Rotary drive device

Abstract

Disclosed is a rotary drive device comprising a housing in which a first rotor and a second rotor are disposed, the first rotor being rotatable about a first axis and having a rotor element protruding radially therefrom, the second rotor being rotatable in an opposite direction to the first rotor about a second axis parallel to the first axis, the second rotor having a recess capable of receiving the rotor element, the first rotor, the second rotor and the housing defining a chamber around the first rotor through which the rotor element passes, the chamber having an inlet and an outlet through which a fluid can enter and exit the chamber.

Description

Technical Field

[0001] The present invention relates to a rotary drive device suitable as a fluid pump including a turbine and a ventilator pump. Further, the rotary drive device of the present invention is also suitable as a rotary engine.

Background Art

[0002] In principle, a rotary drive device transmits energy between a drive shaft and a moving fluid or a combustion fluid. Many configurations for rotary drive devices are known, and there are a wide range of applications for them.

[0003] In a turbine, the moving fluid gives energy to the drive shaft. Current turbines utilize blades that receive pressure from a liquid or a gas to rotate the turbine. Such a concept does not utilize all of the energy available in the gas or fluid because a significant proportion of the gas or fluid passes through the turbine blades without contacting the blades or transferring potential energy to the blades.

[0004] In a rotary engine, energy is transferred from the combustion fluid to the drive shaft. A known combustion engine that does not require a piston is the rotary engine. Finding a replacement for a piston-driven engine is particularly advantageous because a considerable amount of energy is lost in each chamber of the piston when moving the piston up and down. The actual efficiency of a conventional "four-stroke" engine is low compared to the potential energy provided by the fuel. The known concept of a rotary engine attempts to replace the need for a piston chamber with a machine that relies on centripetal energy. Previously, rotary engines and pumps had complex configurations and difficult assembly methods, making them expensive to manufacture. Furthermore, existing rotary engine configurations have complex mechanisms involving lateral movement in addition to rotational movement. The overall result is a loss of power and efficiency. While known rotary engines are useful alternatives to conventional four-stroke engines, they are not viable and complete replacements.

[0005] The object of the present invention is to manufacture a rotary drive device that provides the public with more efficient use of energy, smoother operation, or at least a useful alternative. [Overview of the Initiative]

[0006] In a first aspect of the present invention, a rotary drive device is provided, comprising a housing in which a first rotor and a second rotor are disposed, the first rotor being rotatable about a first axis and having rotor elements projecting radially therefrom, the second rotor being rotatable in the opposite direction to the first rotor about a second axis parallel to the first axis, the second rotor having recesses capable of receiving rotor elements, the first rotor, the second rotor and the housing defining a chamber around the first rotor through which the rotor elements pass, the chamber having an inlet and an outlet through which fluid can enter and exit the chamber.

[0007] In some embodiments, the first rotor and the second rotor can maintain a seal engagement during rotation.

[0008] In some embodiments, the rotor element does not come into contact with the floor of the recess during rotation.

[0009] Optionally, the apparatus further comprises sealing means between the first rotor, the second rotor, and the housing.

[0010] Optionally, the apparatus further comprises sealing means capable of forming a seal between the first rotor and the housing and / or the second rotor.

[0011] Optionally, the apparatus further provides the rotor element with sealing means capable of forming a seal between the rotor element and the housing and / or a second rotor.

[0012] Optionally, the device further comprises shoulders adjacent to the rotor elements and protruding from the first rotor, which at least partially close the inlet and / or outlet during a portion of the cycle of the first rotor.

[0013] Optionally, the leading and / or rear surfaces of the rotor element or shoulder portion may be shaped to reduce or mitigate fluid drag.

[0014] In a preferred embodiment, the device is configured to introduce pressurized fluid through an inlet means to impart energy to the rotor element.

[0015] Optionally, the fluid enters the inlet at an angle offset from the rotation axis of the first rotor to impart more direct pressure to the rotor elements.

[0016] Optionally, in the embodiment of paragraph 0014, the device further comprises sealing means between the second rotor and the housing.

[0017] Optionally, in the embodiment of paragraph 0014, the device further comprises a shoulder portion adjacent to the rotor element and protruding from the first rotor.

[0018] Optionally, in the embodiment of paragraph 0014, the device further comprises two shoulders protruding from the first rotor on both sides of the rotor element.

[0019] Optionally, in the embodiment of paragraph 0014, during the rotation of the first rotor, the shoulder portion precedes the rotor element and closes the inlet during a portion of the first rotor's cycle.

[0020] In some embodiments, the device comprises two rotor elements and two recesses in a second rotor capable of receiving the rotor elements.

[0021] In some embodiments, the second rotor has a diameter twice that of the first rotor, and the second rotor includes two recesses that can receive rotor elements.

[0022] In some embodiments, the inlet and outlet are located within the zone of the chamber in which the rotor element moves, while avoiding the zone in which the second rotor moves.

[0023] Optionally, the inlet and outlet are positioned in a region of the chamber wall substantially perpendicular to the rotor's axis of rotation.

[0024] In some embodiments, when the rotor element engages with the recess, the rotor element simultaneously closes both the inlet and outlet.

[0025] In some embodiments, the rotor element occupies a sector of approximately 60° to 120° with respect to the axis of the first rotor.

[0026] In some embodiments, the rotor element occupies a sector of approximately 80° with respect to the axis of the first rotor.

[0027] In some embodiments, the apparatus further comprises extensions to inlets and / or outlets that further form ventilation areas.

[0028] In some embodiments, the ventilation area avoids the zone where the second rotor moves, while in other embodiments, the ventilation area is disposed in the zone where the second rotor moves.

[0029] Typically, in some embodiments, the rotor element includes a front face that precedes other portions of the rotor element during rotation of the rotor, a rear face opposite the front face, and an outer face that contacts or substantially contacts the wall of the chamber during rotation of the first rotor, an outer front joint between the front face and the outer face of the rotor element, an outer rear joint between the rear face and the outer face of the rotor element, an inner front joint between the outer wall of the first rotor and the front face of the rotor element, and an outer rear joint between the outer wall of the first rotor and the rear face of the rotor element. The recess is defined by a wall spaced apart to receive the front and rear faces of the rotor element, and a floor that contacts or substantially contacts the outer face of the rotor element when the rotor element is received within the recess, an inner front joint between the floor and the front wall of the recess, an inner rear joint between the floor and the rear wall of the recess, an outer front joint between the front wall of the recess and the outer wall of the second rotor, and an outer rear joint between the rear wall of the recess and the outer wall of the second rotor.

[0030] In a preferred embodiment, at an engagement position where the outer joint of the rotor element is equidistant from the line X connecting the axes of the rotors, the inner joint of the rotor element is disposed beside a line extending from the axis of the first rotor and making an angle of approximately +37°, -37° with the line X, the outer joint of the rotor element is disposed beside a line extending from the axis of the first rotor and making an angle of approximately +30°, -30° with the line X, the inner joint of the recess is disposed beside a line extending from the axis of the second rotor and making an angle of approximately +38°, -38° with the line X, and the inlet and outlet are disposed within the zone where the rotor element moves but avoid the zone where the second rotor moves.

[0031] In another preferred embodiment, at an engagement position where the outer joint of the rotor element is equidistant from the line X connecting the axes of the rotor, the inner and outer joints of the rotor element are positioned beside a line extending from the axis of the first rotor and making an angle of approximately +40° and -40° with the line X, the inner joint of the recess is positioned beside a line extending from the axis of the second rotor and making an angle of approximately +43° and -43° with the line X, the outer joint of the recess is positioned beside a line extending from the axis of the second rotor and making an angle of approximately +46° and -46° with the line X, and the inlet and outlet are positioned within the zone in which the rotor element moves but avoid the zone in which the second rotor moves.

[0032] In another preferred embodiment, at an engagement position where the outer joint of the rotor element is equidistant from the line X connecting the axes of the rotor, the inner and outer joints of the rotor element are positioned beside a line extending from the axis of the first rotor and making angles of approximately +40° and -40° with the line X, and the entrance is located within the zone in which the rotor element moves, within a line extending from the axis of the first rotor and making an angle of approximately +38° with the line X, and the zone in which the second rotor moves To avoid the zone in which the rotor element moves, the exit is located within a line extending from the axis of the first rotor and making an angle of approximately -39° with line X, and to avoid the zone in which the second rotor moves, the inner joint of the recess is located beside a line extending from the axis of the second rotor and making an angle of approximately +45° and -45° with line X, and the outer joint of the recess is located beside a line extending from the axis of the second rotor and making an angle of approximately +53° and -53° with line X.

[0033] In a preferred embodiment, the space between the inlet and outlet is defined by lines extending from the axes of both rotors and making angles of approximately +15° and -15° with line X.

[0034] In another preferred embodiment, at an engagement position where the outer joint of the rotor element is equidistant from the line X connecting the axes of the rotor, the inner and outer joints of the rotor element are positioned beside a line extending from the axis of the first rotor and making angles of approximately +40° and -40° with the line X, and the entrance is located within the zone in which the rotor element moves, within a line extending from the axis of the first rotor and making an angle of approximately +38° with the line X, and the zone in which the second rotor moves To avoid the zone in which the rotor element moves, the exit is located within a line extending from the axis of the first rotor and making an angle of approximately -39° with the line X, and to avoid the zone in which the second rotor moves, the inner joint of the recess is located beside a line extending from the axis of the second rotor and making an angle of approximately +46° and -46° with the line X, and the outer joint of the recess is located beside a line extending from the axis of the second rotor and making an angle of approximately +53° and -53° with the line X.

[0035] In some embodiments of the present invention described above, the apparatus is configured to provide rotational energy to a first rotor or a second rotor to draw in fluid through an inlet means and push out fluid through an outlet means.

[0036] Preferably, in the embodiment of paragraph 0035, the fluid is air or an air / oxygen mixture, and the apparatus provides a pump for a ventilator.

[0037] Optionally, in the embodiment of paragraph 0035, during the rotation of the first rotor, the shoulder follows the rotor element and closes the outlet during a portion of the first rotor's cycle.

[0038] Optionally, in the embodiment of paragraph 0035, the outlet is provided with a one-way valve that can be sealed when the pressure is released.

[0039] In some embodiments of the present invention, the device includes two inlets.

[0040] In some embodiments, the apparatus further includes an ignition means and is configured to introduce a combustible fluid or a mixture of fluids through an inlet for combustion in order to energize the rotor element.

[0041] In an optionally configured embodiment, the device further comprises a shoulder portion adjacent to the rotor element and projecting from the first rotor, the shoulder portion closing the inlet ahead of the rotor element during the rotation of the first rotor for a portion of the first rotor's cycle.

[0042] A second aspect of the present invention provides a method for extracting energy from a fluid using the apparatus described above, the method comprising the steps of introducing a pressurized fluid into a chamber through an inlet to impart energy to a rotor element, and allowing the pressurized fluid to exit the chamber through an outlet. In connection therewith, the present invention provides the use of the apparatus described herein as a turbine.

[0043] A third aspect of the present invention provides a method for extracting energy from a combustible fluid using the apparatus described above, the method comprising the steps of introducing the combustible fluid into the chamber of the apparatus through the inlet, igniting the combustible fluid to energize a rotor element, and allowing the burned fluid to exit the chamber through the outlet. In connection therewith, the present invention provides the use of the apparatus described herein as a combustion engine.

[0044] A fourth aspect of the present invention provides a method for pumping a fluid using the apparatus described above, the method comprising the steps of bringing the inlet of the apparatus into contact with the fluid, and applying rotational energy to a first rotor and / or a second rotor to draw the fluid into the inlet and draw it out through the chamber to the outlet. In connection therewith, the present invention provides the use of the apparatus described herein as a pump.

[0045] Optionally, in the method of the fourth embodiment, the fluid is air or an air / oxygen mixture, and the pump is a ventilator pump. [Brief explanation of the drawing]

[0046] The rotary drive device of the present invention is described below in reference to the accompanying drawings illustrating preferred embodiments.

[0047] [Figure 1] Figure 1 shows the interior of a rotary drive housing suitable for use as a pump, turbine, or combustion engine. [Figure 1A] Figure 1A is a view of the inside of the housing of the rotary drive device shown in Figure 1 after half a cycle of rotation. [Figure 2] Figure 2 is a cross-sectional view of the rotational drive shown in Figure 1. [Figure 3A] Figure 3A is a partial perspective view of a rotor showing the sealing means of the present invention. [Figure 3B] Figure 3B is a partial perspective view of the rotor in the present invention without sealing means. [Figure 3C] Figure 3C is a partial perspective view of a rotor according to the present invention, in which the rear surface of the rotor element has a shape that reduces or mitigates drag in the fluid. [Figure 3D] Figure 3D is a cross-sectional view of the arrangement of two rotary drive units coupled to each other within the housing. [Figure 4A] Figure 4A is an internal view of yet another embodiment of a housing suitable for use with a pressurized fluid medium to provide a turbine. [Figure 4B] Figure 4B is an internal view of yet another embodiment of a housing suitable for use with a pressurized fluid medium to provide a turbine, in which both sides of the rotor element are shaped to reduce or mitigate fluid drag. [Figure 5] Figure 5 shows an internal view of a housing of another embodiment suitable for use with a pressurized fluid medium to provide a turbine. [Figure 6] Figure 6 shows an internal view of a housing of a further embodiment of the present invention, suitable for use with a pressurized fluid medium to provide a turbine. [Figure 7]Figure 7 shows an internal view of a housing of a further embodiment of the present invention, suitable for use with a pressurized fluid medium to provide a turbine. [Figure 8] Figure 8 shows an internal view of a housing of a further embodiment of the present invention, suitable for use as a pump, such as a ventilator pump. [Figure 9] Figure 9 shows an internal view of a housing of a further embodiment of the present invention, suitable for use as a pump, such as a ventilator pump. [Figure 10] Figure 10 shows an internal view of a housing of a further embodiment of the present invention suitable for use as a pump or turbine. [Figure 11] Figure 11 shows an internal view of a housing of a further embodiment of the present invention suitable for use as a pump or turbine. [Figure 12A] Figure 12A shows an internal view of a housing of a further embodiment of the present invention suitable for use as a pump or turbine. [Figure 12B] Figure 12B shows an internal view of a housing of a further embodiment of the present invention suitable for use as a pump or turbine. [Figure 13] Figure 13 shows an internal view of a housing of a further embodiment of the present invention suitable for use as a pump or turbine. [Figure 14] Figure 14 shows the interior of a housing of a further embodiment of the present invention suitable for use as a combustion engine. [Figure 15] Figure 15 is an internal view of a housing of a further embodiment of the present invention suitable for use as a combustion engine. [Modes for carrying out the invention]

[0048] [Definition] Throughout this description of the present invention and in the following claims, unless the context should be interpreted to mean something else by explicit language or necessary implication, the word “COMPRISE” or variations such as “COMPRISES” or “COMPRISING” are used in a comprehensive sense, that is, to identify the presence of the described features but not to preclude the presence or addition of further features in the various embodiments of the present invention. In addition, references to elements with the indefinite article “A” or “AN” do not preclude the possibility of multiple elements unless the context explicitly requires that only one element exists. Thus, the indefinite article “A” or “AN” usually means “at least one.”

[0049] As used herein, the term “fluid” is used generally to refer to liquids or gases, and mixtures thereof, including fuel / air mixtures or air / oxygen mixtures.

[0050] In the present invention, it is clear that the requirements or degree of “seal” or “seal engagement” vary depending on the proposed use, including the properties of the fluid and the rotational speed. As used herein, the term “seal engagement” is not intended to mean a complete seal or to imply that a complete seal is required in all cases. Rather, the term “seal engagement” indicates that flow in the opposite direction to the rotor's rotation is prevented at least substantially.

[0051] As used herein, the term “approximately” with respect to angles includes a range of 5°, preferably 4°, 3°, 2°, 1°, or 0.5° greater or less than the stated value, and with respect to percentages includes a range of 5%, preferably 4, 3, 2, or 1% greater or less than the stated value.

[0052] [Overall configuration of the rotary drive device] A general configuration of the rotary drive device according to the present invention is shown in Figures 1 and 2.

[0053] Figure 1 shows a conceptual diagram of "opposing interlocking rotors" of the rotary drive device of the present invention. The housing 10 encloses a first rotor 11 and a second rotor 14. The rotor 11 includes a single protruding rotor element 12 that is received by a recess 13 of the second rotor 14.

[0054] Together with the peripheral walls 16 and 17 of the respective rotors 11 and 14, the housing 10 defines a chamber around the first rotor through which the rotor elements 12 pass. The chamber has at least one inlet 18 and at least one outlet 19 through which fluid can enter and exit the chamber. In the drawings, the inlet 18 and outlet 19 are shown in areas of the chamber wall 15a substantially perpendicular to the rotor's axis of rotation. However, the arrangement of the inlet and outlet can be modified; for example, the inlet can be positioned so that fluid enters the chamber from one side Sa (Figure 2) of the apparatus and exits the chamber on the opposite side Sb (Figure 2), or optionally, the inlet and outlet can be provided on sides Sa and Sb of the apparatus, respectively, to reduce eccentricity. The positions of the inlet and outlet relative to the rotor elements and recesses can also be modified as further described herein.

[0055] In Figures 1 and 2, the protruding rotor element 12 and the recess 13 engage with each other once per cycle. When the rotor element 12 and the recess 13 are not engaged with each other, the first rotor remains in contact with the second rotor, and therefore the second rotor remains sealed engaged with the first rotor throughout rotation. Thus, it will be clear that the rotational speeds of rotors 11 and 14 are the same. Coherence can be achieved by a timing belt, teeth (having meshing teeth), or other timing means known in the art. In Figure 1, the diameters of rotors 11 and 14 are substantially the same. If the diameters were different, the larger diameter rotor would need to rotate faster than the smaller diameter rotor, complicating the mechanism.

[0056] Figure 1A shows the apparatus offset by half a cycle from the apparatus in Figure 1. The protruding rotor element 12 is disengaged from the recess 13 (sealed here by the wall 15a of the chamber 15), and the peripheral walls 16 and 17 of the respective rotors 11 and 14 form a seal that engages with each other for the remainder of the cycle. A high level of machining precision is required if it is desired that the walls 16 and 17 seal each other during rotation.

[0057] [Detailed geometric shape of rotor elements and recesses] The detailed geometric shapes of the rotor elements and recesses can vary. The rotor elements have various faces, indicated by reference numerals 12a, 12b, and 12c in Figure 1. In the rotational direction shown in Figure 1, reference numeral 12b indicates the front of the rotor element, reference numeral 12a indicates the rear, and reference numeral 12c indicates the outer surface of the rotor element. The front is the face that precedes the other parts of the rotor element and is the face that first reaches the fixed parts of the device (e.g., inlet and outlet). The recess 13 generally has walls 13a, 13b and a floor 13c (shown in Figure 1A). Wall 13b is the front wall of the recess that precedes the other parts of the recess when the rotor 14 is rotating in the opposite direction to the rotor 11.

[0058] The different surfaces of the rotor element and recess may have different geometric shapes depending on the purpose, for example, they may be linear or have more complex curved surfaces. In the following description, the geometric shapes of the rotor element and recess are characterized by four joints, each of which may be sharp angles or curved surfaces.

[0059] Referring to Figure 1, the geometric shape of the rotor element 12 is represented by an inner front joint 121, which is the joint between the wall 16 of the rotor 11 and the front surface 12b of the rotor element 12; an inner rear joint 122, which is the joint between the wall 16 of the rotor 11 and the rear surface 12a of the rotor element 12; an outer front joint 123, which is the joint between the front surface 12b and the outer surface 12c of the rotor element 12; and an outer rear joint 124, which is the joint between the rear surface 12a and the outer surface 12c of the rotor element 12.

[0060] Similarly, the geometric shape of the recess 13 is represented by an inner front joint 131, which is the joint between the floor 13c and the front wall 13b of the recess 13; an inner rear joint 132, which is the joint between the floor 13c and the rear wall 13a of the recess 13; an outer front joint 133, which is the joint between the front wall 13b of the recess 13 and the wall 17 of the rotor 14; and an outer rear joint 124, which is the joint between the rear wall 13a of the recess 13 and the wall 17 of the rotor 14.

[0061] In Figure 1, for example, it can be seen that joints 131 and 132 are predetermined corners. Joints 133 and 134 occur as part of a complex curve, corresponding to the points where the circular contour of wall 17 ends.

[0062] A conceptual line X connecting the axes of shafts A and B is shown as a dashed line in Figure 1, and the position of the joint can be explained by referring to line X. This is done by referring to the engagement position where the outer front joint 123 and outer rear joint 124 of the rotor element 12 are equidistant from line X.

[0063] In such engagement positions, the positions of joints 121, 122, 123, and 124 can be represented by the angle created between two lines: the line connecting the joint to the axis of shaft A and line X. This is shown in the figure and specific embodiments will be further described below. The positions of joints 121 and 123 are, for example, approximately +5°, +10°, +15°, +16°, +17°, +18°, +19°, +20°, +21°, +22°, +23°, +24°, +25°, +26°, +27°, +28°, +29°, +30°, +31°, +32°, +33°, +34°, +35°, +36°, +37°, +38°, +39°, +40°, They can be expressed independently by angles such as 41°, +42°, +43°, +44°, +45°, +46°, +47°, +48°, +49°, +50°, +51°, +52°, +53°, +54°, +55°, +56°, +57°, +58°, +59°, +60°, +65°, +70°, +75°, +80°, +85°, +90°, +95°, or +100°. The positions of the joints 122 and 124 are, for example, approximately -5°, -10°, -15°, -16°, -17°, -18°, -19°, -20°, -21°, -22°, -23°, -24°, -25°, -26°, -27°, -28°, -29°, -30°, -31°, -32°, -33°, -34°, -35°, -36°, -37°, -38°, -39°, -40°, - These can be independently represented by angles such as 41°, -42°, -43°, -44°, -45°, -46°, -47°, -48°, -49°, -50°, -51°, -52°, -53°, -54°, ​​-55°, -56°, -57°, -58°, -59°, -60°, -65°, -70°, -75°, -80°, -85°, -90°, -95°, or -100°. Similarly, the positions of joints 131, 132, 133, and 134 can be represented by the angle formed between two lines: the line connecting the joint to the axis of shaft B and line X.The positions of the joints 131 and 133 are, for example, approximately -5°, -10°, -15°, -16°, -17°, -18°, -19°, -20°, -21°, -22°, -23°, -24°, -25°, -26°, -27°, -28°, -29°, -30°, -31°, -32°, -33°, -34°, -35°, -36°, -37°, -38°, -39°, -40°, - Angles such as 41°, -42°, -43°, -44°, -45°, -46°, -47°, -48°, -49°, -50°, -51°, -52°, -53°, -54°, ​​-55°, -56°, -57°, -58°, -59°, -60°, -65°, -70°, -75°, -80°, -85°, -90°, -95°, or -100° can be expressed independently. The positions of the joints 132 and 134 are, for example, approximately +5°, +10°, +15°, +16°, +17°, +18°, +19°, +20°, +21°, +22°, +23°, +24°, +25°, +26°, +27°, +28°, +29°, +30°, +31°, +32°, +33°, +34°, +35°, +36°, +37°, +38°, +39°, +40°, They can be expressed independently by angles such as 41°, +42°, +43°, +44°, +45°, +46°, +47°, +48°, +49°, +50°, +51°, +52°, +53°, +54°, +55°, +56°, +57°, +58°, +59°, +60°, +65°, +70°, +75°, +80°, +85°, +90°, +95°, or +100°.

[0064] As used herein, a positive angle, for example +40°, is an angle measured clockwise from line X around a specified axis (A or B). A negative angle, for example -40°, is an angle measured counterclockwise from line X around a specified axis (A or B).

[0065] The above discussion covers various geometric shapes of the rotor element and the outer range of the recess. These features provide various different profiles for engagement and subsequent disengagement of the rotor element and recess, as well as the inlet and outlet. Next, the geometric shape of the system in cross-section will be described.

[0066] [Rotor elements, recesses, and chambers in cross-section] Figure 2 shows a cross-section of a rotary drive device according to the present invention. In this embodiment, the rotor element 12 has a semicircular outer surface 12c that allows for accommodation by a recess 13. It can be understood that Figure 2 shows only one possibility for the features 12a, 12b, 12c of the rotor element 12. In the embodiment of Figure 2, the drive shaft A is shown on the rotor 11, and the rotor 14 rotates around a further shaft B. As shown in Figure 2, a seal ring, generally indicated by reference numeral 20, can be provided to maintain the integrity of the chamber 15. Further sealing means 21 embedded in the surface of the rotor element 12 can be optionally provided to seal with the chamber wall 15a. The configuration of the rotor 11 and rotor element 12 with the sealing means 21 is shown in Figure 3A. It can be understood that a seal ring may not be necessary when the clearance is extremely small. Embodiments without a seal ring, such as the one shown in Figure 3B, are expected to achieve significantly improved efficiency.

[0067] Figures 2 and 3A to 3C show the curved contours of the rotor element 12 and the chamber wall 15a, but it can be seen that other contours, including flat contours which are easier to manufacture, are also possible. An example of this is shown in Figure 3D, in which the rotor elements 112,212 have flat surfaces parallel to axes A and B which contact the housing 100.

[0068] The rotor thickness relative to the rotor diameter can vary, and may be, for example, approximately 10%, 20%, 30%, 40%, or 50% of the rotor diameter.

[0069] The shape and size of the protruding rotor elements can be adapted according to the laws of fluid dynamics to achieve various results.

[0070] For example, Figure 3C shows one embodiment of the present invention in which the rear surface 12a of a protruding rotor element includes a shape that reduces or mitigates drag in the fluid. In this example, the shape of the rear surface 12a of the rotor element 12 is a composite shape. The rearmost part 12x of the composite shape extends in a smooth curve from the surface 16 to the outermost point 12y of the convex rotor element 12. Such composite shapes on one or both sides of a protruding rotor element can improve efficiency. Generally, composite shapes can be found on one or both sides 12a and 12b of turbines, combustion engines, and pumps / ventilators. Figure 4B shows an example in which both sides 12a and 12b of a rotor element 12 include a composite shape. In Figure 4B, for comparison and to aid in understanding the present invention, the simple shape of the rotor element 12 is shown by a dashed line, but the general locations of the inlet 18 and outlet 19 behind the composite shape are also shown by dashed lines. The composite shape can reduce the stroke volume while improving fluid flow and reducing or mitigating drag. Such a composite shape can incorporate shoulders (or multiple shoulders) adjacent to the rotor element, which can serve to close inlets (or multiple shoulders) and outlets (or outlets) at specific points in the cycle, as will be further described below. Generally, the inlets and / or outlets may be on either side of the chamber 15, rather than just one side as shown in the drawings.

[0071] It is preferable that any fixed point on each rotor surface 16 and 17 moves at the same relative speed. This avoids unnecessary friction and thus loss of efficiency.

[0072] Two or more rotary drive units may be coupled together, and the orientations of the rotors 11 and 14 are offset so that the unit in the "power mode" of the cycle is offset relative to the unit that is not currently supplying power. This is expected to give the system smoother operation. For example, two coupled units offset the orientations of their respective rotors 11 and 14 by 180°, three units by 120°, four units by 90°, and so on. An example of this is shown in Figure 3D. Two units within the housing 100 share shafts A and B and are coupled by a timing belt or a toothed mechanism T. The rotor 112 of the first unit is in the disengaged upper position, and rotor 111 is in contact with rotor 114. The recess 113 is moved to the bottom of the unit. In this position, the rotor element 212 of the second unit occupies the recess of rotor 214. Thus, a portion of the chamber 115 is visible above the second unit.

[0073] [Fluid-driven rotary drive device] Embodiments of the present invention in which the rotary drive device functions as a turbine are shown, for example, in the embodiments shown in Figures 4A to 7. Since almost all of the water generates the driving force, the present invention is considered to function efficiently as a turbine, with the only very small amount of energy that is not captured being the energy in the fluid sliding through very small gaps at various stages of the cycle.

[0074] In some turbine embodiments, the first and second rotors can maintain a seal engagement during rotation, i.e., the rotor elements are in contact with the recesses or the surfaces 16 and 17 are in contact with each other. This prevents the fluid from bypassing the rotor elements and causing power loss during lost contact portions of the cycle. Such power loss is only partial (and can be offset by linking multiple turbines as described later) and reduces the turbine's efficiency. In pump embodiments, this reduction in efficiency may be less of a concern than providing a smooth flow of fluid.

[0075] Referring to Figures 4A, 4B, and 5, fluid pressure is introduced into the chamber 15 through the inlet port 18 and exits the chamber 15 through the outlet 19. The fluid pressure is supplied from a fluid source containing water or steam, such as in a hydraulic or steam-driven turbine. In this way, the rotor element functions as a driving element that drives the rotation of the first rotor. In the illustrated embodiment of a clockwise rotation axis (of the rotor 11), the inlet 18 is preferably located at approximately 7 or 8 o'clock (i.e., +30° to +60°) around axis A with respect to line X, and the outlet 19 is preferably located at 4 or 5 o'clock (i.e., -30° to -60°) around axis A with respect to line X. This gives the maximum "stroke" (either an arc to which power is applied or gas or fluid is pushed out of the chamber 15), but other positions may be possible in future embodiments.

[0076] Preferably, the power cycle begins with the rotor element 12 in a position directly above the inlet 18, for example, at +60° to +90° around axis A with respect to line X (i.e., 8 to 9 o'clock). In this position, walls 16 and 17 are in inlet 18 "rear" seal engagement so that fluid pressure is transmitted to the rear surface 12a of the rotor element 12, thereby pushing the rotor 11 in the clockwise direction shown in this example. The rotor 11 is further mounted on the drive shaft A (Figure 2), and its rotational energy can be made available for further use, including use to generate electricity using a generator in the conventional manner.

[0077] When the protruding rotor element 12 reaches the exit 19, the centrifugal motion continues to rotate both rotors 11 and 14 past the engagement of the rotor element 12 in the recess 13, and a new cycle begins.

[0078] In comparison with Figure 1, in Figures 4A, 4B, and 5, the rotor 11 includes an additional shoulder 26 at the base of the rotor element 12. When the rotor 11 includes the shoulder, the rotor element 12 does not directly join to the wall 16 of the rotor element 12, so the internal joints 121 and 122 of the rotor element 11 do not exist. However, the shape of the rotor element can still be represented by referring to a conceptual internal joint. The shoulder 26 can have the effect of being a shut-off valve covering the inlet 18 at a particular stage of the cycle to improve the success and efficiency of a steam and water-driven turbine. In some embodiments, the shoulder 26 can provide strength to the rotor element. For example, in a turbine embodiment, the shoulder can act as a buttress to resist the pressure applied to the rotor element. In such embodiments, the shoulder can be described as a flange. In Figure 4A, the shoulder 26 covers the inlet 18 and outlet 19 when the rotor element 12 engages with the recess 13 of the rotor 14. In the turbine embodiment, the use of two shoulders 26 on either side of the rotor element 12 is advantageous because, as the rotor rotates, the outlet 19 is not covered by the rear shoulder while the inlet 18 is covered by the leading shoulder, thus providing a constant flow through the turbine. The precise shape of the shoulders 26 relative to the inlet 18 and outlet 19 can be adjusted to result in complete coverage of the inlet 18 and incomplete coverage of the outlet 19. This allows for freer movement of the fluid leaving the chamber 15 and avoids pressure buildup.

[0079] Referring to Figure 4B, a dashed line X is shown between shaft A and shaft B, and further dashed lines are shown extending from both shafts A and B on both sides of line X, forming angles of +50° and -50° with line X. In the figure, these dashed lines illustrate the relationships between parts and help to understand the present invention. For example, in Figure 4B, the inner front joint 121 and the inner rear joint 122 form angles of approximately +50° and -50° with respect to line X. The inner front joint 131 and the inner rear joint 132 of the recess 13 align with these lines from shaft B and therefore form angles of +50° and -50° with respect to line X.

[0080] The shapes of the inlet 18 and outlet 19 themselves can also be adapted. In Figures 1 to 11, the inlet 18 and outlet 19 are shown schematically, illustrating the principle that the inlet 18 and outlet 19 should not be covered by the rotors 11 and 14, and if present, should only be intermittently covered by the rotor elements 12 and shoulders 26. However, in a preferred embodiment, the shapes of the inlet 18 and outlet 19 are as shown in the drawings.

[0081] In Figures 4A and 4B, the inlet 18 is located on the back wall of the chamber 15, adjacent to the engagement of the peripheral walls 16 and 17. To maintain the integrity of the chamber 15, an additional sealing means 20 is shown between the second rotor and the housing. However, in some embodiments, particularly when the clearance between the housing 10 and the wall 17 is very small, the sealing means 20 may not be necessary or beneficial.

[0082] Figure 5 shows a further embodiment having only one shoulder portion 26 molded to cover the inlet 18. In this figure, at the engagement position where the outer front joint 123 and outer rear joint 124 are equidistant from line X, the area for locating the inlet 18 is within the corresponding shape of the shoulder portion 26 and is represented by a dashed line extending from axis A and making a +50° angle with line X. The area for locating the outlet 19 is represented by dashed lines extending from shafts A and B, making angles of -50° and +50° with respect to line X, respectively. When the rotor element 12 is in the illustrated position, the inlet 18 is blocked by the shoulder portion 26, preventing the fluid (water) from entering the housing through the inlet 18, and the rotor is rotating due to the amount of motion from the previous cycle. As the rotor element 12 passes through the inlet 18, the fluid entering through the inlet 18 simultaneously applies pressure to the surface 12a of the rotor element 12 and the exposed surface of the rotor 14, thus driving the next cycle.

[0083] As can be understood, additional seals can be provided to improve efficiency. For example, as shown in Figure 4A, a linear seal 20 can be provided between the wall 17 of the rotor 14 and the wall of the housing 10. However, as mentioned above, in embodiments where the clearance between the wall 17 and the housing 10 is very small, the sealing means is not necessary and may actually reduce efficiency.

[0084] A further means of improving efficiency is to provide a seal, such as an O-ring in a track, on one or both of the flat surfaces of each rotor, which is folded back onto the rotor and extends around the rotor near the outer circumference of the surface.

[0085] For example, when used as a turbine that utilizes the power of high-pressure water or steam generated from coal, oil, nuclear, or geothermal energy, it is possible to include a valve (not shown) at the inlet 18 to momentarily close the intake when the protruding rotor element 12 rotates to a point where it passes directly from the outlet 19 to the inlet 18 (e.g., 9 o'clock). In most cases, it is not necessary to use a valve on the outlet 19, as it simply allows a gas / water escape route when the protruding rotor element 12 is forced to move in the next cycle.

[0086] The inlet valve may be actuated by a cam driven by other moving parts in relation to the stages of the cycle. The inlet valve may not be required and is not shown in Figure 5 or Figure 6.

[0087] Figure 6 shows a further embodiment in which the rotor 14 has two recesses and two protruding rotor elements 12 having surfaces 12a that receive force from a fluid chamber 15 onto the rotor elements 12. Thus, the two recesses of the second rotor accommodate the two rotor elements and maintain a seal engagement when the rotor elements engage with the recesses.

[0088] This configuration can improve efficiency by eliminating rotor eccentricity and improving the balance between rotors 11 and 14. This is particularly advantageous when extremely high revolutions per minute are required.

[0089] Figure 7 shows a further embodiment in which rotor 14 is substantially twice the diameter of rotor 11 and requires two recesses 13 in rotor 14. It should be noted that the principle of multiplying the diameter of one or more rotors can also be applied to other preferred embodiments of the present invention, such as combustion engines and ventilator pumps.

[0090] [Rotary drive device as a pump] Another aspect of the present invention, in which a rotary drive device provides a pump such as a water pump or a ventilator pump, is shown by the embodiments in Figures 8 and 9. This aspect of the present invention also has applications as a condenser device.

[0091] The device functions as a pump when rotational motion is applied externally to the rotor 11 or 14 via the drive shaft while connected to a fluid reservoir (water, gas, or air) at the inlet 18. As shown in Figure 8, a fluid such as air or an air-oxygen mixture is drawn in through the inlet 18 and pushed around the chamber 15 by the surface 12b of the rotor element 12, reaching the outlet 19 at a pressure determined by the rotational speed of the rotor 11. In Figures 8 and 9, during the rotation of the first rotor, the shoulder follows the rotor element and closes the outlet during a portion of the first rotor's cycle, which is useful in embodiments of a high-speed pump.

[0092] Optionally, in embodiments of a pump or ventilator, the first and second rotors can maintain a seal engagement during rotation, i.e., at any stage of rotation, either with the rotor element 12 in contact with the recess 13 or with surfaces 16 and 17 in contact with each other. However, in some embodiments, the first and second rotors may briefly lose contact with each other during a portion of the rotation (e.g., when the rotor element 12 loses contact with the recess 13). During such a stage of rotation, there may be a decrease in the amount of fluid / air drawn in by the pump / ventilator. The fluid / air draw-in returns to its maximum level in the next stage of rotation once the seal between the first and second rotors is re-established.

[0093] Examples are described in more detail below.

[0094] [Example: Embodiment of the pump shown in Figure 8] In Figure 8, the inlet 18 is located inside a sector defined by a dashed line extending from shaft A and making a +50° angle with line X, while the outlet 19 is located outside a sector defined by a dashed line extending from shaft A and making a -50° angle with line X. This arrangement provides maximum pressure to the fluid / gas exiting the outlet 19 until the outlet 19 is blocked by the rotor element 12 and shoulder 26, after which the seal between the rotors is removed when the rotor element 12 no longer contacts the recess 13. Once the seal between the rotors is re-established, the pressure at the outlet 19 is restored. The embodiment in Figure 10 is expected to be particularly suitable for higher-speed rotations, such as high-pressure pumps. Such pumps may not require seals with very small clearances.

[0095] [Example: Embodiment of the pump / ventilator in Figure 9] The embodiment in Figure 9 features two inlets 18 and is more suitable for low-speed pumps such as ventilators. One of the inlets 18 extends from shaft A and is located inside and outside a sector defined by a dashed line making a +50° angle with line X. This arrangement means that when the rotor element 12 reaches the first inlet 18, the rotors 11 and 14 become sealed engagement, and thus new gas can begin to be drawn in. This also prevents a vacuum from being generated when the rotors 11 and 14 seal behind the rotor element 12. An alternative configuration may have two inlets radially aligned with respect to the rotor 11, requiring a smaller size for each inlet. Optionally, such a pump may have rubberized seals incorporated into the design. The embodiment in Figure 9 features a one-way valve on the outlet 19 that can be sealed as the rotor element 12 passes through the outlet 19. The seal on the outlet 19 prevents back pressure from pushing the fluid back into the chamber 15. With respect to outlet 19, the one-way valve may be in contact with the main body 10 of the device or may be separate from the device. Outlet 19 extends from shaft A and is located outside the sector defined by a dashed line that forms an angle of -50° with line X.

[0096] The choice of applying rotational motion to either rotor 11 or rotor 14 provides flexibility when configuring the device of the present invention as part of a pump, such as in a ventilator.

[0097] In one embodiment, the pump for the ventilator can be provided with two inlets, one for air and one for oxygen (as shown in Figure 9), thereby allowing an air / oxygen mixture to be delivered to the patient. The use of two inlets allows for a more precise air / oxygen mixture and also provides the option to adjust it in real time, which is advantageous for the ventilator embodiment.

[0098] [Rotary drive device with wide rotor element] Figures 10 to 13 show rotary drive devices with wide rotor elements. The embodiments shown in these figures are suitable as turbines or pumps, but combustion engines with wide rotor elements will also be described below. In the embodiments of Figures 10 to 13, the rotor 11 and rotor 14 have the same radius, and the rotor element 12 extends radially beyond the rotor 11 or rotor 14 by a distance of about 30% of the radius of rotor 11.

[0099] Generally, a wide rotor element simultaneously closes both the inlet 18 and the outlet 19 in the engagement position shown in Figures 10 to 13. In this way, leakage of fluid around the chamber 15 is avoided. The inlet 18 is positioned near a line making a positive angle with line X in the range of approximately +30° to +90°, preferably +30° to +60°, and the outlet 19 is positioned near a line making a negative angle with line X in the range of approximately -30° to -90°, preferably -30° to -60°. This means that the rotor element generally occupies a sector of approximately 60° to approximately 180°, preferably approximately 60° to 120°, and all joints fall within this sector range. For example, a wide rotor element can preferably occupy a sector of approximately 60°, 70°, 80°, 90°, or 100°. Preferably, the rotor element occupies a sector of approximately 80°. This results in a balanced degree of covering that allows both the inlet 18 and outlet 19 to be covered simultaneously while maintaining the stroke volume of the chamber 15.

[0100] In Figure 10, the inner joints 121 and 122 of the rotor element 12 are located beside a line extending from shaft A and forming angles of +37° and -37° with respect to line X. The rear surface 12a and front surface 12b do not extend radially from the rotor 11. Instead, the outer joints 123 and 124 extend from shaft A and are located beside a line forming angles of +30° and -30° with respect to line X. The radial orientation of the rear surface 12a and front surface 12b is expected to achieve the same result. Turning to the recess 13, the inner joints 131 and 132 of the recess are located by a sector extending from shaft B and forming angles of +38° and -38° with respect to line X.

[0101] The outer surface of rotor 12 moves faster than recess 13 due to its greater distance from shaft A. Therefore, no seal engagement occurs between reference numeral 12 and reference numeral 13; rather, there is near contact between their surfaces, with only a nominal gap between them. The slightly smaller angles of inner joints 121 and 122 compared to inner joints 131 and 132 (a difference of 1° in this case, 37° and 38° respectively) also allow the recess to accommodate the rotor element. The near contact results in some flow through the gap, thus slightly reducing efficiency. The wide rotor element completely covers the inlet 18 and outlet 19 in the engaging orientation shown in Figure 10.

[0102] In this example, the inlet 18 and outlet 19 are located in the zone where the rotor element 12 moves, but avoid the zone where the rotor 14 moves. In the engagement position shown in Figure 10, both the inlet 18 and outlet 19 are blocked by the rotor element. Therefore, the positions of 18 and 19 are such that the flow is affected by the movement of the rotor 11, but not by the movement of the rotor 14.

[0103] Referring to Figure 11, in this embodiment, the rear surface 12a and the front surface 12b extend radially from the rotor 11 and, in the orientation shown, align with the line extending from shaft A, making angles of +40° and -40° from line X (as with the inner joints 121, 122 and the outer joints 123, 124). Thus, the wide rotor element occupies approximately 80° of sector. The inlet 18 is shaped to avoid the zone through which the rotor 14 passes, but the extension to the inlet forms a small ventilation area 18a. Similarly, the extension to the outlet 19 forms a larger ventilation area 19a that extends into the zone of the rotor 14. The ventilation areas act to prevent back pressure from pushing the fluid back into the chamber 15, stopping the device or significantly slowing its rotation, thereby providing smoother operation of the device.

[0104] In the embodiment shown in Figure 11, the inner joints 131 and 132 are positioned by sectors extending from the shaft B and forming angles of +43° and -43° from line X, while the outer joints 133 and 134 are positioned by sectors extending from the shaft B and forming angles of +46° and -46° from line X. Therefore, the recesses can accommodate the rotor elements even though the angles of the inner joints 121 and 122 are slightly smaller than those of the inner joints 131 and 132 (in this case, 40° and 43°, a difference of 3 degrees).

[0105] In the embodiment of Figure 12, similar to Figure 11, the rear surface 12a and the front surface 12b extend radially from the rotor 11 and, at the illustrated engagement position, are aligned with a line extending from shaft A and at angles of +40° and -40° from line X (similar to the inner joints 121, 122 and outer joints 123, 124). The inlet 18 is located in a sector defined by line X and a dashed line extending from axis A and at an angle of +38° to line X. The outlet 19 is located in a sector defined by line X and a dashed line extending from axis A and at an angle of -39° to line X. By selecting +38° and -39°, respectively, to define reference numerals 18 and 19, both are reliably closed by element 12 at the engagement position (except for the ventilation regions 18a and 19a described below). As mentioned above, closing both the inlet port 18 and the outlet port 19 simultaneously prevents fluid leakage around the chamber 15, thereby preventing energy loss.

[0106] The inlet 18 is also shaped to avoid the zone through which the rotor 14 passes, but the extension to the inlet forms a small ventilation region 18A. The outlet 19 is also shaped to avoid the zone through which the rotor 14 passes, but the extension to the inlet forms a small ventilation region 19A. Thus, in the illustrated engagement position, the inlet 18 and outlet 19 are blocked by the rotor element 12, but the ventilation regions 18A and 19A are not blocked. To avoid back pressure, the inlet 18 is preferably slightly smaller than the outlet 19. The relative sizes of the inlet 18 and outlet 19 may vary depending on the function of the device. In the case of a turbine, the inlet is smaller than the outlet because reducing back pressure is desirable, but in a pump (or condenser), the opposite may be true to increase the pressure produced.

[0107] The inner joints 131 and 132 of the recess 13 are positioned next to a line extending from shaft B, making angles of +45° and -45° with respect to line X. The outer joints 133 and 134 are positioned next to a line extending from shaft B, making angles of +53° and -53° with respect to line X. Thus, the recess can accommodate the rotor element even though the angles of the inner joints 121 and 122 are slightly smaller than those of the inner joints 131 and 132 (in this case, 40° and 45°, a difference of 5 degrees).

[0108] The geometric shapes of the inlet 18 and outlet 19 are shown in Figure 12B. As can be seen in the figure, the space between the inlet and outlet is defined by lines extending from the axes of both rotors and making angles of +15° and -15° with respect to line X.

[0109] Figure 13 shows an embodiment similar to the embodiment shown in Figure 12. In this embodiment, the inner joints 131 and 132 of the recess 13 are positioned beside lines extending from the shaft B and making angles of +46° and -46° with respect to line X. This results in a slightly wider recess compared to the example in Figure 12. Other geometric shapes in Figure 13 are equivalent to the geometric shapes shown in Figure 12. A device having this geometric shape functions very efficiently as a pump without generating friction.

[0110] To operate this device as a turbine, efficiency can be improved by increasing the angle at which the fluid enters the inlet 18. Preferably, the fluid enters the inlet 18 at an angle offset from the axis of rotation of the rotor 11 so as to directly push the rotor elements. This minimizes the risk of the rotor 11 being pushed out of its precise alignment. Other methods for reducing eccentricity in the turbine embodiment include drilling holes in both rotors to distribute the pressure more evenly to both sides of the rotor.

[0111] [Combustion-driven rotary drive device] Another aspect of the present invention in which a rotary drive unit functions as a combustion engine is illustrated by the embodiments shown in Figures 14 and 15. Suitable fuels are obvious and include petrol (gasoline) or hydrogen and oxygen.

[0112] In embodiments of the combustion engine, the peripheral walls 16 and 17 of the respective rotors 11 and 14 are able to maintain a seal engagement at least during the intake and combustion phases of the cycle, thus providing a limited space for combustion to transmit power to the rotor elements. The combustion engine further requires a spark plug 22 and utilizes two inlets 23 and 24 (not shown in Figure 14, but shown in Figure 15) that supply the fuel / air mixture as known in the art (for example only). This allows for precise air / fuel mixing and also provides the option of being adjustable in real time. Inlets 23 and 24 may be circular one-way valves. Valves are required to control the distribution of the mixture at inlets 23 and 24. The inlet valves may be actuated by cams driven from other moving parts in relation to the phases of the cycle. Also note that, as shown in Figure 15, the chamber wall 15a of the combustion chamber near the spark plug head is slightly recessed to allow rotation of the rotor element 12 through the spark plug head.

[0113] Combustion is preferably initiated at a stage of the cycle when segment 12 has just passed the last spark plug 22. This also allows for proper mixing time of the gases.

[0114] The explosion of fuel / air presses the rotor element 12 around axis A, driving the shaft to which the rotor 11 is mounted. The exhaust gases exit through outlet 19. Since segment 12 effectively pushes out the exhaust from the previous cycle when starting a new cycle, outlet 19 does not need to include a valve.

[0115] Two or more rotary drive units may be coupled together, and the orientations of the rotors 11 and 14 are offset such that the unit in the "power mode" of the cycle is offset relative to the unit that is not currently supplying power. This is expected to result in smoother engine rotation. For example, two coupled units offset the orientations of their respective rotors 11 and 14 by 180°, three units by 120°, four units by 90°, and so on. Several conventional "two-stroke" or "four-stroke" combustion engines with two or more units have their "power mode" offset using such an arrangement of units.

[0116] In a "two-stroke" combustion engine, energy is lost because the piston must be moved up and down. In this invention, the energy saved by not having to move the piston up and down is considered to outweigh the efficiency loss caused by compression losses beyond the seals, etc. Furthermore, while each cycle generates power, a four-stroke combustion engine requires one cycle to expel exhaust gases and draw in a fresh combustible gas mixture.

[0117] The size of the protruding rotor element 12 and the depth of the recess 13 may also be adjusted for proportionally larger thrust. The specific shape of the rotor element 12 within the recess 13 may also be modified to arrange optimal operating characteristics.

[0118] Although the shoulder portion 26 is shown in Figure 14, it is expected that this will not be necessary in the combustion-driven embodiment. Other variations of this alternative "valve" arrangement may be possible within the scope of the present invention.

[0119] It should be noted that in the embodiment of the combustion engine, using a wide rotor element 12 of the type shown in Figures 10 to 13 can provide better efficiency.

[0120] The rotary drive device of the present invention can be highly efficient and is considered to have the potential to replace conventional pump, turbine, or engine designs. At the very least, alternatives that present a method for constructing a "rotary" drive device should be considered.

Claims

1. A rotary drive device comprising a housing in which a first rotor and a second rotor are disposed, wherein the first rotor is rotatable about a first axis and has integrally formed rotor elements projecting radially therefrom, the rotor elements projecting radially from the rotor elements adjacent to the rotor elements such that the shoulders project radially from the first rotor such that the shoulders contact the sides of the rotor elements and at least partially close the outlet during a first portion of the cycle of the first rotor, the second rotor is rotatable about a second axis parallel to the first axis in the opposite direction to the first rotor, the second rotor has recesses capable of receiving the rotor elements, and the first rotor, the second rotor and the housing define a chamber around the first rotor through which the rotor elements pass, the chamber having inlets and outlets through which fluid can enter and exit the chamber.

2. The apparatus according to claim 1, wherein the first rotor and the second rotor can maintain a seal engagement during rotation.

3. The apparatus according to claim 1 or 2, wherein the rotor element does not come into contact with the floor of the recess while rotating.

4. The apparatus according to any one of claims 1 to 3, further comprising sealing means capable of forming a seal between the first rotor and the housing and / or the second rotor.

5. The apparatus according to any one of claims 1 to 4, further comprising sealing means on the rotor element capable of forming a seal between the rotor element and the housing and / or the second rotor.

6. The apparatus according to any one of claims 1 to 5, wherein the leading surface and / or rear surface of the rotor element or the shoulder portion are shaped to reduce or mitigate fluid drag.

7. The apparatus according to any one of claims 1 to 6, wherein the apparatus is configured to introduce pressurized fluid through the inlet to impart energy to the rotor element.

8. The apparatus according to claim 7, wherein the fluid enters the inlet at an angle offset from the first axis so as to impart more direct pressure to the rotor element.

9. The apparatus according to claim 7 or 8, further comprising a sealing means between the second rotor and the housing.

10. The apparatus according to any one of claims 7 to 9, further comprising a second shoulder portion protruding from the first rotor on the other side of the rotor element relative to the shoulder portion.

11. It comprises two rotor elements and two recesses in the second rotor that can receive the rotor elements, or The apparatus according to any one of claims 7 to 10, wherein the second rotor has a diameter twice that of the first rotor, and the second rotor comprises two recesses capable of receiving the rotor elements.

12. The apparatus according to any one of claims 1 to 11, wherein the inlet and outlet are located within the zone of the chamber in which the rotor element moves, and are located so as to avoid the zone in which the second rotor moves.

13. The apparatus according to any one of claims 1 to 12, wherein the inlet and outlet are located in a region of the chamber wall substantially perpendicular to the first axis of the first rotor.

14. A rotary drive device comprising a housing in which a first rotor and a second rotor are disposed, wherein the first rotor is rotatable about a first axis and has rotor elements projecting radially therefrom, the second rotor is rotatable in the opposite direction to the first rotor about a second axis parallel to the first axis, the second rotor has recesses capable of receiving the rotor elements, the first rotor, the second rotor and the housing define a chamber around the first rotor through which the rotor elements pass, the chamber has an inlet and an outlet through which fluid can enter and exit the chamber, and when the rotor elements engage with the recesses, the rotor elements substantially close both the inlet and the outlet simultaneously.

15. The apparatus according to claim 14, wherein the rotor element occupies a sector of about 60° to about 120° with respect to the axis of the first rotor.

16. The apparatus according to claim 15, wherein the rotor element occupies a sector of approximately 80° with respect to the axis of the first rotor.

17. The apparatus according to any one of claims 14 to 16, further comprising extensions to the inlet and / or outlet that further form a ventilation area.

18. A rotary drive device comprising a housing in which a first rotor and a second rotor are disposed, wherein the first rotor is rotatable about a first axis and has rotor elements projecting radially therefrom, the second rotor is rotatable in the opposite direction to the first rotor about a second axis parallel to the first axis, the second rotor has a recess capable of receiving the rotor elements, the first rotor, the second rotor and the housing define a chamber around the first rotor through which the rotor elements pass, the chamber has an inlet and an outlet through which fluid can enter and exit the chamber, and when the rotor elements engage with the recesses, the rotor elements substantially close both the inlet and the outlet simultaneously. The rotor element is The front surface that precedes the other parts of the rotor element during the rotation of the first rotor, the rear surface opposite to the front surface, and the outer surface that contacts or substantially contacts the wall of the chamber during the rotation of the first rotor, The outer front joint portion between the front surface and the outer surface of the rotor element, The outer rear joint portion between the rear surface and the outer surface of the rotor element, The inner front joint between the outer wall of the first rotor and the front surface of the rotor element, The inner rear joint between the outer wall of the first rotor and the rear surface of the rotor element, Defined by, The aforementioned recess is Walls spaced apart to receive the front and rear surfaces of the rotor element, and a floor that contacts or substantially contacts the outer surface of the rotor element when the rotor element is received in the recess, The inner front joint portion of the recess between the floor and the front wall of the wall, The inner rear joint portion of the recess between the floor and the rear wall of the wall, The outer front joint between the front wall of the recess and the outer wall of the second rotor, The outer rear joint between the rear wall of the recess and the outer wall of the second rotor, Defined by, At an engagement position where the outer front joint and the outer rear joint of the rotor element are equidistant from the line X connecting the axis of the first rotor and the axis of the second rotor, (a) The inner front joint and the inner rear joint of the rotor element are positioned next to a line extending from the axis of the first rotor and making an angle of approximately +37° and -37° with line X, The outer front joint and the outer rear joint of the rotor element are positioned next to lines extending from the axis of the first rotor and making angles of approximately +30° and -30° with line X. The inner front joint and the inner rear joint of the recess are positioned beside a line that extends from the axis of the second rotor and makes an angle of approximately +38° and -38° with line X. (b) The inner front joint, the inner rear joint, the outer front joint, and the outer rear joint of the rotor element are positioned next to lines extending from the axis of the first rotor and making angles of approximately +40° and -40° with line X, The inner front joint and the inner rear joint of the recess are positioned beside a line that extends from the axis of the second rotor and makes an angle of approximately +43° and -43° with line X. The outer front joint and the outer rear joint of the recess are positioned beside lines extending from the axis of the second rotor and making angles of approximately +46° and -46° with line X. (c) The inner front joint, the inner rear joint, the outer front joint, and the outer rear joint of the rotor element are positioned next to lines extending from the axis of the first rotor and making angles of approximately +40° and -40° with line X, The inlet is located within a line extending from the axis of the first rotor and making an angle of approximately +38° with line X. The outlet is located within a line extending from the axis of the first rotor and making an angle of approximately -39° with line X. The inner front joint and the inner rear joint of the recess are positioned beside a line that extends from the axis of the second rotor and makes an angle of approximately +45° and -45° with line X. The outer front joint and the outer rear joint of the recess are positioned beside a line extending from the axis of the second rotor and making an angle of approximately +53° and -53° with line X, or (d) The inner front joint, the inner rear joint, the outer front joint, and the outer rear joint of the rotor element are positioned next to lines extending from the axis of the first rotor and making angles of approximately +40° and -40° with line X, The inlet is located within a line extending from the axis of the first rotor and making an angle of approximately +38° with line X. The outlet is located within a line extending from the axis of the first rotor and making an angle of approximately -39° with line X. The inner front joint and the inner rear joint of the recess are positioned beside a line that extends from the axis of the second rotor and makes an angle of approximately +46° and -46° with line X. The outer front joint and outer rear joint of the recess are positioned next to a line extending from the axis of the second rotor and making an angle of approximately +53° and -53° with line X, respectively, in a rotary drive device.

19. The inner front joint, inner rear joint, outer front joint, and outer rear joint of the rotor element are positioned next to lines extending from the axis of the first rotor and making angles of approximately +40° and -40° with line X. The inlet is located within the zone in which the rotor element moves, and is positioned within a line extending from the axis of the first rotor and making an angle of approximately +38° with line X, while avoiding the zone in which the second rotor moves. The outlet is located within the zone in which the rotor element moves, within a line extending from the axis of the first rotor and making an angle of approximately -39° with line X, and avoids the zone in which the second rotor moves. The inner front joint and the inner rear joint of the recess are positioned beside a line that extends from the axis of the second rotor and makes an angle of approximately +45° and -45° with line X. The outer front joint and the outer rear joint of the recess are positioned beside a line that extends from the axis of the second rotor and makes an angle of approximately +53° and -53° with line X. The apparatus according to claim 18, wherein the space between the inlet and the outlet is defined alongside a line extending from the axes of both rotors and making an angle of approximately +15° and -15° with the line X.

20. The apparatus according to any one of claims 1 to 6 or 14 to 19, wherein the apparatus provides rotational energy to the first rotor or the second rotor to draw in fluid through the inlet and push out the fluid through the outlet means.

21. The apparatus according to claim 20, which is dependent on any one of claims 1 to 6, wherein the shoulder portion follows the rotor element and closes the outlet during a portion of the cycle of the first rotor.

22. Use of the apparatus according to claim 20 or 21 as a pump.

23. The use according to claim 22, wherein the fluid is air or an air / oxygen mixture, and the pump is a ventilator pump.

24. The apparatus according to any one of claims 14 to 19, further comprising an ignition means and configured to introduce a combustible fluid or a mixture of fluids through the inlet for combustion in order to supply energy to the rotor element.

25. Use of the apparatus according to claim 24 as a combustion engine.

26. Use of the apparatus according to any one of claims 7 to 19 as a turbine.

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