GB2183732A - Sinusoidal pump/motor - Google Patents

Abstract

A sinusoidal pump/motor which utilises a constant work area of each vane throughout each revolution has curved parallel trackways 3,4 for the vanes 1 and a vane carrier ring 2, providing work chambers around the circumference on both sides of the ring. The vanes are forced to alternatively sweep each chamber's volume content either to pump fluid or to be driven by incoming pressurised fluid. In an alternative embodiment (Figure 2), the vanes extend axially of the rotational axis of the pump/motor and cooperate with a pair of axially-spaced trackways. <IMAGE>

Description

SPECIFICATION Sinusoidal pump/motor This invention relates to a vane pump/motor.

Vane pumpsimotors are in common use. They are not known to be used to produce high pressures as pumps or developing hightorques as motors.

According to the present invention, there is a design of a sinusoidal pump/motor, which employs full 100% work area of all vanes throughout 360 of every revolution and which allows the design to incorporate as manyvanes inthe same plane as desirable.

Specific embodiment of the invention will now be described with reference to accompanying drawings in which: Figure ? shows in linearschematicviewageneral arrangement of vanes and trackways in axial design.

Various arrangements of ports (a,b, and c) and a example of constant blade area exposure (d,e,f and 9).

Figure 2shows a perspective view of a axial design in an "around tube" application.

Figure3shows a cross section of a radial design in a "around tube" application.

Figure4shows a perspective view of a radial design.

Referring to drawings, the principal features of the invention are two, sinusoidally curved, circumferential trackways 3 and 4.

The crests ofthe curves being equispaced around the axis of rotation. The trackways 3 and 4 are orientated relative to each otherso,thatthecrestof one is directly oposite to the trough of the other. This arrangement grants a constant distance between the trackways as they are separated from each other axially (figure 1 and 2) or radially (figure 3 and 4). A carrier ring 2 is positioned in this space. The carrier ring 2 is in contanct with and forms seal at the crest of each trackway. The fluid work chambers arethe internal spaces between the crests.

Although the carrier ring 2 seals againstthe fluid pressure atthetrackway crests, it can rotate or allows rotation of the trackways.

Both trackways are held relative to each other by an outer cylinder7 in axial design or by common base 10 in radial design.Whilethecylinder7 provides the outerwall and the innertube 8the inner wall oftheworkchambers in axial design, in radial design where the sides of the work chambers are created by the trackways 3 and 4, the work chambers are completed byte base 10 andthetopwhich is part of the carrier ring.

The carrier ring houses vanes 1 which are guided so,thatthey reciprocate in direction parallel to the axis of rotation in the axial desing or in perpendicular direction to the rotation axis in radial design as they follow the contours of the trackways.

Afluid seal informed at the contact edges ofthe vanes with the trackway's surface. The contact edges may incorporate a rollerto eliminate wearthrough friction.

The working fluid (liquid or gas) enters and leaves the workchabers via ports 5 and 6. Ports may have various locations figure 1 a, 1 b, 1 c. There may be other combinations but essentially the ports will be placed in close proximity of the peak of each crest or in vicinity of vanes 1, if not to be part of the vanes themselves.

The vanes 1 or the contact surface of the trackways will open and close ports in course ofthe rotational and reciprocative movement.

The movementforpumping is induced byexternal drive of either carrier ring or both trackways. In case of a hydraulic motor, pressurised fluid, guided in via inlet ports 5, will cause rotation dueto unbalanced force acting on the work area of each blade in case of rotating carrier ring ordueto the same force acting on side ofthe crests in case of rotating trackways.

1. Asinusoidal vane pump/motorwhich employs full 1 00%work area of all vanes throughout every revolution and which allows the design to incorporate as manyvanes inthe same plane as desirable.

2. Asinusoidal vane pump which is pumping in positive displacement manner.

3. Asinusoidal vane motor which may be constructed as a ring of almost unlimited size and so producetorquesmatching any requirement (mining, oil drilling, steam engine).

4. Asinusoidalvane pump/motorwhichcan be used for liquids or gases in both capacities.

5. Asinusoidalvane pump/motorwhich can be constructed in axial or radial plane whichever may be more convenient.

6. Asinusoidal vane pump/motor which can be usedforhigh pressure pumping ordrive.

7. A sinusoidal vane pump/motorwhich can be built as a stage unit.

8. Asinusoidalvane motorwhich can utiiisea source of water energy with high pressure/low volume.

**WARNING** end of DESC field may overlap start of CLMS **.

Claims (8)

**WARNING** start of CLMS field may overlap end of DESC **. SPECIFICATION Sinusoidal pump/motor This invention relates to a vane pump/motor. Vane pumpsimotors are in common use. They are not known to be used to produce high pressures as pumps or developing hightorques as motors. According to the present invention, there is a design of a sinusoidal pump/motor, which employs full 100% work area of all vanes throughout 360 of every revolution and which allows the design to incorporate as manyvanes inthe same plane as desirable. Specific embodiment of the invention will now be described with reference to accompanying drawings in which: Figure ? shows in linearschematicviewageneral arrangement of vanes and trackways in axial design. Various arrangements of ports (a,b, and c) and a example of constant blade area exposure (d,e,f and 9). Figure 2shows a perspective view of a axial design in an "around tube" application. Figure3shows a cross section of a radial design in a "around tube" application. Figure4shows a perspective view of a radial design. Referring to drawings, the principal features of the invention are two, sinusoidally curved, circumferential trackways 3 and 4. The crests ofthe curves being equispaced around the axis of rotation. The trackways 3 and 4 are orientated relative to each otherso,thatthecrestof one is directly oposite to the trough of the other. This arrangement grants a constant distance between the trackways as they are separated from each other axially (figure 1 and 2) or radially (figure 3 and 4). A carrier ring 2 is positioned in this space. The carrier ring 2 is in contanct with and forms seal at the crest of each trackway. The fluid work chambers arethe internal spaces between the crests. Although the carrier ring 2 seals againstthe fluid pressure atthetrackway crests, it can rotate or allows rotation of the trackways. Both trackways are held relative to each other by an outer cylinder7 in axial design or by common base 10 in radial design.Whilethecylinder7 provides the outerwall and the innertube 8the inner wall oftheworkchambers in axial design, in radial design where the sides of the work chambers are created by the trackways 3 and 4, the work chambers are completed byte base 10 andthetopwhich is part of the carrier ring. The carrier ring houses vanes 1 which are guided so,thatthey reciprocate in direction parallel to the axis of rotation in the axial desing or in perpendicular direction to the rotation axis in radial design as they follow the contours of the trackways. Afluid seal informed at the contact edges ofthe vanes with the trackway's surface. The contact edges may incorporate a rollerto eliminate wearthrough friction. The working fluid (liquid or gas) enters and leaves the workchabers via ports 5 and 6. Ports may have various locations figure 1 a, 1 b, 1 c. There may be other combinations but essentially the ports will be placed in close proximity of the peak of each crest or in vicinity of vanes 1, if not to be part of the vanes themselves. The vanes 1 or the contact surface of the trackways will open and close ports in course ofthe rotational and reciprocative movement. The movementforpumping is induced byexternal drive of either carrier ring or both trackways. In case of a hydraulic motor, pressurised fluid, guided in via inlet ports 5, will cause rotation dueto unbalanced force acting on the work area of each blade in case of rotating carrier ring ordueto the same force acting on side ofthe crests in case of rotating trackways. CLAIMS

1. Asinusoidal vane pump/motorwhich employs full 1 00%work area of all vanes throughout every revolution and which allows the design to incorporate as manyvanes inthe same plane as desirable.

2. Asinusoidal vane pump which is pumping in positive displacement manner.

3. Asinusoidal vane motor which may be constructed as a ring of almost unlimited size and so producetorquesmatching any requirement (mining, oil drilling, steam engine).

4. Asinusoidalvane pump/motorwhichcan be used for liquids or gases in both capacities.

5. Asinusoidalvane pump/motorwhich can be constructed in axial or radial plane whichever may be more convenient.

6. Asinusoidal vane pump/motor which can be usedforhigh pressure pumping ordrive.

7. A sinusoidal vane pump/motorwhich can be built as a stage unit.

8. Asinusoidalvane motorwhich can utiiisea source of water energy with high pressure/low volume.