connection with a rotary machine.

Rotary machines to which this invention are applicable include rotary steam engines, rotary pumps and, importantly, rotary internal combustions engines, all of the type known as "cat and mouse" machines.

Such rotary machines typically comprise a pair of at least double vaned pistons disposed in a cylinder. The piston vanes are rotatable about the central axis of the cylinder such that chambers are formed between adjacent vanes, one vane from each piston. These pistons are connected by way of a control mechanism in a manner whereby, in addition to a common rotary motion, a relative oscillatory motor is superimposed thereon causing the chamber created between adjacent vanes to cyclically enlarge and reduce.

The present invention is more particularly directed to both power transmission to or from and control of the relative oscillatory motion between the pistons of the rotary machine.

BACKGROUND ART

To obtain an effective benefit from a rotary machine one of two possible operational actions must be used.

The first action involves superimposing on the rotational motion of the first piston a backward and forward rocking cyclical oscillation, relative to the second piston. Examples of rotary machines operating with this action can be found in GB 987989, GB 1028098, GB 1031626, GB 1034023, and GB 1410498.

The second action involves superimposing a backward

and forward rocking cyclical oscillation on the rotational motion of both pistons, phase shifted by 180° with respect to each other so that as the vanes of the first piston rock forward the vanes of the second piston, in relative terms, rock backward to meet them. WO 86/01255, GB 1419043 and GB 2251655 describe rotary machines which operate on this action.

Rotary machines are generally of much simpler construction than their reciprocating counterparts, requiring no valves, connecting rods and the like. However, a problem does arise in how to control the relative motion of the pistons to achieve the desired effect.

In this regard, the desired action is most easily produced in the form of a simple harmonic rocking oscillation derived from the motion of a point rotating about an axis. The principle difficulty in achieving control of the piston relative motion is in turning what is essentially a two dimensional motion, namely, rotation, into a simple backward and forward rocking oscillation.

Many prior art control systems utilise a sliding pin and slot arrangement to produce the simple harmonic oscillation from rotation of the pin on a pinion gear running off a gear mounted on the main shaft of the rotary machine, or some similar arrangement. GB 1034042 and US 4788952 provide examples. Other prior art control systems involve complex systems of cranks, connecting rods and/or cams to derive the oscillation. GB 987989, GB 1028098, GB 1031626, GB 1410478 and WO 86/01255 disclose devices in this regard. All of the above noted prior art devices are deficient in at least one or other of the following ways - they include oscillating masses at relatively large distances from the rotational axis creating complex vibration

patterns resulting in mechanical inefficiencies, they are unable to cope with high speed operation and/or rapid changes in operating speed, they are subject to high mechanical wear, and they are large and unwieldy relative to the other components.

GB 1419043 represents a different approach. The arrangement provided is a step towards a workable solution, but as is shown in the drawings accompanying this patent specification, notably figure 1, the control mechanisms and transmission occupy more space than the rotary machine proper. Moreover, the provision of a single offset pinion wheel (11) at each end of the rotary machine which, as shown in figures 1 and 4 to 7 of the drawings, do not combine to resolve to a zero nett force, produce an unworkable result because of the dynamic imbalance and thus instability.

The transmission and control mechanism device disclosed in GB 2251655 provides a further advance. Notably in this connection, the control mechanism is mounted on the main shaft of the rotary machine and therefore enables a relatively compact unit to be produced. Problems with the mechanism disclosed are that the connecting arms (16) reciprocate, generating an alternating force longitudinally along the main shaft. When the rotary machine operates under the first action noted above significant vibration will occur. This vibration is largely avoided when a seconddevice is mounted on the other side of the machine proper and arranged to operate 180° out of phase. This latter setup causes the rotary machine to operate under the second above noted action. Notwithstanding this, the disclosed device is still undesirable because of the mechanical problems associated with the reciprocating arm system. Further, because of. the need for particular ratios between the bevel gear (12) and bevel gears (11) there is a limit to the magnitude of the

oscillating which can be transferred to the piston vanes, which thus limits the chamber size of the rotary machine. Finally, having a transmission and control mechanism device mounted on either side of the rotary machine provides disadvantages from the standpoint that assembly and maintenance is difficult, and orientation for practical use of the machine is more difficult.

It is an object of the present invention to provide a control mechanism serving also as a transmission, suitable for use with a rotary machine of the "cat and mouse" type, which at least in part overcomes the above noted problems in the prior art.

SUMMARY OF THE INVENTION

In a first broad aspect of this invention there is provided a device serving as a control mechanism and a transmission suitable for use in conjunction with a rotary machine, the device comprising a housing from which extends a first and second shaft, the shafts being coaxial, the device being characterised in that the second shaft terminates in a frame which rotates in company with rotation of the said second shaft, the device further comprising a first and a second annular bevel gear, which first and second annular bevel gears are fixed mounted to the housing, are coaxially aligned with the first and second shafts, and are spaced apart allowing the frame to be freely rotatable therebetween, a first and second pinion gear mounted in the frame, which first and second pinion gears are coaxial, having an axis of rotation offset from the perpendicular to the common axis of the first and second shafts and the first and second annular bevel gears, such that the first pinion gear is in engagement with the first annular bevel gear only and the second pinion gear is in engagement with the second annular bevel gear only, such that when the second

shaft and the frame rotate the first and second pinions are in engagement with their respective annular bevel gear and rotate in the same direction, there being a transfer element mounted in the frame between the pinion gears in engagement with the first shaft to transfer a simple harmonic backward and forward rocking oscillation thereto or therefrom.

The above noted device provides a significant advance on the prior art, in that it can be in full dynamic balance. Further, a device constructed as described can be compact, mechanically very strong and long lasting.

Preferably the transfer element comprises a constant velocity joint mounted on and to the first shaft, the constant velocity joint having a first and second projection, the first projection being eccentrically and rotatably connected to the first pinion gear and the second projection being eccentrically and rotatably connected to the second pinion gear.

Desirably the first and second projections are aligned on a common axis, which common axis passes through the centre of the constant velocity joint.

Conveniently the angle of eccentricity of the common axis of the first and second projections relative to the rotational axis of the first and second pinion gears is between 5° and 80°.

Optionally the angle of eccentricity of the common axis of the first and second projections relative to the rotational axis of the first and second pinion gears is between 30° and 60°.

Alternatively the angle of eccentricity of the common axis of the first and second projections relative to

the rotational axis of the first and second pinion gears is between 5° and 40°, and expendiently between 15° and 25°.

Alternatively the transfer element includes a spherical member fixed mounted to and between the first and second pinion gears, the spherical member including a circular cam track tilted to an angle between the axis of rotation of the first and second pinion gears and the spherical member, and the axis of rotation of the first shaft, the transfer element further including an annular cam follower rotatably mounted in the cam track, the cam follower being pivotably connected to a yoke which in turn is connected to the first shaft.

Desirably the angle of tilt of the cam track relative to the axis of rotation of the spherical member, and thus the first and second pinion gears, is between 10° and 85°. Optionally the angle of tilt is between 30° and 60°. Alternatively the angle of tilt is between 50° and 85°. Expediently the angle of tilt is between 55° and 75°.

In a further embodiment the transfer element can comprise a member pivotably pinned to the first shaft, said member having a first and a second projection, the first projection being eccentrically and rotatably connected to the first pinion gear and the second projection being eccentrically and rotatably connected to the second pinion gear.

Desirably the first and second projections are aligned on a common axis, which common axis passes through the centre of the pivotably pinned member.

Conveniently the angle of eccentricity of the common axis of the first and second projections relative to the rotational axis of the first and second pinion

gears is between 5° and 80°.

Optionally the angle of eccentricity of the common axis of the first and second projections relative to the rotational axis of the first and second pinion gears is between 30° and 60°.

Alternatively the angle of eccentricity of the common axis of the first and second projections relative to the rotational axis of the first and second pinion gears is between 5° and 40°, and expediently between 15° and 25°.

Desirably the annular bevel gears and pinion gears are spiral bevel gears.

Preferably the first and second shafts are concentric, with the second shaft being hollow to receive the first shaft.

Conveniently the device includes a third shaft, coaxial with the first and second shafts, connected to the frame, which third shaft extends from the opposite side of the frame to the second shaft.

Advantageously the number of teeth on the annular bevel gears is a binary multiple of the number of teeth on the pinion gears.

Expediently the annular bevel gears have twice as many teeth as the pinion gears.

In a second broad aspect cf this invention there is provided a rotary machine incorporating a device according to the preceding aspect, the rotary machine being of the "cat and mouse" type.

Preferably the rotary machine includes two pistons .

each having two radially opposed piston vanes.

Conveniently the first shaft of the device according to the first aspect is connected to one piston and the second shaft of the device according to the first aspect is connected to the other piston.

Alternatively the sample hamonic backward and forward rocking oscillation is transferred to or from both pistons, at a 180° phase shift, via a differential arrangement.

Expediently the first shaft of the device according to the first aspect is connected to one piston and the second shaft of the device according to the first aspect terminates in circular yoke radially outwardly from which project a plurality of equispaced freewheeling pinion gears . the freewheeling pinion gears being in engagement with two annular bevel gears coaxially mounted, one said annular bevel gear on each of the two pistons.

An advantage of this later arrangement is that the second action noted above can be achieved using only a single transmission and control mechanism device.

Preferably the rotary machine is a pump. Alternatively the rotary machine is either an internal combustion engine or a steam engine.

BRIEF DESCRIPTION OF THE DRAWINGS

Presently preferred embodiments of the invention will now be described, by way of example only, with reference to the accompanying drawings, in which:

FIGURE 1 illustrates a partially sectioned schematic side elevation of a transmission and control device according to the present invention:

FIGURE 2 illustrates a plan view of the cam follower, yoke and oscillating shaft combination of the device of figure 1;

FIGURE 3 illustrates a side elevation of the spherical cam of the device of figure 1;

FIGURE 4 illustrates a partially sectioned schematic side elevation of an alternative transmission and control device according to the present invention;

FIGURE 5 illustrates an exploded perspective view of the transfer element, first and second shafts, and frame of the device of figure 4 ;

FIGURE 6 illustrates a sectional end elevation of the device of figure 4, sectioned through line XX' ;

FIGURE 7 illustrates the device of figure 4 coupled to the pistons of a schematically shown rotary machine;

FIGURE 8 illustrates the device of figure 4 coupled to the pistons of a schematically shown rotary machine utilising a differential arrangement; and,

FIGURE 9 illustrates an end elevation, pivotably sectioned, of the combination of figure 8 viewed at line ZZ ' .

DESCRIPTION OF THE PREFERRED EMBODIMENTS

In a first embodiment of this invention, as shown in figures 1 to 3 , there is provided a device, as generally indicated at 1, suitable for use with a rotary machine of the "cat and mouse" type as a control mecnanism and transmission.

Broadly, the device 1 comprises a housing 2 from one side of which extends two shafts 3,4. The shafts 3,4

are coaxial and concentric, with the shaft 4 being hollow and rotatably receiving the shaft 3. One end of the shaft 4 terminates at, and is fixed mounted to, a rotatable frame 5.

A first 6 and a second 7 annular bevel gear are fixed mounted to the housing 2, facing each other in coaxial alignment and in coaxial alignment with the shafts 3,4. The gears 6,7 are sufficiently spaced apart to allow the frame 5 to rotate therebetween. A first 8 and a second 9 pinion gear are coaxially mounted in the frame 5 on an axis of rotation offset by an angle μ from the perpendicular to the axis of rotation of the gears 6 and 7. The angular offset ensures that the pinion gear 8 only engages the annular bevel gear 6, and that the pinion gear 9 only engages the annular bevel gear 7. Thus, as the shaft 4 and frame 5 rotate the pinion gears 8,9 rotate in the same direction.

Mounted between the pinion gears 8,9 is a transfer element 10 in engagement with the shaft 3 to transfer a simple harmonic backward and forward rocking oscillation thereto or therefrom.

The transfer element 10 comprises a spherical cam member 11 having a circular cam track 12 tilted at an angle A from the rotational axis of the member 11. Stub shafts 13, 14 extend outwardly from opposite sides of the member 11 and are each fixedly connected to a respective one of the pinion gears 8,9. Thus , the pinion gears 8,9 rotate in accompaniment with the spherical cam member 11.

As shown most clearly in figure 2, an annular cam follower 15 is slidably located in the cam track 12. The cam follower 15 is pivotably mounted about its centre line to a yoke 16 which is formed as an extension of the shaf 3.

When the spherical cam member 11 rotates the tilted circular cam track 12 spins around, with the annular cam follower 15 slidably positioned therein. As the cam follower 15 forces or follows the cam track 12 around angular changes in its orientation in the plane parallel to the shaft 3 are accommodated by relative pivoting between the yoke 16 and follower 15. However, angular changes in orientation in the plane perpendicular to the shaft 3 are resolved into or produced by a simple harmoni backwards and forwards rocking oscillation of the shaft 3.

The device 1 further includes a third shaft 17 fixed mounted to the frame 5 coaxial with but on the opposite side of the housing 2 from the shafts 3 and 4.

Depending on whether the device 1 is used in conjunction with a rotary pump, or a rotary internal combustion engine or steam engine the shaft 17 will serve as the main input or output shaft. Further in this regard, the shaft 3 has a free end which extends beyond the end of the shaft 4 to enable the respective pistons (not shown) cf a rotary machine (not shown) to be connected to the appropriate shaft 3,4.

Turning now to the alternative embodiment of the present invention as illustrated in figures 4 to 6, like components to the first embodiment have been like numbered.

The transfer element 10 comprises a constant velocity joint 20 splined to the end of the shaft 3 interior of the housing 2. Stub axles 21,22 extend from opposite edges of the constant velocity joint 20. Each stub axle 21,22 is eccentrically and rotatably located in a hub 23,24 which in turn is rotatably mounted in the frame 5.

The pinion gear 8 is fixed mounted to a stub axle 25 projecting from the hub 23, coaxially aligned with its rotational axis. Similarly, the pinion gear 9 is fixed mounted to a stub axle 26 projecting from the hub 24 coaxially aligned with its rotational axis.

Due to the eccentric mounting of the stub axles 21,22 relative to their respective hubs 23,24 the constant velocity joint 20 is tilted to an angle B from the common rotational axis of the pinion gears 8,9.

As the interconnected shafts 17 and 4 rotate the pinion gears 8 and 9 also rotate, being pulled by (or pushing) the frame 5. When the pinion gears 8,9 rotate the hubs 23,24 must also be in rotation, and thus the stub axles 21,22 located within the hubs 23,24 transfer a wobbling action to (or from) the constant velocity joint 20.

When the constant velocity joint 20 wobbles motion in the plane parallel to the shaft 3 is taken up (or produced) by the constant velocity joint 20 itself. However, motion perpendicular to the shaft 3 is transferred to the shaft 3 by the constant velocity joint 20 (or vice versa).

Thus, the shaft 3 imparts, or is imparted with two angular components, namely, pure rotation, in common with the shaft 4 , and also a simple harmonic backward and forward rocking oscillation.

It will be apparent that in the described arrangement the constant velocity joint 20 is acting, relative to the shaft 3, purely as a pinned pivot type member. Thus in some situations it may be desirable to simply replace the constant velocity joint 20 with a pivotable member pinned pivotably directly or indirectly to the shaft 3.

However, it is envisaged that for smaller capacity and sized devices 1 the constant velocity joint 20 will prove more advantageous, as force transfer is spread over the full circumference of the shaft 3.

Figures 7 to 9 illustrate two different possible configurations of rotary machine using the device 1.

The rotary machine 30 of figure 7 has the shaft 3 of the device 1 connected to a first piston 3, and the shaft 4 connected to a second piston 32. In this arrangement the rotary machine 30 will operate under the first action described earlier, namely, the second piston 32 will rotate at a particular angular velocity, while the first piston 31 will oscillate above and below that angular velocity due to the superimposed relative simple harmonic forward and backward rocking oscillation controlled by the device 1.

In the second configuration the rotary machine 40 of figures 8 and 9 has the shaft 3 of the device 1 connected to a first piston 41. However, unlike the configuration of figure 7, the shaft 4 is not directly connected to the other piston 42, but instead terminates in a splined section 43 onto which is mounted a yoke 44. Extending radially outwardly from the yoke 44 at equispaced intervals are four stub axles 45. Mounted on each stub axle 45 is a free wheeling pinion gear 46. Each of the pistons 41,42 have an inwardly facing annular bevel gear 47,48, respectively, thereon with which each pinion gear 46 is in engagement.

The nett arrangement produced is a differential, such that while both pistons have a forward angular velocity component V in common, they will also have superimposed thereon an oscillating angular velocity component, 180° out of pnase with respect to each other, controlled bv the device 1.

Revisiting now the earlier discussion, the angles A and B shown in figures 1 and 4, respectively, represent the magnitude of the backward and forward rocking oscillation which can be transferred to one or both of the pistons 31 (41,42) of the rotary machine

30 (40).

In the drawings A is shown as approximately 60° and B is shown as approximately 25°.

It will be apparent that the value of A is equivalent to a value of B calculated as 90°-A. Therefore for figure 1 the value equivalent is 30°.

For the embodiment of figure 1, in the arrangement of figure 7, the magnitude of oscillation of the piston

31 would be a total of 60°. Similarly, for the embodiment of figure 4 in the arrangement of figure 7 the magnitude of oscillation of the piston 31 would be a total of 50°. Where each piston 31,32 has two radially opposed vanes each would need to occupy a sector of approximately 59° for the embodiment of figure 1 and 64° for the embodiment of figure 4 (leaving a gap of 2° between the pistons 31 and 32 and the extremities of the oscillation) .

However, in the arrangement of figures 8 and 9 each one of a two vaned piston would need to occupy a sector of approximately 29° if incorporating the embodiment of figure 1 and 34° if incorporating the embodiment of figure 4.

It may prove advantageous in the arrangement of figure 7 to in fact have four or some other multiple of two vanes per piston. In that case, for example, each vane would need to occupy only half the sector area of a two vane piston.

Clearly if the rotary machine is an internal combustion

engine to obtain the desired two or four stroke operation it may be also necessary to adjust the frequency of the oscillations. This may be achieved by varying the ratio of the number of teeth on the pinion gears 8,9 to the number of teeth on the bevel gears 6,7. However, the ratio should also be a multiple of two.

Where the rotary machine in connection with which the device 1 is used is a pump no problems arise from transmission of torque from the shaft 3 to the shaft

17. However, where the rotary machine is an internal combustion engine or steam engine, so that torque and power is to be into the shaft 3 and out through shaft 17 care must be exercised to ensure that the power stroke occurs at the correct position of the transfer element 10. In this regard, the power stroke should not continue across the mid point of the simple harmonic oscillation, forward or backward, or else the device 1 may be inclined to lock up in some circumstances.

Additional advantages of the present invention will become apparent to those skilled in the art after considering the principles in particular form as discussed and illustrated.

Accordingly, it will be appreciated that changes may be made to the above described embodiments of the invention without departing from the principles taught herein. For example, all of the gears may be spiral bevel generated to improve performance at speed. Further, the piston vanes may be any shape.

Finally, it will be understood that this invention is not limited to the particular embodiments described or illustrated, but is intended to cover all alterations, additions or modifications which are within the scope of the appended claims .