CONCENTRIC ROTARY MACHINE

TECHNICAL FIELD

In general, this invention relates to improvements in the rotary technology's design and operability described in the U.S. Pat. No. 8,001,949B2 patent application, the disclosure of which is herein incorporated by reference as if set forth in its entirety, finding application to various machine types, such as internal combustion engines, compressors, expanders, and pumps. The description below will focus on the compressors' technology, but the same design modifications and improvements can apply to all machine types mentioned above.

The current invention is related to a machine used as a compressor, expander, pump, part of an internal combustion engine, or a combination thereof. For instance, in the case of the compressor or expander, this machine needs no multiple-stage compression/expansion process; it is smaller and lighter than the conventional machines; compatible with all typical installations that would otherwise include a standard compressor/expander and with a higher energy economy during its operation.

Embodiments of the present invention are directed to a concentric rotary compressor that compresses any gaseous or liquid working fluid. In general, the compressor of the present invention can be used in conjunction with any working fluid; such as water, atmospheric air, refrigerants (e.g., R134a, R1234yf, R407c, R11, R12, R13, R21, R22, R23, R32, R41, R113, R114, R115, R116, R123, R124, R125, R141b, R142b, R143a, R152a), Organic Rankine cycle fluids (e.g., R245fa, R141b, R236fa, R218, R227ea, R236ea, R245ca, R365mfc, RC318), ammonia, propane, carbon dioxide, or any combination thereof. Certain embodiments of the compressor are described in greater detail below in conjunction with the accompanying drawings, as an exemplary embodiment. The same operating principle and embodiments are also applicable to describe the components and/or operation of a concentric rotary expander, a pump, and/or parts of an internal combustion engine. The embodiment of the compressor also describes the intake & compression process/chamber of an internal combustion engine, for example, as described in U.S. Pat. No. 8,001,949B2, incorporated herein in its entirety. Similarly, the expander can describe the combustion and expansion process/chamber of an internal combustion engine.

The working fluid compressed by the described compressor can be used in a wide variety of applications, including the compression of air and/or other fluids, solar and/or conventional cooling applications, desalination applications, refrigeration, Stirling engine applications, thermoelectric applications, internal combustion engine applications, turbomachinery applications, large scale steam turbine applications, power production applications, automobile driving power applications, and combinations thereof.

BACKGROUND ART

Compressors are commonly used mechanical devices for fluid compression and/or fluid circulation in hydraulic networks. Many prior art compressors are rotary compressors that rotate around a shaft and transfer mechanical energy to a working fluid, thereby increasing the fluid's potential energy. Some compressors also have blades typically enclosed in a hull or operate in direct contact with the environment. In addition to rotary compressors, there are reciprocating compressors used in industrial applications, which utilize the potential energy of a moving piston to compress the working fluid inside a cylinder. An exhaust valve can open and release the compressed working fluid when the desired compression level is attained in both compressors' types.

Conventional compressors such as these present a series of disadvantages. One such disadvantage is the inability to reach high compression levels without using multiple stages of compression. In other words, if a compressor today wants to reach a 20 bar compression, it has to use a 2-stage compression process. This limitation precludes more than one compressor for high compression levels, increasing the weight and size of the whole infrastructure and reducing the total installation's efficiency. Another disadvantage of conventional compressors is their high cost and complexity of construction. Further, for most conventional compressors, especially at high compression ratios, the cooling requirements make the lubrication of the compression chamber unavoidable. Consequently, conventional compressors are not considered suitable to compress working fluids, sensitive to contamination by the lubricant medium.

Accordingly, there is a need for a compressor that improves upon the disadvantages exhibited by conventional compressors, and mainly a compressor that minimizes the number of moving parts, compresses the working fluid more efficiently, does not require lubrication that would potentially contaminate the working medium, and reduces or eliminates the need for multiple stages of compression processes like the state-of-the-art compressors do. Avoiding multiple compression processes also gives the advantage of a lower weight and smaller size of the whole compression process infrastructure.

SUMMARY OF THE INVENTION

The current invention is related to a concentric rotary machine that can run as a compressor, expander, pump, or parts of an internal combustion engine for the intake-compression and/or combustion/expansion process. The type of the machine may depend on the working fluid that enters the intake port (1). For instance, if a high-pressure working fluid enters through the intake port into the chamber, the machine acts as an expander, having the high-pressure working fluid at its back. If a low-pressure or atmospheric gas enters through the intake port (1) into the chamber, then the machine acts as a pump or compressor. Depending on the position of the intake port, the piston may rotate counter-clockwise (FIG. 1-C) or clockwise (FIG. 1-D).

This rotary machine may have an isolator rotating at a plane perpendicular to the plane of the piston's circular orbit (see FIG. 1-A) or at the same or parallel plane with the piston's orbit (see FIGS. 1-C and D).

This machine needs no multiple stages to complete the compression/expansion process; it is smaller and lighter than the conventional machines used for the same processes; it is compatible with all typical installations that would otherwise include a standard compressor/expander/pump/internal combustion engine and with a higher energy economy.

In some embodiments, the rotary concentric machine (compressor, expander, pump, or internal combustion engine) comprises a shaft rotatable about an axis. In some embodiments, the machine includes a piston configured to rotate about said axis concentrically with the shaft. In some embodiments, the piston is coupled to the shaft. In some embodiments, the piston is coupled to a disc or rotor that coupled to the shaft. In some embodiments, a shell forms a chamber, wherein the piston is configured to rotate within the chamber. In some embodiments, there is an isolator configured to separate the chamber into a plurality of sub-chambers. In some embodiments, there is at least one outlet port. In some embodiments, there is at least one intake port, located on said shell. In some embodiments, there is at least one intake port on the at least one edge of said shaft.

Disclosed herein, in some aspects, is a rotary concentric machine comprising: a shaft rotatable about an axis, a piston that rotates on a circular orbit about said axis concentrically with the shaft, wherein the piston is coupled directly to a cylindrical surface of the shaft, thereby forming a piston-shaft assembly; a shell that forms a chamber, wherein the piston is configured to rotate within the chamber; an isolator configured to separate the chamber into a plurality of sub-chambers; at least one outlet port; and at least one intake port, located on said shell or on the at least one edge of said shaft.

Disclosed herein, in some aspects, is a rotary concentric machine comprising: a shaft rotatable about an axis, a piston that rotates on a circular orbit about said axis concentrically with the shaft, wherein the piston and a cylindrical surface of the shaft form a unitary component, thereby forming a piston-shaft part; a shell that forms a chamber, wherein the piston is configured to rotate within the chamber; an isolator that is configured to separate the chamber into a plurality of sub-chambers; at least one outlet port; and at least one intake port, located on said shell or on the at least one edge of said shaft.

Disclosed herein, in some aspects, is a rotary concentric machine comprising: a shaft rotatable about an axis, a piston that rotates on a circular about said axis concentrically with the shaft, wherein the piston is coupled to a disc or rotor that is coupled to the shaft, thereby forming a piston-disc or piston-rotor assembly; a shell that forms a chamber, wherein the piston is configured to rotate within the chamber; an isolator that is configured to separate the chamber into a plurality of sub-chambers; at least one outlet port; and at least one intake port, located on said shell or on the at least one edge of said shaft.

Disclosed herein, in some aspects, is a rotary concentric machine comprising: a shaft rotatable about an axis, a piston that rotates on a circular orbit about said axis concentrically with the shaft, wherein the piston and a disc or rotor form a unitary component that is coupled to the shaft, thereby forming a piston-disc or piston-rotor part; a shell that forms a chamber, wherein the piston is configured to rotate within the chamber; an isolator that is configured to separate the chamber into a plurality of sub-chambers; at least one outlet port; and at least one intake port, located on said shell or on the at least one edge of said shaft.

Described herein, in some aspects, is a rotary machine based on the above descriptions, further comprising one or more additional pistons, shafts, discs or rotors, shells, isolators.

In some embodiments, the rotary machine further comprises at least one intake port.

In some embodiments, for any rotary machine described herein, the intake port is placed the closest possible position to the isolator.

In some embodiments, for any rotary machine described herein, the intake port is placed at the side of the chamber that the RSP isolator opens; when it is rotating clockwise, the intake port is located at the right side of the chamber; when RSP isolator rotates counter-clockwise, the intake port is located at the left side of the chamber.

In some embodiments, for any rotary machine described herein, the intake port is significantly smaller compared to the piston's diameter.

In some embodiments, for any rotary machine described herein, the intake port has a rectangular shape with or without fillets around its corners and it is located close or tangential to the upper area of the chamber's walls.

In some embodiments, for any rotary machine described herein, the intake port has a circular shape and it is located in the middle of the intake chamber's sidewalls height.

In some embodiments, at least one intake port is significantly smaller than the piston. In some embodiments, at least one intake port has the shape of a circle with a diameter significantly smaller compared to the piston's diameter. In some embodiments, wherein at least one intake port has any shape or orientation that allows for trapping the pressure wave released from the compression chamber inside the intake chamber when the two chambers get into communication and enhances the free drag of the working fluid through the intake port at the backside of the piston.

In some embodiments, the shaft and the at least one disc have at least one internal canal each to provide the working fluid inside at least one intake chamber. In some embodiments, the shaft, at least one disc, and at least one piston has at least one internal canal each to provide the working fluid inside at least one intake chamber. In some embodiments, at least one shaft's internal canals have a big diameter near the shaft's edges and a smaller diameter at the point this canal communicates with at least one of the disc's internal canals.

In some embodiments, the internal canals of the shaft have blades adapted at the edges of the shaft.

In various embodiments, as shown in FIG. 6, FIG. 7, and FIG. 8, it uses at least one isolator (3) that separates periodically the main chamber into two sub-chambers, e.g., in the case of the compressor, the isolator (3) isolates the compression chamber from the intake chamber (FIG. 1). The isolators (3) may be a reciprocating Linear Sliding Port (LSP) or a Rotary Sliding Port (RSP).

Ideally, the RSP isolator (3) should be as big in diameter as possible (FIG. 9).

In some embodiments, at least one isolator is a linear sliding port. Its reciprocating motion periodically separates the chamber into two sub-chambers, where at least one piston rotates in those two sub-chambers. In this case, the periphery of the disc, where the pistons are coupled, has a cylindrical shape. In some embodiments, at least one isolator is a rotary sliding port. Its rotating motion periodically separates the chamber, where at least one piston is rotating in, into two sub-chambers. In that case, the periphery of the disc, where the pistons are adapted, has a curved shape that follows the shape of the periphery of the isolator. In some embodiments, there is at least one RSP and at least one LSP.

In some embodiments, the rotary machine further comprises a plurality of pistons coupled to the at least one disc or the shaft's cylindrical surface. In this case, the pistons are axis-symmetrically distributed on the disc's periphery to weight-balance the piston-disc assembly.

In some embodiments, a linear actuator controls the motion of at least one LSP. This linear actuator can comprise of a plurality of sub-actuators including at least first and second linear sub-actuators, each of the first and second sub-actuators comprising an elongate body with a longitudinal axis and a piston or other member configured and arranged for periodically reciprocating along the longitudinal axis between an unextended position and an extended position, the first and second linear sub-actuators being connected in series such that (a) the respective drives of the first and second linear sub-actuators reciprocate between their respective unextended and extended positions at the same time and along the same longitudinal axis, and (b) a total length of extension of the first and second linear actuators comprises a sum of extension lengths of each of the first and second sub-actuators.

In some embodiments, more than one linear actuator with the same or different lift-time is connected in series to lift at least one LSP, and the LSP's lift is based on the sum of the lifts of all linear actuators together.

In some embodiments, the first linear sub-actuator has a time for effecting extension from its unextended to its extended position that is the same as that of the second linear sub-actuator such that a time for effecting the total length of extension of the first and second linear actuators connected in series is the same as the time for effecting extension of one of the first and second sub-actuators.

In some embodiments, at least one of the plurality of linear sub-actuators is constructed and arranged such that, in the absence of an in series connection between the plurality of linear sub-actuators, an amount of time for effecting extension of the at least one linear sub-actuator would be longer than that for a remainder of the plurality of linear sub-actuators and such that, with the plurality of linear sub-activators connected in series, an amount of time for effecting the total length of extension of the plurality of sub-activators is the same as the time for effecting extension of the at least one linear sub-actuator.

In some embodiments, at least one of the plurality of linear sub-actuators has a length of extension from its unextended to its extended position that is shorter than that of a remainder of the plurality of linear sub-actuators such that a time for effecting the total length of extension is the same as the time for effecting extension of the said linear sub-actuator.

In some embodiments, the linear actuator according to claim 6, wherein at least one of the plurality of linear sub-actuators has a length of extension from its unextended to its extended position that is longer than that of a remainder of the plurality of linear sub-actuators such that a time for effecting the total length of extension is the same as the time for effecting extension of the said linear sub-actuator.

This linear actuator can be a component of any device that has a part that requires periodically reciprocating movement, wherein the part is connected at an end of the second sub-actuator to effect the periodically reciprocating movement. Such a device can be also a rotary concentric machine comprising of at least one shaft; at least one piston that rotates on a circular orbit concentrically located with the at least one shaft; a shell that forms at least one chamber, wherein the at least one piston is configured to rotate within the at least one chamber; at least one isolator configured to separate the chamber into a plurality of sub-chambers; and at least one outlet port.

In some embodiments, regardless of the number of pistons, there is only one RSP with one piston-passing hole and speed higher than the pistons'. In some embodiments, the rotary machine comprises only one RSP having a number of piston-passing holes equal to the number of the pistons, wherein the speed of the rotation of the RSP is equal to the piston's speed.

In some embodiments, the rotary machine further comprises a plurality of pistons and a plurality of RSPs, wherein the number of RSPs in the plurality of RSPs is equal to the number of pistons in the plurality of pistons, where all the pistons and the RSPs are axis-symmetrically located with each other.

In some embodiments, if there is a limitation in space, a group of three RSP isolators mechanism (10,11,12) may replace any single RSP isolator (3), as shown in FIG. 10. All of them have a minimum distance from each other. The middle RSP rotates with the shaft's angular velocity, but both outer RSPs rotate with a double angular velocity than the shaft does. Only one of the outer RSPs is rotating in the same direction with the middle one and the other rotates in the opposite direction. In some embodiments, the outer RSP that directly faces the high-pressure sub-chamber is thicker than the other two. In some embodiments, the middle RSP is thicker than the outer RSP that faces directly the lower in pressure sub-chamber. In some embodiments, at least one outer RSP has a different shape for the piston-passing hole than the middle one. In some embodiments, material is removed from at least one sidewall of the RSP to weight-balance the part. In some embodiments, the weight of all the pistons are minimized to facilitate weight balance of the disc-piston assembly.

Described herein, in some aspects, is a method to weight-balance a rotating part or assembly with a through-all hole is to remove material from at least one of its sidewalls opposite to the through-all hole's position.

Described herein, in some aspects, is a method to weight-balance a rotating part or assembly with a through-all hole is to replace part of its material with a heavier material at least at one of its sidewalls close to the through-all hole's position.

Described herein, in some aspects, is a method to weight-balance a rotating part or assembly having an extra mass on its periphery that causes the part's or assembly's center of mass to move out of a respective rotation axis, the method comprising: removing material from the part or assembly at an opposite location of the extra mass; and adding a heavier material in the location.

Described herein, in some aspects, is a method to weight-balance a part or assembly having an extra mass on its periphery, the method comprising: removing material close to a location of the extra mass, wherein an area corresponding to the material removal may comprise of two symmetrical or asymmetrical areas compared to a symmetry-axis of the part or assembly.

For any method described herein, the method further comprises: locating one or more parts at the sidewalls of the part or assembly (perpendicular to the rotation axis) each having at least one material removal area configured to move the center of mass of the assembly at its rotation axis, wherein the material removal areas on each part may optionally be symmetrical or asymmetrical to each other.

In some embodiments, for any rotary machine described herein, the isolators/RSPs and pistons-disc assemblies are weight-balanced with any one method described herein or any combination of methods described herein.

In any case, since this machine runs at high speeds, its critical rotating components (disc-piston assembly (2, 8) and the RSP isolator (3)) have to be weight-balanced by either removing or adding extra material (17, 19, 24, 23), like FIG. 11, FIG. 15 and FIG. 16 show.

In some embodiments, for any method to correct the weight-balance of the rotating part or assembly described herein, material is added at the areas of removed material.

In some embodiments, for any method to correct the weight-balance of the rotating part or assembly described herein, material is added at the areas of the piston that material has been removed to make it lighter.

Described herein, in some aspects, is a labyrinth sealing method for liquid and gaseous working fluids, comprising of at least one metal or non-metal labyrinth fin or knife (e.g., as shown in FIG. 10); a layer of a softer metal or non-metal material; where the free edges of the fins or knives come into contact or forced contact with the softer metal or non-metal material during the assembling of the labyrinth seal. The fins or knives, as well as the layer, may be both stationary or rotating parts or one stationary and the other rotating. In some embodiments, at least one screw that moves the knives or fins far from the layers and, at least one screw that moves them close to the layers arrange the distance between the fins or knives and the layers. In some embodiments, there is at least one hole on the stationary part and at least one leading wall on the rotating part to protect the bearings of a possible sealing malfunction, by preventing any high-pressure leakage at the end of the sealing system to go against the bearings and, wherein the leading wall leads the leaked high-pressure working fluid through the holes directly to the environment.

Described herein, in some aspects is a gaseous or liquid sealing method between a first stationary and a second moving wall or machine component that is created by constructing the stationary wall with very low roughness, the moving wall with a very high roughness (N11 or N12), and putting them at a distance of less than about 1 mm; 50 microns to 100 microns for small applications and up to 1 mm for heavy-duty large applications. The second machine component or wall can even be rotatable relative to the first stationary machine component about an axis. In that case, the surface roughness of the first machine component is sufficiently low, the surface roughness of the second machine component is sufficiently high and the gap is sufficiently small such that leakage of working medium passing through the gap is less than 3% (3% mass loss or 3% pressure loss. It depends on what is the application's most critical parameter). More precisely, the first machine component has a surface roughness that does not exceed N10, and the second machine component has a surface roughness that is at least N11, preferably N12, and most preferably more than N12 (Ra>50 micrometer).

Described herein, in some aspects, is a gaseous or liquid sealing method between a stationary and a moving wall that is created by constructing the stationary wall with very low roughness, and on the rotating wall's surface (internally or externally) are configured very thin knives or fins, wherein free edges of the knives or fins teeth are very close to the stationary wall, less than about 1 mm; 50 microns to 100 microns for small applications and up to 1 mm for heavy-duty large applications. In some embodiments, the knives or fins are not perpendicular to the outer surface of the rotating wall but in angular orientation.

In some embodiments, for any rotary machine described herein, no piston rings are located around the piston to seal the gap between the piston and the internal surface of the chamber, wherein, the leakage between these two components is limited by keeping a gap of less than about 1 mm between the piston's sidewall and the housing and by rotating the piston at a very high speed, either by a high shaft's speed, by rotating the piston on a circular orbit of a very high diameter, or the combination of the two. In some embodiments, for any rotary machine described herein, the pistons' sidewall may be toroidal or cylindrical. In some embodiments, for any rotary machine described herein, the isolators seal the sub-chambers by having their moving walls at a less than 1 mm distance from the stationary walls of the housing; 50 microns to 100 microns for small applications and up to 1 mm for heavy-duty large applications.

In some embodiments, for any rotary machine described herein, the walls of the chambers and the isolators' housing are the thinnest possible, due to cooling purposes and to minimize their thermal expansion, so that the gap between the rotating and stationary parts does not increase significantly due to the thermal expansion of the materials.

In some embodiments, for any rotary machine described herein, the material of the main rotating parts (pistons, disc, and isolators) should have a higher thermal expansion than the housing material around them to prevent the gap between the rotating and stationary parts from increasing significantly due to the thermal expansion of the materials.

Described herein, in some aspects, is a labyrinth sealing method for liquid and gaseous working fluids, comprising of at least two labyrinths systems in fluid communication, at least one having a vertical configuration, and at least one having a horizontal configuration (e.g., as shown in FIG. 17); and at least one shaft seal or seal ring (such as PTFE shaft seals) operatively coupled with at least one of the two labyrinth systems and configured to prevent or reduce the amount of the working fluid from escaping to the environment or to protect other components (e.g., bearings) from the high-pressure of the working medium. In some embodiments, at least one labyrinth system comprises a small gap in the entrance of a labyrinth chamber that leads the working medium towards a curved wall within the labyrinth chamber. In some embodiments, the curved wall leads the working medium to contact an opposite wall and optionally pass through a second small gap having an orientation that may be tangential to the end of the curved wall, and is optionally located at a minimum distance from the end of the curved wall wherein the labyrinth chamber and a second labyrinth chamber comprises a parallel configuration (for example, labyrinth chambers shown in FIG. 22). In some embodiments, this parallel orientation and the small size of the gap delays the working medium to pass through the second gap and enter the next labyrinth's chamber. In some embodiments, this configuration is repeated one or more times (e.g., one or more additional labyrinth chambers) so as to lower the fluid's pressure at the desired levels.

Disclosed herein, in some aspects, is a labyrinth sealing system for liquid and gaseous working fluids between two rotating or two stationary parts, or a stationary and a rotating part, comprising of at least one labyrinth system; and at least one shaft seal or seal ring (such as PTFE shaft seals) operatively coupled with the at least one labyrinth system and configured to prevent or reduce the amount of the working fluid from escaping to the environment and/or to protect other components from the high-pressure of the working medium.

Disclosed herein, in some aspects, is a labyrinth sealing system for liquid and gaseous working fluids between two rotating or two stationary parts, or a stationary and a rotating part, comprising of at least two labyrinths systems in fluid communication, at least one having a vertical configuration, and at least one having a horizontal configuration (e.g., as shown in FIG. 22); and at least one shaft seal or seal ring (such as PTFE shaft seals) operatively coupled with at least one of the two labyrinth systems and configured to prevent or reduce the amount of the working fluid from escaping to the environment and/or to protect other components from the high-pressure of the working medium.

In some embodiments, where at least one labyrinth system comprises a small gap in the entrance of a labyrinth chamber that leads the working medium towards a curved wall within the labyrinth chamber; wherein the curved wall leads the working medium to contact an opposite wall and optionally pass through a second small gap having an orientation that is optionally tangential to the end of the curved wall, and is optionally located at a minimum distance from the end of the curved wall, wherein the labyrinth chamber and a second labyrinth chamber comprises a parallel configuration (for example, labyrinth chambers shown in FIG. 22), and the small size of the second gap delays the working medium to pass through the second gap and enter the second labyrinth's chamber.

In some embodiments, where the orientation to the end of the curved wall is not tangential but has an opposite slope than the fluid's stream direction or is perpendicular to the fluid's stream direction.

In some embodiments, where the limited space close to the shaft seal or ring does not allow for a vertical labyrinth and the latter is replaced by a wall between the high-pressure working medium and the seal ring/shaft seal.

In some embodiments, where the limited space close to the shaft seal or ring does not allow for a vertical labyrinth and the latter is replaced by a washer or a ring-shaped part and a retaining ring between the high-pressure working medium and the seal ring/shaft seal.

In some embodiments, where the one of the two parts (rotating and/or stationary) to seal has a softer material than the other, so as to protect the labyrinth system design in case of a potential contact between the two parts.

In some embodiments, where the two parts (rotating and/or stationary) to seal have initially no gap between them but the labyrinth system is used to seal a potential gap between them, wherein the one of the two parts has a softer material than the other.

In some embodiments, for any rotary machine described herein, the rotation radius of the compression piston is the maximum possible.

In some embodiments, for any rotary machine described herein, at least one linear or rotating Sliding Port's periphery is non-cylindrical and optionally creates a labyrinth with the chamber's walls (see FIG. 17).

In some embodiments, for any rotary machine described herein, the stationary housing is divided into as many parts as the number of different planes where the assembly's shafts are located, including the machine's main shaft and any auxiliary shafts used to move gears, isolators, and pistons. In some embodiments, for any rotary machine described herein, at least one housing part of each pair of housing parts that come in contact through a flange has a protrusion along its interior configurations to prevent any leakage around the sealing flange or any intersection of the sealing flange with the moving parts.

In other embodiments, the at least one piston-passing hole (15) that the RSP (3) may have for the piston (2) (see e.g., FIG. 1) to pass through its body may be the smallest possible (see FIG. 11-A) or wider (FIG. 11-B). Alternatively, the RSP (3) may have also at least one internal cavity configuration (73) near or adjacent to said piston-passing hole (15) in fluid communication with said piston-passing hole (15) inside the main body of the RSP (3) (FIG. 11-C).

In some embodiments, for a rotary machine described herein, the RSP defines a receptacle configured to receive the piston wherein this receptacle may have a larger size than the piston's size requires and/or the RSP has a cavity configuration in fluid communication with said receptacle. In some cases, the role for either of these designs is to reduce pressure build-up at the front side of the piston when the piston is entering into said receptacle along its rotation on the circular orbit. In some embodiments, said extra space (74) (e.g., see FIG. 11-C) of a larger receptacle or said cavity configuration (73) has an orientation to favor the expansion of a trapped working fluid between the piston and the RSP. In some embodiments, said extra space (74) of a larger receptacle or said cavity configuration (73) has an opening opposite to the piston's front side, when the piston reaches a periphery of the RSP. In some embodiments, said extra space (74) of a larger receptacle or said cavity configuration (73) has a bigger size than said piston. In some embodiments, an area corresponding to the extra space (74) of a larger receptacle or cavity configuration (73) of the RSP may comprise of two symmetrical or asymmetrical areas (75α and 75β) about a symmetry or rotation axis of the RSP. In some embodiments, the area corresponding to the extra space (74) of a larger receptacle or cavity configuration (73) of the RSP may comprise of two asymmetrical areas about a symmetry-axis or rotation-axis of the RSP, wherein the largest area of said extra space (74) of a larger receptacle or said cavity configuration (73) may be located close to an area of the RSP where high pressure is developed.

The area corresponding to the extra space (74) of a larger receptacle or to the material removal of said cavity configuration (73) may comprise of two symmetrical or asymmetrical areas (75α and 75β) compared to a “symmetry” plane or a symmetry- or rotation-axis of the RSP's part or assembly.

In other embodiments, the area corresponding to the extra space (74) of a larger receptacle or to the material removal of the cavity configuration (73) may comprise of two asymmetrical areas compared to a “symmetry” plane or a symmetry- or rotation-axis of the RSP's part or assembly, wherein the largest area (75α) of said extra space (74) or cavity configuration (73) may be located close to the area (76) where high pressure is developed on the RSP.

In some embodiments, there is at least one cavity configuration (e.g. 8 or 10 or 12 in FIG. 19) that serves as a weight balance configuration for a piston-disc or piston-rotor assembly (e.g. 7 or 9) or a piston-disc or piston-rotor part (e.g. 14). In other embodiments, said cavity may also be close to areas of high temperature (11α) and serve as a cooling mean for those areas.

In some embodiments, for a rotary machine described herein, the piston-shaft assembly or part has at least one cavity configuration serving as a weight balance configuration, wherein said cavity has an inclination compared to a horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane (like the one shown in FIG. 19-D) in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, and wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part.

In some embodiments, for a rotary machine described herein, the piston-shaft assembly or part has at least one cavity configuration serving as a weight balance configuration, wherein the area corresponding to the cavity may comprise of two asymmetrical areas about a “symmetry” plane or a symmetry- or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, and wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part.

In some embodiments, for a rotary machine described herein, the piston-shaft assembly or part has a cavity configuration close to areas of the assembly or part where high temperature is developed to create walls with a thickness that favors faster cooling of those hot areas.

In some embodiments, for a rotary machine described herein, the piston-shaft assembly or part has a cavity configuration with a double role: to weight balance the piston-shaft assembly or part and also to cool areas where high temperature is developed, by having an inclination compared to a horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane (like the one shown in FIG. 19-D) in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, wherein material removal of the assembly or part is avoided from areas where such weight of the material is necessary to counterbalance the assembly or part; and wherein expanding the cavity configuration close to areas of the assembly or part where high temperatures are developed, the cavity configuration creates walls with a thickness that favors faster cooling of those hot areas.

In some embodiments, for a rotary machine described herein, the piston-shaft assembly or part has a cavity configuration with a double role: to weight balance the piston-shaft assembly or part and to cool areas where high temperature is developed, where the area corresponding to the cavity may comprise of two asymmetrical areas about a “symmetry” plane or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part; and wherein expanding the cavity configuration close to areas where high temperatures are developed create walls with a thickness that favors faster cooling of those hot areas.

In some embodiments, for a rotary machine described herein, the piston-disc or piston-rotor assembly or part has at least one cavity configuration serving as a weight balance configuration, wherein said cavity has an inclination compared to a horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane (like the one shown in FIG. 19-D) in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, and wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part.

In some embodiments, for a rotary machine described herein, the piston-disc or piston-rotor assembly or part has at least one cavity configuration serving as a weight balance configuration, wherein the area corresponding to the cavity may comprise of two asymmetrical areas about a “symmetry” plane or a symmetry- or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, and wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part.

In some embodiments, for a rotary machine described herein, the piston-disc or piston-rotor assembly or part has a cavity configuration close to areas of the assembly or part where high temperature is developed to create walls with a thickness that favors the faster cooling of those hot areas.

In some embodiments, for a rotary machine described herein, the piston-disc or piston-rotor assembly or part has a cavity configuration with a double role: to weight balance the piston-disc or piston-rotor assembly or part and also to cool areas where high temperature is developed, by having an inclination compared to a horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane (like the one shown in FIG. 19-D) in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part; and wherein expanding the cavity configuration close to areas of the assembly or part where high temperatures are developed, the cavity configuration creates walls with a thickness that favors faster cooling of those hot areas.

In some embodiments, for a rotary machine described herein, the piston-disc or piston-rotor assembly or part has a cavity configuration with a double role: to weight balance the piston-shaft assembly or part and to cool areas where high temperature is developed, where the area corresponding to the cavity may comprise of two asymmetrical areas about a “symmetry” plane or a symmetry- or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part; and wherein expanding the cavity configuration close to areas where high temperatures are developed create walls with a thickness that favors faster cooling of those hot areas.

Disclosed herein, in some aspects, is a method to counter balance an assembly or part of a rotary machine, by creating a cavity configuration inside the body of the assembly or part, wherein said cavity has an inclination compared to a horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane (like the one shown in FIG. 19-D) in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, and wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part.

Disclosed herein, in some aspects, is a method to counter balance an assembly or part of a rotary machine by creating a cavity configuration inside the body of the assembly or part, wherein the area corresponding to the cavity may comprise of two asymmetrical areas about a “symmetry” plane or a symmetry- or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, and wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part.

Disclosed herein, in some aspects, is a method to counter balance an assembly or part of a rotary machine by creating a cavity configuration inside the body of the assembly or part, wherein said cavity is close to areas where high temperature is developed to create walls with a thickness that favors faster cooling of those hot areas.

Disclosed herein, in some aspects, is a method to counter balance an assembly or part of a rotary machine by creating a cavity configuration inside the body of the assembly or part with a double role: to weight balance the assembly or part and also to cool areas of the assembly or part where high temperature is developed, where the area corresponding to the cavity may comprise of two asymmetrical areas about a “symmetry” plane or a symmetry- or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part; and wherein expanding the cavity configuration close to areas where high temperatures are developed create walls with a thickness that favors faster cooling of those hot areas.

In some embodiments, for a rotary machine described herein, further comprising one or more additional pistons, shafts, disc or rotors, shells, and/or isolators/RSPs.

BRIEF DESCRIPTION OF THE FIGURES

In the Figures, reference characters generally refer to the same parts throughout the different views. Also, the Figures are not necessarily to scale; emphasis is instead generally placed upon illustrating the principles of the invention. In the following description, various embodiments of the present invention are described with reference to the following Figures.

FIG. 1 depicts a schematic 3D illustration of an exemplary operating principle of a concentric rotary compressor/expander/pump that can work with any gaseous working fluid, according to an embodiment described herein. FIG. 1 (A) shows the machine's exterior with a configuration that the isolator's motion is on a plane perpendicular to the piston's rotation axis, and FIG. 1 (B) shows the same view but with the housing cross-section to make the machine's moving parts visible. FIG. 1 (C and D) shows the ability of the rotary machine to operate clockwise and counter-clockwise and with the isolator's motion being on the same plane with the piston's circular orbit (parallel to the piston's rotation axis.

FIG. 2 shows an exemplary depiction of different shapes and positions for the intake port, according to an embodiment described herein. Images C and D indicate that the intake port's position depends on the rotation direction of the RSP. The intake port is better to be located at the sidewall of the chamber where the RSP first exposes the intake chamber to the compression chamber (85) so that they get into fluid communication.

FIG. 3 is a schematic 2D illustration of an exemplary shape and size of the intake port (1), as well as it shows how the intake port limits the Compression Ratio, according to one embodiment. As shown in FIG. 3, the existence of the intake port (1) limits the minimum angle φ that the intake process can start. In addition to or in an alternate embodiment, by replacing the intake port (1) with an internal canal that passes through the shaft's, disc's and piston's body, the intake process can start earlier.

However, CFD simulations (“Converge CFD” solver) showed that this design can work efficiently only if there is a one-way valve at the backside of the piston (idea Savvas Savvakis).

FIG. 4 is a schematic 3D illustration of an exemplary shaft internal canal design (34) to increase the mass flow rate of intake air, according to one embodiment. FIG. 4 shows the shape of an internal canal (34) that enhances the pistons' internal cooling (e.g., see U.S. Pat. No. 8,001,949B2, which is incorporated herein in its entirety), according to an embodiment described herein. In some cases, the same internal canals may also replace the intake port (1).

FIG. 5 is a schematic 2D illustration of exemplary internal canals (39) that can replace the intake port (1) and supercharge the intake chamber (4), according to an embodiment described herein. Those canals may pass through the piston (2), and then the intake-fluid enters the intake chamber (4) through the backside of the piston (2) (which may cool the piston) or passing only through the shaft (7), and the disc (8) and then the intake-fluid enters the same chamber at the backside of the piston (2).

FIG. 6 is a schematic 3D illustration of exemplary main moving parts when one or more linear sliding ports (LSP (3)) control the isolation of the chambers.

FIG. 7 is a schematic 3D illustration of an exemplary linear actuator (9) that can move the LSP (3), according to two different embodiments; the LSP (3) consisting of a single linear actuator (A) or a plurality of linear actuators (B).

FIG. 8 is a schematic 3D illustration of exemplary main moving parts when the isolator is a Rotary Sliding Port (RSP (3)), according to four different exemplary embodiments: Single piston, single RSP with a single piston-passing hole (FIG. 8-A); two pistons and two piston-passing holes on single RSP (FIG. 8-B); single piston-passing hole on single RSP and two pistons (FIG. 8-C); and two pistons and two RSPs each with a single piston-passing hold (FIG. 8-D).

FIG. 9 is a schematic 3D illustration of two exemplary alternative RSP (3) sizes for the same embodiment, according to an embodiment described herein, depicting the two sizes as superimposed against each other (A) and perspective views of both (B).

FIG. 10 is a schematic 3D illustration of using triple RSP (10,11,12) instead of a single RSP (3), according to one embodiment, with the triple RSP depicted as together (A) and an exploded view of the three RSPs separated (B).

FIG. 11 is a schematic 3D illustration of exemplary weight balancing of the RSP (3) for three alternative piston-passing hole configurations (A)-(C), according to an embodiment described herein.

FIG. 12 is a schematic diagram of the pressure developed during one operating cycle of said compressor at the front side of the piston (2) with and without said cavity configuration (73) on the RSP, and a 3D visualization of the pressure field for said compressor with and without said cavity configuration (73) on the RSP, at the end of the compression process, according to an embodiment described herein. In some cases, a design like the one of FIG. 11 (B) gives similar pressure results with the design of FIG. 11 (C).

FIG. 13 is a schematic 3D illustration of dividing an exemplary housing into parts (40, 41, 42, 43) (A) for easy assembling and controlling the dimensions of the sealing gaps. In some emobiments, the number of planes where at least one of the assembly's shafts is located defines the number of parts. In some embodiments, these shafts include the machine's main shaft (7) (B) and any auxiliary shaft used to move gears, isolators, or pistons. The resulting final design (C) is depicted after removing the unnecessary material to make the chamber and SP housing as thin as possible, according to an embodiment described herein.

FIG. 14 is a schematic 3D illustration of an exemplary way the housing parts are tightly adjusted with each other through flanges (46) and the problems that may occur if the leap (44) does not support the flange, and therefore the leap has the shape of flange (45), according to an embodiment described herein. In some embodiments, to seal the parts with each other, there is a small leap (44) along the interior configurations of each housing's part and a flange (46) of an isolating material like PTFE to prevent any leakage of the working fluid between any pair of tightly adjusted neighboring housing parts.

FIG. 15 is a schematic 3D illustration of weight balancing the piston-disc assembly (2, 8), according to three embodiments (three different piston designs).

FIG. 16 is a schematic 3D illustration of exemplary alternative ways (A), (B) to weight-balance the piston-disc (2, 8) assembly, according to an embodiment described herein.

FIG. 17 shows an exemplary depiction of the weight-balancing method of a rotary sliding port, according to embodiment described herein.

FIG. 18 shows an exemplary depiction of the weight-balancing method of the piston-disc assembly, according to an embodiment described herein.

FIG. 19 (A-D) depict exemplary schematic 3D illustrations of the piston-disc or piston-rotor assembly (66 or 68) or piston-disc or piston-rotor part (72) with three alternative weight balance configurations (67, 69, 71).

FIG. 20 is a schematic 3D illustration of exemplary air-sealing methods and designs used in the compressor/expander/pump/internal combustion engine, according to three embodiments. It shows different labyrinth fins (26) (A, C) and knives (26) (B) for sealing the piston-disc and RSP with the housing.

FIG. 21 is an exemplary schematic 2D illustration of how the bearings (32) are protected in the case of an air-sealing malfunction, according to one embodiment. In some embodiments, there is a leading wall (33) on the rotating parts and at least one hole (31) on the stationary housing to protect the bearings (32) from malfunction or insufficient sealing of the labyrinth seal (26-27).

FIG. 22 shows an exemplary depiction of three combinations (A), (B), (C) of labyrinth seals with shaft seals (47) to seal a gap between two parts, in this example, a rotating (27) and a stationary part (26), according to an embodiment described herein.

FIG. 23 shows an exemplary depiction of two alternative combinations of labyrinth seals with shaft seals (47) to seal a gap between two parts, in this example, a rotating (27) and a stationary part (26), as well as the use of a labyrinth on the periphery of the RSP, according to an embodiment described herein.

DETAILED DESCRIPTION

In various embodiments, the compressor described here may be connected serially with a second compressor to increase the output pressure of the working fluid.

Each numerical value presented herein, for example, in a table or a chart, is contemplated to represent an exemplary value in a range for a corresponding parameter. Accordingly, when added to the claims, the numerical value provides support for claiming a range around that value, which may lie above or below the numerical value, according to the teachings herein. Absent inclusion in the claims, each numerical value presented herein is not to be considered limiting in any regard.

The terms and expressions employed herein are used as terms and expressions of description and not of limitation. In using such terms and expressions, there is no intention of excluding any equivalents of the features shown and described or portions thereof. In addition, having described certain embodiments of the invention, it will be apparent to those of ordinary skill in the art that other embodiments incorporating the concepts disclosed herein may be used without departing from the spirit and scope of the invention. The various embodiments' structural features and operational functions may be arranged in various combinations and permutations, and all are considered to be within the scope of the disclosed invention. Accordingly, the described embodiments are to be considered in all respects as only illustrative and not restrictive. Furthermore, the configurations, materials, and dimensions described herein are intended as illustrative and in no way limiting. Similarly, although physical explanations have been provided for explanatory purposes, there is no intent to be bound by any particular theory or mechanism or to limit the claims in accordance therewith.

All simulations were based on BETA CAE Systems software (ANSA, META, and neere) and CONVERGENT SCIENCE solver (CONVERGE CFD).

Embodiments of the present invention are directed to a concentric rotary compressor that compresses any gaseous or liquid working fluid. In general, the compressor of the present invention can be used in conjunction with any working fluid; such as water, atmospheric air, refrigerants (e.g., R134a, R1234yf, R407c, R11, R12, R13, R21, R22, R23, R32, R41, R113, R114, R115, R116, R123, R124, R125, R141b, R142b, R143a, R152a), Organic Rankine cycle fluids (e.g., R245fa, R141b, R236fa, R218, R227ea, R236ea, R245ca, R365mfc, RC318), ammonia, propane, carbon dioxide, hydrogen and combinations thereof. Certain embodiments of the compressor are described in greater detail below in conjunction with the accompanying drawings. The same operating principle and embodiments are also applicable to describe the components and/or operation of a concentric rotary expander, pump, and/or parts of an internal combustion engine. The embodiment of the compressor also describes the intake and compression process/chamber of an internal combustion engine, for example, as described in the first patent application (U.S. Pat. No. 8,001,949B2). Similarly, the expander can describe the combustion & expansion process/chamber of an internal combustion engine.

In the first embodiment, depicted in FIG. 1, the operating principle of a compressor/expander/pump or parts of an internal combustion chamber is described.

FIG. 1 depicts an exemplary rotary machine. In some embodiments, wherein the machine of FIG. 1 receives through the intake port (1) a low-pressure or atmospheric working fluid, then FIG. 1 depicts an embodiment of a compressor or a pump. In the case of said compressor, an isolator (e.g., (3)) in combination with piston (2) is configured to separate a chamber (within which the piston (2) is rotating) into two sub-chambers: the compression chamber (4α) and the intake chamber (4β). When the isolator (3) closes the path of the piston (2), the piston (2) compresses the fluid trapped between its front side and the closed isolator (3). Once the pressure of the working fluid within the compression chamber (4α) reaches a desirable level, a valve at the outlet port (6) opens to allow for transferring the compressed working fluid to a storage or dampener tank (in the case of a compressor) or to a high-pressure tank assembly in the case of an internal combustion engine.

In various embodiments, the rotary machine may be a compressor that uses at least one piston (2) to divide with the help of an isolator (3) its main chamber into two sub-chambers: a compression chamber (in FIG. 1-(B and C), chamber 4α, or in FIG. 1-D, chamber 5α), where the working fluid is compressed, and an intake chamber (in FIG. 1-(B and C), chamber 4β, or in FIG. 1-D, chamber 5β). At the back of said piston (2) is the said intake chamber and at its front side the said compression chamber.

In other embodiments, the expander uses at least one piston (2) that divides its main chamber into two sub-chambers: an expansion chamber (in FIG. 1-(B and C), chamber 4β, or in FIG. 1-D, chamber 5β), where the working fluid is expanded, and a fluid-removal chamber (in FIG. 1-(B and C), chamber 4α, or in FIG. 1-D, chamber 5α). At the back of said piston (2) is said expansion chamber and at its front side the said exhaust chamber.

In some embodiments, wherein the machine of FIG. 1 receives through the intake port (1) a low-pressure or atmospheric working fluid, then FIG. 1 depicts an embodiment of a compressor or pump. In the case of the compressor, an isolator (e.g., (3)) periodically closes and separates the chamber (where the piston (2) is rotating) into two sub-chambers, the compression chamber (in FIG. 1-(B and C), chamber 4α, or in FIG. 1-D, chamber 5α) and the intake chamber (in FIG. 1-(B and C), chamber 4β, or in FIG. 1-D, chamber 5β). When the isolator (3) or, in this case, Rotary Sliding Port (3) (RSP) closes, the piston (2) compresses the fluid trapped between its front side and the closed isolator. Once the pressure of the working fluid within the compressor chamber (in FIG. 1-(B and C), chamber 4α, or in FIG. 1-D, chamber 5α) reaches a desirable level, a valve at the outlet port (6) opens to allow for the transfer of the compressed working fluid to a storage or dampener tank. In some embodiments, where the machine is part of an internal combustion engine, the compressed working fluid is sent to the combustion chamber, as described in the U.S. Pat. No. 8,001,949B2. This paragraph describes an exemplary complete cycle of the operation of the compressor of the present invention. Subsequently, the cycle may be repeated, as identified in FIG. 1.

In the pump case, the piston (2) drags the low-pressure or atmospheric fluid at its backside and, in parallel, pushes at its front side the working fluid dragged during the previous operation cycle towards the outlet port (6). So, it transfers the working fluid to the desired location/space (pump's operating principle). This paragraph describes an exemplary complete cycle of the operation of the pump of the present invention. Subsequently, the cycle may be repeated, as identified in FIG. 1.

In some embodiments, wherein the machine of FIG. 1 receives through the intake port (1) a high-pressure working fluid, then FIG. 1 depicts an embodiment of the expander. In this case, the piston (2) takes motion from the expanding working fluid at its backside and gives motion to the shaft (7). At the same time, the piston (2) transfers through the outlet port (6) the expanded fluid of the previous operation cycle to the environment or another device (e.g., a storage, buffer, or dampener tank). This paragraph describes an exemplary complete cycle of the operation of the expander of the present invention. Subsequently, the cycle may be repeated, as identified in FIG. 1.

In some embodiments, at least one piston (2) can be coupled to (for example, in some cases, attached directly), the cylindrical surface of the shaft (7) or at a distance from the cylindrical surface of the shaft (7). In the latter case, for example, at least one piston (2) can be coupled (for example, attached) at the periphery of a disc (8). In some cases, the disc (8) is firmly coupled to the shaft (7).

As shown in FIG. 17, if the piston-pass gap is large enough that the region (17) of removed material is not enough to weight-balance the body of the RSP isolator, a heavier material (61) such as lead can be used in some areas of the body around the piston-pass gap.

As shown in FIG. 18, even in the case of the main shaft, a heavier material (62) may replace part of the body to weight-balance the body without the use of areas of removed material such as described in FIG. 15 and FIG. 16. In both cases, during the testing of the weight balance of the bodies, material may be added at the areas of removed material (17) (FIG. 17) or (62) (FIG. 18) to correct the mass center of the assembly.

In some embodiments, with respect to FIG. 2, the intake port may be rectangular with or without fillets around the corners (63) or circular (64). In the rectangular case, the intake port (63) may be close or tangential to the upper area of the chamber's walls. In the second case, the circular intake port (64) gives better results if it is placed in the center of the chamber.

In some embodiments, when the intake port is placed closest possible to the isolator, the peak pressure becomes higher.

In some embodiments, when the intake port is significantly smaller compared to the piston's diameter, the peak pressure becomes higher.

In some embodiments, when the intake port is placed opposite to the sidewalls of the intake chamber that the RSP isolator opens the communication of the compression and intake chamber (position 75 in FIG. 2-C and D), the peak pressure becomes higher. For instance, when the RSP isolator rotates counter-clockwise and its piston-pass gap meets first the left sidewalls of the intake chamber (position 75 in FIG. 2-C), the intake port is located at the right sidewalls of the chamber. In other embodiments, where the RSP isolator rotates clockwise, the intake port will be located at the left sidewalls of the intake chamber (position 75 in FIG. 2-D).

In some embodiments, according to the initial patent application (U.S. Pat. No. 8,001,949B2—see FIGS. 15-19, 21), the pistons and the shaft and the moving arms may have internal canals to cool the pistons by feeding environmental air through the interior of the pistons. In addition to that idea, the internal canal (34) that passes through the shaft (35) may have a big diameter at the shaft's edges (36) and a smaller diameter at the place that the shaft's canal (34) communicates with the motion arm's or disc's canal (37) [area (38)]. The different cross-section diameters accelerate the air-stream and increase the mass flow rate so that the cooling becomes through the convection phenomenon more efficient (FIG. 4).

In other embodiments, the same design may also have blades adapted at the edges of the shaft to accelerate the air dragged through the internal canals even more and supercharge the machine which increases the output pressure.

In other embodiments, contrary to the initial patent's idea, there is no intake port. The internal canals may replace the intake port and let the intake air enter the intake chamber (4) only through internal canals (39) that pass through the shaft (7) and the disc (8) (left design in FIG. 5). The absence of an intake port results in a higher compression ratio (CR) because the lack of an intake port avoids the geometrical limitation of the compression's starting angle. As shown in FIG. 3, if there is an intake port (1), the compression process cannot start until the piston (2) passes the angle φ where the intake port (1) stops to feed air at the front side of the piston (2). Moreover, like CFD simulations have shown (based on the software “Converge CFD”), the use of internal canals instead of intake ports lowers the drag at the backside of the piston because, with those canals, the pressure does not fall under 1 bar.

In other embodiments, the internal canals (39) pass only through the shaft (7), the disc (8), and the piston (2), leading the intake air at the backside of the piston and not through the piston (right design in FIG. 5). This design allows for using bigger diameters for the internal canals, and it is more favorable for higher speeds. In some cases, the design through the piston cools the piston better.

In some embodiments, with a machine having internal canals and no intake port can also supercharge the intake chamber (4). The centrifugal forces, combined with the low pressure developed at the backside of the piston, force the intake air to enter the intake chamber with a high mass flow rate. In some cases, this flow rate is higher than if the air would have entered the same chamber through an intake port, forced only by the low pressure that the piston creates at its back.

In some embodiments, blades adapted on the edges of the machine's shaft can improve the result of the internal canals (position 36 in FIG. 4).

In other embodiments, the internal canal inside the shaft has a big diameter at the edges of the shaft (position 36) and a smaller diameter when it meets the internal canal (37) of the disc (region 38), as shown in FIG. 4.

In other instances, there will be any combination of no intake port, internal canals, blades on the shaft's edges, and a shaft's internal canal of big diameter near the shaft's edges and small diameter when it meets the disc's internal canal.

In various embodiments, a disc replaces both the “motion arm” and “moving wall” of the initial patent for higher robustness (FIG. 6). The peripheral surface of the disc (e.g., outer surface, see for example dark grey surface of disc (8) in FIG. 6) can define a cylindrical shape of the disc (see detail A-FIG. 6 depicting an interface between the disc and a Linear Sliding Port (LSP) with a small gap between them of around 100-300 μm) or otherwise curved shape (see detail A-FIG. 8 depicting an interface between the disc and an RSP isolator with a small gap between them of around 100-300 μm). The shape of the peripheral surface of the disc may follow the peripheral shape of the corresponding sliding port. For instance, the peripheral shape of the disc and sliding port are aligned in FIG. 6 (see detail A—FIG. 6) and in FIG. 8 (see detail A—FIG. 8). The curvature of the peripheral surface in FIG. 4 allows the isolator (here RSP (3)) to rotate close to the disc without coming in contact with the outer periphery of the disc, and thus retaining a constant small gap between the two peripheral surfaces of the RSP and the disc.

FIG. 6 depicts two alternative embodiments having a different number of pistons used for the compression process. In some cases, a machine described herein can have more than two pistons, all of which may be equally distributed on the periphery of the disc (8) or the cylindrical surface of the shaft (7). According to FIG. 6, for each piston, there is an isolator. The second embodiment is used when the pistons (2) rotate on a circular orbit of big diameter and the compression ratio has to be small. The axis-symmetric distribution of the pistons is to self-balance the weight of the piston-disc assembly (parts 2 and 8) shown in FIG. 6.

The isolator (3) can have a linear (reciprocating) motion (Linear Sliding Port-LSP) (as shown in FIG. 6) or a rotary motion (Rotary Sliding Port-RSP), as shown in FIG. 8.

RSP's and LSP's material can be any material that can resist the applied high pressure and temperature.

In other embodiments, there may be a combination of at least one RSP isolator and at least one LSP.

In some embodiments, the compressor includes at least one actuator per installed sliding Port (RSP or LSP (3)). In line with the initial patent U.S. Pat. No. 8,001,949, there is at least one isolator for isolating the compression chamber from the intake chamber (FIG. 1). If the machine uses two axis-symmetrically located pistons (2), it may also have two isolators installed axis-symmetrically (FIG. 6).

In other embodiments, the isolator may be the thinnest possible because the CFD results show that this increases the compression ratio by offering extra space to the compression and/or intake chamber. Moreover, a thin isolator operates as a labyrinth for the working fluid because it forces the fluid to change its direction sharply.

In the case of an LSP (3), at least one linear actuator (9) can arrange its reciprocating motion (e.g., FIG. 6). If the linear actuators (9) have a lift smaller than the piston (2) requires, the LSP can use more than one linear actuator (9) installed in series. For instance, if the linear actuators have a lift of up to 5 mm and a lift time of 1 millisecond, then for a piston's diameter of 40 mm, eight linear actuators (9) have to be connected as shown in FIG. 7 to lift the LSP (3) for 40 mm in 1 millisecond.

In some embodiments, like the one shown in FIG. 8, the compression/expansion ratio needs to be small, and thus at least two pistons can use the same isolator (3). In this case, there is only one isolator regardless of the number of pistons installed. FIG. 8 and FIG. 9 include exemplary RSP isolator (3) shapes that cover various compression needs. If the RSP (3) has the same speed as the pistons, the RSP isolator then requires one piston-passing hole for each piston installed. These holes are necessary for allowing the pistons to pass through the isolator body when the pistons reach the isolator.

In other instances, the RSP isolator has only one piston-passing hole, but the chamber has more than one piston. Then, the RSP isolator may be required to rotate at a higher speed than the rotation of the pistons. For example, the RSP isolator may need to rotate faster than the pistons at a rate that correlates to the ratio between the number of the pistons and RSP isolator. For instance, when there are three pistons in the same chamber, the RSP isolator can have a three times faster rotation speed than the pistons' speed. If the RSP isolator (3) rotates twice as fast as the pistons, then it may have only one piston-passing hole for a pair of pistons that are axis-symmetrically installed (FIG. 8).

In other embodiments, there is a need to have a fully symmetrical design, then two RSP isolators (3) will be used (FIG. 8).

As shown in FIG. 9, in some embodiments where there is no space limitation for the machine's design, the diameter of the RSP isolator (3) can be as big as possible. To minimize RSP isolator's opening and closing time and increase the compression ratios (CR), RSP isolator may have a diameter bigger than the diameter of the piston's circular orbit. Accordingly, in some cases, the bigger the RSP isolator diameter is, compared to the diameter of the piston's circular orbit, the better (e.g., enables higher compression ratio). When the RSP isolator becomes bigger in diameter, the angle φ of the piston-passing hole (15) becomes smaller because the arc length of the hole remains the same (D1=D2). A smaller φ gives a shorter opening and closing time for the RSP isolator, making the compression process last longer. Therefore, the CR becomes higher. Since the piston-passing hole (15) remains the same, but the RSP isolator size increases, the piston-passing hole (15) covers a smaller area of the big solid disc-shaped RSP isolator. Thus, the piston-passing hole is now small compared to the RSP isolator's big size, and, in general, a smaller hole on a disc also means a more robust disc-shaped RSP isolator (3).

In other instances, when there are space limitations for a large RSP isolator (e.g., by diameter), the single RSP isolator (3) can be replaced by three RSP isolators for each piston, as shown in FIG. 10. In this case, the collaboration of the three RSP isolators gives a much faster closing/sealing process (8-12 degrees instead of 44 degrees which is the single RSP isolator's closing time). This design achieves up to 70% faster RSP isolator closing, thus improving all four machine types' compression and expansion ratio. The three RSP isolators have neither the same rotation speed nor the same direction. The outer sliding ports (10) and (11) are rotating in opposite directions with each other (counter-clockwise & clockwise) and with double rotational speed compared to the shaft (7) and the middle RSP isolator (12). Every 180 degrees, due to their double rotational speed, the outer RSP isolators (10) and (11) open again. Since the middle RSP isolator (12) rotates at the same speed as the shaft (7), the chambers remain isolated. Therefore, RSP isolator (12) serves as an isolating device for the chambers every 180 degrees when the other two are open. (FIG. 10).

In some embodiments, the RSP isolator (10) and (12) may be thinner than RSP isolator (11) (see FIG. 10 width C>width B>=width A) because the pressure applied on them is lower than the one applied on RSP isolator (11). The RSP isolator (11) has one face inside the compression chamber and therefore faces the highest pressure forces. On the other hand, RSP isolator (10) is inside the intake chamber and, therefore, can have the thinnest width among the three RSP isolators.

In other embodiments, the RSP isolators' piston-passing holes (13, 14, 15) for the pistons differ from each other (FIG. 10). Their shape depends on their position (outer or middle RSP isolator) and their direction in relation to the piston's motion. More precisely, the middle RSP isolator (12) may have a symmetrical hole (14), and the outer holes (13 and 15) may have a non-symmetrical shape in order to isolate the chambers as soon as possible after the piston (2) passes through.

As shown in FIG. 13, in some embodiments, the stationary housing (outer shell) (which may encompass stationary and/or rotating parts) is divided into as many parts (e.g. 40, 41, 42, 43) as the number of different planes where the assembly's shafts are located. The number of planes where at least one of the assembly's shafts is located defines the number of parts. These shafts can include the machine's main shaft (7) and any auxiliary shaft used to move gears, isolators, or pistons. This housing division makes assembling easy and allows for easy quality control of the critical gaps between the moving and stationary parts.

In other embodiments, the thickness of the walls of the isolator's housing and the main chamber's housing are minimized to increase cooling of the machine and/or to help minimize the thermal expansion of the housing. In some cases, if the thermal expansion of the housing becomes higher than the piston's and SP's thermal expansion, it can cause a significant increase in the gap between the SP and the housing and between the piston and the housing. This increment may become critical for the sealing of the machine. Therefore, in some cases, the rotating parts comprise of a material with a higher thermal expansion than the material of the stationary parts. The left-hand side of FIG. 13 shows the cheapest CNC construction of the housing if there was no thermal expansion problem. The right side of FIG. 13 shows an assembled housing that minimizes the thermal expansion phenomenon.

In other embodiments (FIG. 14), to seal certain parts of the machine with each other, there is a small protrusion (44) along the interior configurations of each housing's part and a flange (45 or 46) of an isolating material (such as PTFE) to prevent any leakage of the working fluid between two tightly adjusted neighboring parts. The design of the flange is crucial to prevent any leakage or intersection with the moving parts. In some embodiments, the parts have different dimensions at the point they contact each other. Therefore, if the flange's design follows the interior configuration of any of the two housing parts in contact, the flange will be a little smaller or a little larger than the borders of the other part. In the case of smaller, there will be a leakage along the flange. In cases where the flange is larger than at least one of the two housing parts in contact, there may be an intersection between the moving parts and the flange, especially after the thermal expansion during the operation of the machine. In FIG. 14, detail A shows the case of having a larger flange than the bottom part, and thus there is a small part of the flange that penetrates the piston's path. Considering that the machinery constructs the flanges with tolerances of 250 μm, the penetrated flange may be even bigger and close the sealing gap of, for example, 100-300 μm between the piston and the chamber's internal wall entirely.

As shown in FIG. 11, since the RSP isolator is a disc with a cylindrical or curved outer periphery, no extra weight can be added to its outer surface to weight-balance the piston-passing hole (15). Therefore, the only way to weight-balance the disc is to remove material. Material-removed area (17) is always at the opposite side of the piston-passing hole (15), and its region may be wider than the hole's region (18) in order to limit the depth of the material removal. Moreover, the material removal can be applied only on one of the two planar sides of the RSP isolator or symmetrically at both sides.

With reference to FIG. 11, in some embodiments, apart from the piston-passing hole (15), the RSP isolator (3) may contain a cavity configuration (73) in order to avoid the development of high pressures at the front side of the piston when the piston passes through the body of said RSP isolator. During the pass of the piston through the RSP isolator, the compression process is complete and any high pressure development at the front side of the piston is translated into a negative torque and energy for the compression process. After the compression process is complete, any pressure applied on the front side of the piston is negative for the efficiency of the compressor. CFD studies (see for e.g. FIG. 12,) show that the cavity helps the compressor to have up to 42% lower peak-pressure during its pass through the RSP isolator.

FIG. 12 shows the position of the piston when the pressure reaches its peak value when the piston passes through the RSP isolator. On the left hand-side, the RSP isolator has no cavity and the available space front of the piston is very limited. Thus, the fluid trapped between the piston and the RSP isolator is continuing to be compressed and increase its pressure. On the right-hand side, the same piston is at the same position but the trapped fluid between the piston and the RSP isolator has extra space to expand itself inside the cavity and therefore the pressure at this moment is 42% lower.

Ideally the cavity's orientation should be like the one shown in, oriented to maximize the free expansion of the fluid inside its interior. However, such an orientation is very difficult for CNC machining (e.g., the cavity on the right image of FIG. 12 represents an ideal cavity, while cavities (73) and (74) in FIG. 11 represents a more actual depiction of the cavity due to CNC machining limitations). Therefore, any orientation that is the closest possible to that is acceptable.

In some embodiments, as depicted in FIG. 11, angle φ′ between an opening to the RSP isolator receptacle and a tangential longitudinal plane helps promote the transfer of trapped working fluid to the back of the piston, thereby minimizing kinetic energy losses of the fluid. In some embodiments, the angle φ′ is from about 10 degrees to about 90 degrees.

In other embodiments, for achieving the higher possible pressure drop, the distance “S′” must be the smallest possible and the radius “R′” the greater possible. There is no typical value for this dimensions since their value depends on the size of the machine.

Pistons (2) may be attached on the disc (8) in the way that blades are attached on the shaft of gas turbines (FIG. 15). If the pistons are more than one, they are located symmetrically on the disc's periphery. Thus, there is no need for weight-balance the piston-disc assembly (FIG. 8). However, if there is only one piston, the piston-disc assembly has to be weight-balanced. Since no material can be added to the cylindrical (when LSP is used) or curved periphery (when RSP is used) of the disc (8), material has to be removed from the disc and preferably close to the location of the piston on the disc. Since the area under the piston (2) should ideally be solid metal for a more robust disc (8), two regions of material removal may be created and located symmetrically to the piston (19, FIG. 15).

In some embodiments, when the disc (8) is so thin that symmetrical material removal (19) is not enough for weight-balancing the piston-disc assembly, the piston (2) may need to be as light as possible to minimize the required material removal from the piston-disc. Since the high-pressure applies only at the front side of the piston, the final design of a light piston will be similar to that of piston (20)-FIG. 15. This design has its center of mass closer to the front side of the piston (20). The non-symmetric mass distribution of the piston's weight necessitates a third material removal area (21) at the disc to balance the center of mass of the piston (20). As shown in FIG. 15, area (21) is not symmetrically located to counterweight the non-symmetric weight of piston (20).

In other embodiments, even the three regions are not enough. In that case, extra parts (22) have to be attached at both sides of disc (8) to correct the center of mass location (FIG. 15). Those parts may have any possible shape that can correct any rotation unbalance of the piston-disc assembly. For instance, in FIG. 15, the extra parts have the shape of discs (22), and they have a material removal region (23) with a depth deeper than the height of the extruded material on both sides of disc (24).

In some embodiments, if the extra discs (22) are thick enough, as an alternate to removing the area (21), an appropriate mass area (25) on the extra side discs (22) can be removed. In FIG. 16, on the left-hand side is with the removal area (21) and extra discs (22), and on the right-hand side is the same result (with respect to weight-balancing) using only the extra discs (22) but with the mass removal area (25) that replaces the area (21).

In some embodiments, where there is a need for extra material removal, any combination of all areas mentioned above of material removal may become necessary (19, 20, 21, 23 from FIGS. 15 and 25 from FIG. 16).

FIG. 19 depicts exemplary piston-disc or rotor assemblies and/or parts having a weight balance configurations. As used herein, the terms “disc” and “rotor” may be used interchangeably. In some embodiments, the piston (2) contains a weight balance configuration (e.g. 67 in FIG. 19-A) at its back to reduce its mass and provide the rotating mechanism a more stable window of operation. The symmetrical weight balance configuration with number 67 (FIG. 19-A) is a typical one to avoid eccentricity of the mass center around the rotation axis. The method to weight-balance a part or assembly, having an extra mass on its periphery (e.g., via a piston (2)), comprises of removing material close to a location of said extra mass, wherein an area corresponding to the material removal may comprise of two symmetrical or asymmetrical areas (69), (71) compared to a “symmetry” plane or a rotation-/symmetry-axis of the part (72) or assembly (66 or 68).

When the area corresponding to the material removal comprises of two asymmetrical areas (e.g. 69) compared to a “symmetry” plane (e.g., the “symmetry plane 01” shown in FIG. 19-B) of an assembly (e.g. 68), then an extra part (68α) of higher weight-density should be placed at the side of the “symmetry” plane where the most material is removed.

The area corresponding to the material removal may comprise of two symmetrical (like 67 at FIG. 19-A) or asymmetrical areas (like 69 and 72 at FIG. 19 B and D) compared to a “symmetry” plane (like the “symmetry plane 01” shown in FIG. 19-B) of the piston-disc or piston-rotor assembly (e.g., (66) or (68)) or part (like 72).

In other embodiments, the weight balance configuration may include mass removal not only from areas around or close to the extra mass (piston) located on the periphery of the disc or rotor, but also areas (e.g. 70α) where high temperature is developed during the machine's operating cycle. This cavity configuration (such as 71 at FIG. 19-C) helps the metals that absorb the developed heat of the process to release the heat faster towards the environment. The temperatures inside the weight balance configuration during the entire operating cycle is around 300K. Thus, the temperature difference between the hot metal and the “cold” fluid trapped in the cavity configuration (e.g., (71)) accelerates the cooling of the hot metals. The fluid in cavity (71) has a low temperature during the entire machine's operating cycle due to the high velocity fluid that runs around the cavity configuration (71).

In those embodiments, in order for the cavity configuration to function as a weight balance configuration as well, the approach and material removal close to the hot areas may be achieved by digging the metal with an inclination (e.g. angle φ at FIG. 19-C) thereby providing the cavity with an incline φ as compared to a “symmetry” plane or any plane parallel to a “symmetry” plane as shown in FIG. 19-C. This inclination is important to avoid material removal from areas (e.g., 70β) that are necessary to weight-balance the material removal areas (70α). In some embodiments, the angle φ ranges from 0 deg to about 90 deg, from about 5 deg to about 75 deg, from about 10 deg to about 60 deg, from about 15 deg to about 45 deg, from about 20 deg to about 30 deg, or from about 22 deg to about 25 deg.

In some embodiments, the reference character “t” depicts a wall thickness of the piston and rotor that remains with a respect to a cavity therein from material being removed for weight balancing and/or cooling. The wall thickness depends on the size of the machine. In general, the thinner the wall, the better the cooling of the metal. However, there is a limitation for the lowest thickness, which depends on the pressure that applies on the metal during the operating cycle of the machine. In some embodiments, the wall thickness “t” is from about 2 mm to about 350 mm. In some embodiments, having a wall thickness “t” from about 2 mm to about 20 mm helps a faster heat release to the environment.

In some embodiments, the reference character “R” depicts a curvature of said cavity with a respect to said cavity therein from material being removed for weight balancing and/or cooling. In some embodiments (according to the machine's size), the curvature “R” is from about 1 mm to about 1000 mm. In some embodiments, having a big curvature “R” from about 20 mm to about 50 mm with a small angle “φ” from about 90 degrees to about 120 degrees helps the creation of the same cooling result with a smaller cavity.

In some embodiments, the reference character “S” depicts how deep is said cavity. In some embodiments, the distance “S” is from about 1 mm to about 3000 mm; it depends on the machine's size. The bigger the distance “S”, the greater the area that can be cooled through the thin walls created by the cavity.

In general, their value may depend on the size of the machine, and it can be even greater than the one indicated here.

In some embodiments, a method to seal a gap between a rotating and a stationary part on the machine comprises using at least one metal or non-metal knife or fin (26) disposed on the rotating part to come in contact with a layer (27) of a softer metal or non-metal material, disposed on the stationary part (FIG. 20). The knives' edges (e.g., knife teeth, as depicted in FIG. 20) must come into contact or into forced contact with the layers during assembling, such that the contact prevents air leakage from areas of high pressure to the environment. In some cases, if the thermal expansion of the knives makes the knives or fins (26) press against the layers (27), the layers (27) will compress at those locations of contact (e.g., knife teeth will push more into layers), and thereby retain the contact of the two materials (knives or fins (26) and layers (27)). In some cases, once the temperature becomes low, the knives or fins (26) may compress, thereby forming a gap between the layers and the fins'/knives' edges (e.g., teeth). In some cases, this creates an efficient labyrinth with gaps (28) of around 100-300 μm between the layers (27) and the fins'/knives' edges (26).

In some embodiments, to arrange the distance between the fins or knives (26) and the layers (27), the knives or fins (26) are assembled at the housing by using at least one screw (29) that drags the knives or fins (26) towards the housing and at least one screw (30) that drags them towards the layers (27) (FIG. 21).

In other embodiments, to protect the bearings from a sealing malfunction, at least one hole (31) with at least one leading wall (33) prevents any leakage of high-pressure working fluid from hitting against the bearings. The wall (33) leads the leaked fluid directly to the environment through the holes (31) (FIG. 21).

In some embodiments, the piston's sidewall may be toroidal or even cylindrical for making the construction cheaper. The sealing advantage of using a toroidal sidewall instead of a cylindrical one is less than about 1.5%.

In other embodiments, for a more efficient sealing, computational fluid dynamics (CFD) results in “Converge CFD” solver showed that if the chamber's surface is of very low roughness and the piston's cylindrical or toroidal surface is very rough (H11 or H12), then an efficient aerodynamic sealing is achieved.

As shown in FIG. 15, the piston's sidewall (47) may have very thin knives or fins (e.g., teeth), very close to each other like the teeth of a comb. This configuration provides an interference (for example, close to or substantially the same effect of a barrier, such as a wall) and the height of the teeth (of the knives or fins) gives a very high roughness for the working fluid when it goes around the piston's sidewall (47), and combined with a tiny gap between the free edges of the teeth (of the knives or fins) and the internal wall of the chamber wall (less than about 1 mm or 2 mm), gives a very efficient sealing of the piston. The same configuration may be applied on the RSP isolator's periphery. The “comb's teeth” may be created internally or externally on the surface of either the piston's sidewall or the RSP isolator periphery.

In other embodiments, such as depicted in FIG. 22, to seal a gap between a rotating (27) and a stationary part (26) or two rotating parts or two stationary parts, there is a combination of at least one labyrinth seal with shaft seals or seal rings. In some cases, the labyrinth seal lowers the high pressure and temperature of the working medium developed in the chambers to values that are acceptable for the commercially available shaft seals or seal rings. For instance, they can reduce a dynamic pressure of about 35 bar to about 5 bar, and a dynamic temperature of about 700K to about 350K. Accordingly, in some cases, such reduction in pressure and temperature facilitate the use of shaft seals (47), such as PTFE seals, that can stand up to about 10 bar and about 450K. Combining this labyrinth seal with at least one shaft seal or seal ring, such as PTFE seals that can stand up to about 10 bar and about 450K, the gap is sealed successfully. In this case, there is no need of holes (31) and leading walls (33) to protect the bearings (32) (like the one shown in FIG. 21). The shaft seals (47) protect the bearings (32) (FIG. 22). As described herein, this sealing method can be used between a rotating part and a stationary part, between two rotating parts, and/or between two stationary parts.

In general, shaft seals operate efficiently only in a static pressure environment and up to about 10-20 bar. In some cases, with the above described method, they can operate efficiently also in dynamic pressure environments, because putting a labyrinth before the shaft seal translates the dynamic pressure to static pressure. For example, the working medium may become trapped inside the at least one labyrinth, and eventually the shaft seal does not face a strongly varying pressure and/or temperature. Moreover, in some cases, the trapped working medium has a much lower pressure and temperature when it comes close to the shaft seal, thereby permitting the use of shaft seals in such high pressure compression and combustion/expansion processes.

There is a combination of at least two labyrinth systems, a vertical (48a) and a horizontal (49), and at least one shaft seal (47). The working medium enters the first labyrinth chamber (52) through a small gap (50) (e.g. of about 100-500 μm) and contacts a curved wall (51) of the rotating part (27) that leads the fluid towards the stationary part (26). After that, the fluid, in order to escape to the second labyrinth's chamber (53), has to find a small gap (e.g. of about 100-500 μm or more in case of heavy duty applications) which is located in a direction unfavorable for the fluid's stream (e.g., see (65)). This procedure is repeated until the working medium enters the horizontal labyrinth (49). The horizontal labyrinth can help by further delaying the working medium from contacting the shaft seal, giving time for the dynamic pressure developed in the high-pressure chamber to become lower because the operating cycle goes to another stage where the pressure starts to decrease.

In other embodiments, where the available space does not allow for using the vertical labyrinth (48a) described above, an alternative vertical labyrinth (48b) may be used. For instance, as shown in FIG. 23, at the left sidewall of RSP isolator (3), there is enough space to use the vertical labyrinth (48a). At the right sidewall of the same RSP isolator, the space between the right RSP isolator sidewall and the bearing (32) is limited, and the vertical labyrinth (48a) is replaced by the alternative vertical labyrinth (48b). At the (48b) labyrinth system (see FIG. 22), the working medium enters the first labyrinth chamber (52) through a small gap (50) (e.g. of about 100-500 μm or more in case of heavy duty applications) and contacts a curved wall (51) of the rotating part (27) that leads the fluid towards part (26). After that, the fluid, in order to escape to the second labyrinth's chamber (53), has to find a small gap (e.g. of about 100-500 μm or more in case of heavy duty applications) which is located in a direction unfavorable for the fluid's stream, perpendicular or at an opposite slope (see upper image of FIG. 22). This procedure is repeated until the working medium enters the horizontal labyrinth (49). The horizontal labyrinth can help by further delaying the working medium from contacting the shaft seal, giving time for the dynamic pressure developed in the high-pressure chamber to become lower because the operating cycle goes to another stage where the pressure starts to decrease.

In some embodiments, where the space between the shaft seal and the exit of the vertical labyrinth is limited, as shown in FIG. 23, inclusion of one knife or fin or small wall (59) is sufficient to protect the shaft seal (47).

In other embodiments, the limited space does not allow for the construction of at least one knife or fin or small wall (59), e.g. in most cases CNC machines require a fillet of at least 3 mm radius to construct wall (59). In these cases, a combination of at least one retaining ring (55) and at least one independent part (54) may be an acceptable solution. For instance, FIG. 23 uses a ring-shaped metal part for part (54), such as a washer.

In some embodiments, the gaps (56) or (57) between the parts (3) and (26) or (51) may be about 100-500 μm or even greater if the machine's size is big enough or the peak-pressure is not too high compared to the shaft seal's acceptable operating conditions. In some cases, part (26) may consist of a softer metal than the material of part (3), so that the possible contact between them does not destroy the design of part (3).

In other embodiments, the two parts may come in contact from the beginning at regions (56) or (57), and in this case part (26) or (51) has to consist of a softer material than part (3).

As shown in FIG. 23, in some embodiments, RSP isolator's periphery may be non-cylindrical in order to prevent the pass of the fluid between the two sides of the RSP isolator. It may have at least one channel such as the channel (60). The deeper the channel (60) on the RSP isolator's periphery, the better the sealing's efficiency.

In some embodiments, the RSP isolator periphery may have a constant distance from the housing's walls, or in some cases, the gap between the RSP isolator periphery and the housing's wall may differ, as shown in detail (58) of FIG. 23. For example, see detail (58) in FIG. 23, wherein the gap is getting gradually greater until reaching the center of RSP isolator (3) and then it becomes again gradually smaller. In some cases, the RSP isolator periphery includes a channel (60) or labyrinth defining a gap between the RSP isolator periphery and housing wall.

In some embodiments, there are no piston rings (no contact seal) to seal the gap between a shell that forms the internal surface of at least one chamber of a rotary concentric machine (circumferential gap for passage of the working medium) and the piston or any other member that rotates within the at least one chamber. The leakage of working medium from the at least one chamber to a neighboring chamber caused by a blow-by effect around a body of the at least one piston between these two components can be limited to less than 3% of the total mass of the working medium trapped in said chamber by rotating the piston at a very high speed (linear velocity more than 30 m/sec). This gap was initially evaluated to be 100 μm at 4,000 rpm or 50 μm at 2,000 rpm, but the latest simulations showed that it could be much bigger (up to 500 μm) if the piston rotates at 10,000 rpm, or even more than 500 μm (e.g. 1 mm) at higher rotation speeds or big applications. In case, the leakage is calculated based on the pressure loss caused by the leakage, the 3% refers to the pressure loss caused due to the leakage compared to the peak pressure should be achieved if there was no leakage. Therefore, the piston and the toroidal chamber sealing is not achieved by an air sealing mechanism but by running the piston at very high speeds, achieved by either high shaft speed (sufficiently high rotation speed) or using a sufficiently large rotation radius for the piston's rotating motion or both. A high circular orbit radius gives a high linear velocity to the piston. So, the piston needs no sealing because its high linear velocity prevents the air from leaking between its cylindrical or toroidal wall and the chamber's (shell's) walls. Its speed depends on the machine's speed and the diameter of the circular orbit where the piston runs. For a high piston's speed, both the machine's speed and the diameter of the circular orbit have to be high. The high speed of the piston allows for the use of more significant gaps between the piston and the surface of the chambers and makes the construction of the machine cheaper (for example, via the use of more relaxed tolerances).

In some embodiments, a high rotation radius for the piston, e.g. in the case of a compression process, allows for higher pressure outputs to be achieved. In some cases, the higher pressure output is based on a similar concept as described in FIG. 9. For example, in some cases the sliding port needs a specific time to open and close. The time for the sliding port to open and close may correspond to a specific part of the piston's orbit. For example, the time to open and close may be similar to the angle φ described in FIG. 9, wherein instead of representing the periphery of the sliding port, FIG. 9 depicts the piston's circular orbit. When the radius of the piston's orbit increases, the same opening and closing time corresponds to a smaller angle φ and a smaller part of the total piston's orbit. Therefore, the distance that the piston has to run until it meets the sliding port becomes longer, which is translated to a higher compression ratio.

As shown in FIG. 3, in some embodiments, the compressor may be supercharged by creating a very small intake port (1), e.g., if the intake port (1) has the shape of a circle, its diameter can be even 70% smaller than the diameter of the piston (2). Logical thought is to make the intake port (1) large to ensure a good charging coefficient for the intake chamber (4) (e.g., larger intake port may be thought to enable higher air intake). However, at the end of the compression process, in some cases, when the isolator brings the intake chamber (4) in communication with the compression chamber (6), the highly compressed air trapped in the compression chamber (6) creates a pressure wave that exits through the intake port (1) to the environment. In some cases, if the intake port (1) is small, the pressure wave travels along the intake chamber (4) until it meets the backside of the piston (2). After it hits against the piston (2), it travels back towards the intake port (1), and the procedure continues until this pressure wave loses its kinetic energy. An advantage of this procedure (via a small intake port) is that the pressure wave's momentum drags at its backside fresh air from the intake port, increasing the intake chamber's charging coefficient (4). Eventually, this phenomenon results in supercharging the compression chamber (6).

In other embodiments, the intake port (1) may have any shape or size or orientation or location that allows for trapping the pressure wave inside the intake chamber (4) but also enhances the free drag of the working fluid through the intake port (1) at the backside of the piston (2) (FIG. 3), thereby supercharging the rotary machine. As mentioned above, in some embodiments, the most favorable location of the intake port is the closest possible to the isolator, because the pressure wave is developed at that location with a direction tangential to the port's entering. In some embodiments, the best orientation of the intake port is opposite inclined to the pressure wave's direction. In some embodiments, a smaller intake port size is beneficial, leading to higher output pressure because when the intake port is small, there is a smaller back flow to the intake pipe when the pressure wave is released from the compression chamber towards the intake chamber.

In other embodiments, the intake port may have any shape or size or location or orientation, but there is a valve that controls the fluid communication of the intake chamber with the intake manifold or pipe or environment. In that case, a late opening of the vale will allow for the developed pressure wave to pass the intake port when it is closed and afterwards open the port to allow for the wave to drag strongly intake working medium and supercharge the machine.

In other embodiments, there is an outlet valve that remains close for more than one operating cycles, and the intake valve's timing described above supercharges the machine for more than one operating cycles. CFD results showed that this procedure can increase the output pressure up to 30%.

In some embodiments, the rotary concentric machine comprises at least one shaft; at least one piston that rotates on a circular orbit concentrically located with the at least one shaft, wherein the at least one piston is coupled directly to a cylindrical surface of the shaft, thereby forming a piston-shaft assembly; a shell that forms at least one chamber, wherein the at least one piston is configured to rotate within the at least one chamber; at least one isolator configured to separate the chamber into a plurality of sub-chambers; and at least one outlet port.

In some embodiments, the rotary concentric machine comprises at least one shaft; at least one piston that rotates on a circular orbit concentrically located with the at least one shaft of the machine, wherein the at least one piston and a cylindrical surface of the shaft form a unitary component, thereby forming a piston-shaft part; a shell that forms at least one chamber, wherein the at least one piston is configured to rotate within the at least one chamber; at least one isolator that is configured to separate the chamber into a plurality of sub-chambers; and at least one outlet port.

In some embodiments, the rotary concentric machine comprises at least one shaft; at least one disc or rotor coupled to the at least one shaft; at least one piston that rotates on a circular orbit concentrically located with the at least one shaft, wherein the at least one piston is coupled to a disc or rotor of the at least one disc or rotor, thereby forming a piston-disc or piston-rotor assembly; a shell that forms at least one chamber, wherein the at least one piston is configured to rotate within the at least one chamber; at least one isolator that is configured to separate the chamber into a plurality of sub-chambers; and at least one outlet port.

In some embodiments, the rotary concentric machine comprises at least one shaft; at least one disc or rotor coupled to the shaft; at least one piston that rotates on a circular orbit concentrically located with the at least one shaft, wherein the at least one piston and a disc or rotor of the at least one disc or rotor form a unitary component, thereby forming a piston-disc or piston-rotor part; a shell that forms at least one chamber, wherein the at least one piston is configured to rotate within the at least one chamber; at least one isolator that is configured to separate periodically the chamber into a plurality of sub-chambers; and at least one outlet port.

For any rotary machine described herein, in some embodiments, further comprising at least one intake port, such that a working fluid enters into the chamber via the intake port.

For any rotary machine described herein, in some embodiments, a dimension of the at least one intake port is significantly smaller than a dimension of the at least one piston, wherein significantly smaller corresponds to the dimension of the at least one intake port being at least about 50% to about 90% smaller than the dimension of the at least one piston.

For any rotary machine described herein, in some embodiments, the dimension of the at least one intake port corresponds to a size of the intake port opening, and the dimension of the at least one piston corresponds to a diameter of the at least one piston.

For any rotary machine described herein, in some embodiments, the at least one intake port comprises a circular opening, such that a diameter of the circular opening is significantly smaller compared to the at least one piston's diameter, wherein significantly smaller corresponds to the diameter of the circular opening being at least about 50% to about 90% smaller than the diameter of the at least one piston.

For any rotary machine described herein, in some embodiments, the at least one intake port has a rectangular shape with or without fillets around its corners, and is located proximate to and/or tangential to an upper portion of the chamber.

For any rotary machine described herein, in some embodiments, the at least one intake port comprises any shape or orientation (e.g. with a perpendicular or negative inclination to the working fluid's stream direction) enabling for trapping of any pressure wave developed inside the chamber, such that the pressure wave remains inside the chamber and a free drag of a working fluid entering through the at least one intake port increases towards a backside of the at least one piston.

For any rotary machine described herein, in some embodiments, the at least one intake port is located such that the distance between the intake port and the motion plane of the isolator is minimal or as small as possible to a motion plane of the isolator.

For any rotary machine described herein, in some embodiments, the at least one intake port is placed at a sidewall of the chamber where the isolator first exposes an intake sub-chamber of the plurality of sub-chambers with a compression sub-chamber of the plurality of sub-chambers, thereby placing the intake sub-chamber and the compression sub-chamber into fluid communication. (e.g. area 85 in FIG. 2);

For any rotary machine described herein, in some embodiments, the at least one shaft and/or the at least one piston each comprise at least one internal canal to provide a working fluid inside the chamber

For any rotary machine described herein, in some embodiments, the shaft, at least one disc or rotor, and/or at least one piston each comprise at least one internal canal to provide a working fluid inside the chamber.

For any rotary machine described herein, in some embodiments, further comprising a one-way valve located where said internal canal meets the chamber, so as to prevent the working fluid inside the chamber to enter the internal canal.

For any rotary machine described herein, in some embodiments, the shaft's internal canal comprises a first diameter proximate to at least one edge of the shaft, and second diameter where said internal canal interfaces with an internal canal of the disc or rotor, wherein the second diameter is smaller than the first diameter.

For any rotary machine described herein, in some embodiments, the internal canals of the shaft have blades adapted at the at least one of the edges of the shaft.

For any rotary machine described herein, in some embodiments, a rotation radius of the at least one piston is maximized to make a sealing at its periphery more efficient and/or to maximize a compression/expansion ratio of the machine.

For any rotary machine described herein, in some embodiments, a thickness of the at least one isolator minimized.

For any rotary machine described herein, in some embodiments, the at least one isolator comprises a rotary sliding port (RSP) isolator and at least one linear sliding port (LSP).

T For any rotary machine described herein, in some embodiments, the at least one isolator comprises a linear sliding port (LSP).

For any rotary machine described herein, in some embodiments, a linear actuator controls the motion of the LSP.

For any rotary machine described herein, in some embodiments, further comprising a plurality of linear actuators having a same or different lift-time connected in series to lift the LSP, such that the lift of the LSP is based on a sum of the lifts of the plurality of linear actuators together.

For any rotary machine described herein, in some embodiments, the at least one isolator comprises a rotary sliding port (RSP).

For any rotary machine described herein, in some embodiments, a periphery of the disc or shaft where the pistons are located comprises a shape corresponding to a shape of a periphery of the RSP, or the periphery of the RSP has a shape corresponding to a shape of a surface of the disc or shaft where the pistons are located.

For any rotary machine described herein, in some embodiments, the diameter of the RSP isolator is maximized.

For any rotary machine described herein, in some embodiments, material is removed from at least one sidewall of the RSP isolator to weight-balance the part.

For any rotary machine described herein, in some embodiments, comprising only one RSP isolator with one piston-passing hole, wherein the RSP isolator rotates at a speed higher than a rotation speed of the at least one piston.

For any rotary machine described herein, in some embodiments, comprising only one RSP isolator comprising a same number of piston-passing holes as a number of pistons of the at least one piston, wherein a speed of rotation of the RSP isolator is equal to a speed of rotation of the piston.

For any rotary machine described herein, in some embodiments, further comprising a plurality of pistons and a plurality of RSP isolators, wherein the number of RSP isolators in the plurality of RSP isolators is equal to the number of pistons in the plurality of pistons, where all the pistons and the RSP isolators are axis-symmetrically located with each other.

For any rotary machine described herein, in some embodiments, the RSP isolator comprises a group of three RSP isolators, each having a prescribed distance from each other, wherein a middle RSP isolator rotates with an angular velocity of the shaft, and both outer RSP isolators rotate with an angular velocity that is double the angular velocity of the shaft, wherein, optionally, only one of the outer RSP isolators rotates in a same direction as the middle RSP isolator, while the remaining outer RSP isolator rotates in an opposite direction thereto.

For any rotary machine described herein, in some embodiments, the outer RSP isolator that directly faces a high-pressure sub-chamber of the plurality of sub-chambers is thicker than the other two RSP isolator.

For any rotary machine described herein, in some embodiments, the middle RSP isolator is thicker than the outer RSP isolator that faces a lower-pressure sub-chamber.

For any rotary machine described herein, in some embodiments, at least one outer RSP isolator has a different shape for the piston-passing hole than the middle RSP isolator.

For any rotary machine described herein, in some embodiments, the RSP isolator defines a receptacle or piston-passing hole configured to receive the at least one piston, wherein said receptacle or piston-passing hole is sized so as to reduce pressure build-up at a front side of the at least one piston when the at least one piston is entering into said receptacle along its rotation on the circular orbit.

For any rotary machine described herein, in some embodiments, the RSP isolator defines a receptacle or piston-passing hole configured to receive the at least one piston, wherein the RSP isolator has a cavity configuration in fluid communication with said receptacle or piston-passing hole to reduce pressure build-up at a front side of the at least one piston when the at least one piston is entering into said receptacle along its rotation on the circular orbit.

For any rotary machine described herein, in some embodiments, said receptacle or cavity configuration has an orientation to favor expansion of a trapped working fluid between the piston and the RSP isolator.

For any rotary machine described herein, in some embodiments, said receptacle or cavity configuration has said cavity opposite to the piston's front side, when the piston reaches a periphery of the RSP isolator.

For any rotary machine described herein, in some embodiments, an area corresponding to the cavity configuration or receptacle of the RSP isolator comprises of two symmetrical or asymmetrical areas about a symmetry plane or a symmetry- or rotation-axis of the RSP isolator.

For any rotary machine described herein, in some embodiments, the area corresponding to the cavity configuration or receptacle of the RSP isolator may comprise of two asymmetrical areas about a symmetry plane or a symmetry-axis or rotation-axis of the RSP isolator, wherein a largest area of said cavity configuration is located proximate to an area of the RSP isolator where high pressure is developed.

For any rotary machine described herein, in some embodiments, comprising a stationary housing divided into as many parts as a number of different planes where the at least one shaft is located, including a main shaft and any auxiliary shafts used to move gears, the at least one isolator, and the at least one piston.

For any rotary machine described herein, in some embodiments, at least one housing part of each pair of housing parts of the stationary housing that comes in contact through a flange has a protrusion along its interior configurations to prevent any leakage around the sealing flange or any intersection of the sealing flange with the moving parts.

For any rotary machine described herein, in some embodiments, a weight of the at least one piston is minimized to facilitate weight balance of one or more parts and/or assemblies that contain the at least one piston.

For any rotary machine described herein, in some embodiments, the at least one isolator and/or piston-disc assemblies or parts thereof are weight-balanced with one of the methods of the invention.

For any rotary machine described herein, in some embodiments, the piston-shaft assembly or part has a cavity configuration comprising at least one cavity serving as a weight balance configuration, wherein a cavity of the at least one cavity has an inclination compared to a horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane in order to weight balance the piston-shaft assembly or part without a need of using any extra part with a higher weight-density as a counterweight, and wherein material removal from the piston-shaft assembly or part is avoided from areas where weight of such material is necessary to counterbalance the piston-shaft assembly or part.

For any rotary machine described herein, in some embodiments, the piston-disc or piston-rotor assembly or part has a cavity configuration comprising at least one cavity serving as a weight balance configuration, wherein a cavity of the at least one cavity has an inclination compared to a horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane in order to weight balance the piston-disc or piston-rotor assembly or part without a need of using any extra part with a higher weight-density as a counterweight, and wherein material removal from the piston-disc or piston-rotor assembly or part is avoided from areas where weight of such material is necessary to counterbalance the piston-disc or piston-rotor assembly or part.

For any rotary machine described herein, in some embodiments, the piston-shaft assembly or part has a cavity configuration comprising at least one cavity serving as a weight balance configuration, wherein an area corresponding to said at least one cavity comprises of two asymmetrical areas about a symmetry plane or a symmetry-axis or rotation-axis of the part or piston-shaft assembly in order to weight balance the piston-shaft assembly or part without a need of using any extra part with a higher weight-density as a counterweight, and wherein material removal of the piston-shaft assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part.

For any rotary machine described herein, in some embodiments, the piston-disc or piston-rotor assembly or part has a cavity configuration comprising at least one cavity serving as a weight balance configuration, wherein an area corresponding to the at least one cavity comprises of two asymmetrical areas about a symmetry plane of the part or piston-disc or piston-rotor assembly in order to weight balance the piston-disc or piston-rotor assembly or part without the need of using any extra part with a higher weight-density as a counterweight, and wherein material removal of the piston-disc or piston-rotor assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part.

A method to correct the weight-balance of any rotary machine described herein, in some embodiments, wherein material is added at one or more areas of the at least one piston where material has been removed to make the at least one piston lighter.

For any rotary machine described herein, in some embodiments, the piston-shaft assembly or part has a cavity configuration disposed proximate to areas of the piston-shaft assembly or part where high temperature is developed to create one or more walls of the piston-shaft assembly or part having a thickness that favors faster cooling of those hot areas.

For any rotary machine described herein, in some embodiments, the piston-disc or piston-rotor assembly or part has a cavity configuration disposed proximate to areas of the piston-disc or piston-rotor assembly or part where high temperature is developed to create one or more walls of the piston-disc or piston-rotor or part having a thickness that favors faster cooling of those hot areas.

For any rotary machine described herein, in some embodiments, the piston-shaft assembly or part has a cavity configuration with a double role: to weight balance the piston-shaft assembly or part and also to cool areas where high temperature is developed, by having an inclination compared to a horizontal or symmetry plane or any plane parallel to a symmetry plane in order to weight balance the piston-shaft assembly or part without a need of using any extra part with a higher weight-density as a counterweight, wherein material removal from the piston-shaft assembly or part is avoided from areas where such weight of the material is necessary to counterbalance the piston-shaft assembly or part; and wherein expanding the cavity configuration proximate to areas of the piston-shaft assembly or part where high temperatures are developed, the cavity configuration creates one or more walls of the piston-shaft assembly or part having a thickness that favors faster cooling of those hot areas.

For any rotary machine described herein, in some embodiments, the piston-disc or piston-rotor assembly or part has a cavity configuration with a double role: to weight balance the piston-disc or piston-rotor assembly or part and also to cool areas where high temperature is developed, by having an inclination compared a horizontal or symmetry plane or any plane parallel to a symmetry plane in order to weight balance the piston-disc or piston-rotor assembly or part without a need of using any extra part with a higher weight-density as a counterweight, wherein material removal from the piston-disc or piston-rotor assembly or part is avoided from areas where weight of such material is necessary to counterbalance the piston-disc or piston-rotor assembly or part; and wherein expanding the cavity configuration close to areas of the piston-disc or piston-rotor assembly or part where high temperatures are developed, the cavity configuration creates one or more walls of the piston-disc or piston-rotor having a thickness that favors faster cooling of those hot areas.

For any rotary machine described herein, in some embodiments, the piston-shaft assembly or part has a cavity configuration with a double role: to weight balance the piston-shaft assembly or part and to cool areas where high temperature is developed, where an area corresponding to a cavity of the cavity configuration comprises of two asymmetrical areas about a symmetry plane or a symmetry-axis or rotation-axis of the part or piston-shaft assembly in order to weight balance the piston-shaft assembly or part without a need of using any extra part with a higher weight-density as a counterweight, wherein material removal from the piston-shaft assembly or part is avoided from areas where weight of such material is necessary to counterbalance the piston-shaft assembly or part; and wherein expanding the cavity configuration close to areas where high temperatures are developed creates one or more walls of piston-shaft assembly or part having a thickness that favors faster cooling of those hot areas.

For any rotary machine described herein, in some embodiments, the piston-disc or piston-rotor assembly or part has a cavity configuration with a double role: to weight balance the piston-shaft assembly or part and to cool areas where high temperature is developed, where an area corresponding to a cavity of the cavity configuration comprises of two asymmetrical areas about a symmetry plane or a symmetry-axis or rotation-axis of the part or piston-disc or piston-rotor assembly in order to weight balance the piston-disc or piston-rotor assembly or part without a need of using any extra part with a higher weight-density as a counterweight, wherein material removal from the piston-disc or piston-rotor assembly or part is avoided from areas where weight of such material is necessary to counterbalance the piston-disc or piston-rotor assembly or part; and wherein expanding the cavity configuration close to areas where high temperatures are developed creates one or more walls on the piston-disc or piston-rotor assembly or part having a thickness that favors faster cooling of those hot areas.

For any rotary machine described herein, in some embodiments, no piston rings are located around the at least one piston to seal a gap between the at least one piston and an internal surface of the chamber, wherein, leakage between the at least one piston and the internal surface of the chamber is limited by i) keeping a gap of about 50 μm to about 1 mm between a sidewall of each of the at least one piston and a housing, and ii) by rotating the at least one piston at a very high speed, either by a high shaft's speed, by rotating the piston on a circular orbit of a very high diameter, or both of high speed and a high rotation radius for the at least one piston's rotating motion.

For any rotary machine described herein, in some embodiments, one or more isolators of the at least one isolator seal the plurality of sub-chambers by having one or more walls of each isolator of the one or more isolate disposed at less than about 50 microns to about 1 mm in distance from one or more stationary walls of a housing of the rotary machine.

For any rotary machine described herein, in some embodiments, a wall of the at least one isolator creates a labyrinth with the chamber.

For any rotary machine described herein, in some embodiments, a thickness of one or more walls of an outer shell comprising the at least one chamber and one or more housings for the at least one isolator is minimized to prevent or reduce an increase in a gap between rotating and stationary parts of the rotating concentric machine due to thermal expansion of materials thereof.

For any rotary machine described herein, in some embodiments, material for rotating parts have a higher thermal expansion than housing material disposed around said rotating parts to prevent or reduce an increase in a gap between the rotating and stationary parts due to thermal expansion of materials thereof.

Any rotary machine described herein, in some embodiments, comprising an intake chamber configured to receive a working fluid and that follows a back side of a rotating piston; a compression chamber configured to compress the working fluid when being pushed by the rotating piston, thereby forming compressed a working fluid, the compression chamber separated from the intake chamber at least by an isolator; and an intake port, wherein upon the intake chamber and compression chamber becoming in fluid communication via the isolator, an orientation (perpendicular or with negative inclination compared to the stream direction of the working fluid), size (the opening size should be at least 50% and up to 90% smaller than the piston's diameter or size), location (as close as possible to the isolator's motion plane), or any combination thereof of the intake port enables the compressed working fluid to travel along the intake chamber and drag even more working fluid into the intake chamber from the intake port, thereby dragging even more intake working fluid into the intake chamber and preventing or reducing the amount of compressed working fluid leaving the intake chamber and/or compression chamber, so as to supercharge the rotary machine.

Any rotary machine described herein, in some embodiments, comprising an intake chamber configured to receive a working fluid and that follows a back side of a rotating piston; a compression chamber configured to compress the working fluid when being pushed by the rotating piston, thereby forming compressed working fluid, the compression chamber separated from the intake chamber at least by an isolator; and an intake valve, wherein upon the intake chamber and compressed chamber becoming in fluid communication via the isolator, the intake valve opens after at least one pressure wave developed during the fluid communication of the intake chamber with the compression chamber to pass said intake valve and travel along the intake chamber, thereby dragging even more intake working fluid into the intake chamber and preventing or reducing the amount of compressed working fluid leaving the intake chamber and/or compression chamber through the intake valve, so as to supercharge the rotary machine.

Any rotary machine described herein, in some embodiments, comprising an intake chamber of the plurality of sub-chambers configured to draw in a working fluid and that follows a back side of a rotating piston of the at least one piston; a compression chamber of the plurality of sub-chambers configured to compress the working fluid when being pushed by the rotating piston, thereby forming compressed working fluid, the compression chamber separated by the intake chamber at least by the at least one isolator; and an intake port, wherein upon the intake chamber and compressed chamber becoming in fluid communication via a receptacle in the at least one isolator, an orientation, size, location, or any combination thereof of the intake port enables the compressed working fluid to travel along the intake chamber and drag even more working fluid into the intake chamber, thereby dragging even more intake working fluid into the intake chamber and preventing or reducing the amount of compressed working fluid leaving the intake chamber and/or compression chamber, so as to supercharge the rotary machine.

Any rotary machine described herein, in some embodiments, comprising an intake chamber of the plurality of sub-chambers configured to draw in a working fluid and that follows a back side of a rotating piston of the at least one piston; a compressed chamber of the plurality of sub-chambers configured to compress the working fluid when being pushed by the rotating piston, thereby forming compressed working fluid, the compressed chamber separated by the intake chamber at least by the isolator; and at least one intake valve, wherein upon the intake chamber and compressed chamber becoming in fluid communication via a receptacle in the at least one isolator, the at least one intake valve opens after at least one pressure wave developed during the fluid communication of the intake chamber with the compression chamber passes said at least one valve and travels along the intake chamber, thereby dragging even more intake working fluid into the intake chamber and preventing or reducing the amount of compressed working fluid leaving the intake chamber and/or compression chamber through the intake valve, so as to supercharge the rotary machine.

Any rotary machine described herein, in some embodiments, further comprising one or more additional pistons, shafts, disc or rotors, shells, and/or isolators.

Any rotary machine described herein, in some embodiments, further comprising a plurality of pistons coupled to the at least one disc or rotor or a surface of the shaft.

Any rotary machine described herein, in some embodiments, the pistons are axis-symmetrically distributed on a periphery of the at least one disc or rotor periphery to weight-balance the piston-disc assembly.

Any rotary machine described herein, in some embodiments, a sidewall of the at least one pistons is toroidal or cylindrical.

A linear actuator for linear motion applications in automation, consisting of more than one linear sub-actuators with a same or different lift-time connected in series to lift at least one periodically reciprocating moving part, wherein a total lift is based on a sum of the lifts of all linear sub-actuators together.

Any rotary machine or mechanism described herein, in some embodiments, comprising a rotary valve assembly comprising three rotating sliding port (RSP) isolators arranged sequentially and having a minimum distance from each other, wherein a middle

RSP isolator is configured to rotate with a first angular velocity of a shaft of the at least one shaft, wherein two RSP isolators are disposed as outer RSP isolators in the sequential configuration and configured to rotate with a second angular velocity that is about double of the first angular velocity, wherein the the outer RSP isolators are rotating in opposite direction with each other.

Any rotary valve described herein, in some embodiments, wherein a first outer RSP isolator that directly faces a first sub-chamber of the plurality sub-chambers having a higher pressure than the remaining sub-chambers is thicker than the other two RSP isolators.

Any rotary valve described herein, in some embodiments, wherein the middle RSP isolator is thicker than a second outer RSP isolator that faces directly a second sub-chamber that is lower in pressure than the first sub-chamber.

In a preferred embodiment of the invention, the rotary valve may have at least one outer RSP isolator having a different shape for the piston-passing hole than the middle RSP isolator.

A method to weight-balance a rotating part or assembly of a rotary machine or mechanism described herein, in some embodiments, the method comprising removing material from at least one sidewall of said rotating part or assembly.

A method to counter balance an assembly or part of a rotary mechanism or machine described herein, in some embodiments, with a through-all hole of a rotary part or assembly, the method comprising to remove material from at least one sidewall opposite to the through-all hole's position.

A method to counter balance an assembly or part of a rotary mechanism or machine described herein, in some embodiments, with a through-all hole of a rotary machine, the method comprising to replace at least a portion of the rotating part or assembly with a heavier material at a region close to the through-all hole's position.

A method to counter balance an assembly or part of a rotary mechanism or machine described herein, in some embodiments, having an extra mass on a periphery of the rotating part or assembly that causes a center of mass of the rotating part or assembly to move out of a respective rotation axis, the method comprising: removing material from the rotating part or assembly at an opposite location of the extra mass; and adding a heavier material in the location.

A method to counter balance an assembly or part of a rotary mechanism or machine described herein, in some embodiments, comprising: removing material close to a location of the extra mass, wherein an area corresponding to the material removal comprises of two symmetrical or asymmetrical areas compared to a symmetry-axis of the rotating part or assembly.

A method to counter balance an assembly or part of a rotary mechanism or machine described herein, in some embodiments, locating one or more parts at the sidewalls of the rotating part or assembly perpendicular to the rotation axis, each having at least one material removal area configured to move the center of mass of the assembly at its rotation axis, wherein the material removal areas on each part may optionally be symmetrical or asymmetrical to each other.

A method to counter balance an assembly or part of a rotary mechanism or machine described herein, in some embodiments, by creating a cavity configuration inside a body of the assembly or part, wherein said cavity has an inclination compared to a horizontal or symmetry plane or any plane parallel to a symmetry plane in order to weight balance the assembly or part without a need of using any extra part with a higher weight-density as a counterweight, and wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part.

A method to counter balance an assembly or part of a rotary mechanism or machine described herein, in some embodiments, by creating a cavity configuration inside the body of the assembly or part, wherein an area corresponding to the cavity comprises two asymmetrical areas about a symmetry plane or a symmetry-axis or rotation-axis of the part or assembly in order to weight balance the assembly or part without a need of using any extra part with a higher weight-density as a counterweight, and wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part.

A method to counter balance an assembly or part of a rotary machine or mechanism described herein, in some embodiments, by creating a cavity configuration inside a body of the assembly or part, wherein said cavity is close to areas where high temperature is developed to create one or more walls on the assembly or part having a thickness that favors faster cooling of those hot areas.

A method to counter balance an assembly or part of a rotary machine or mechanism described herein, in some embodiments, by creating a cavity configuration inside a body of the assembly or part with a double role: to weight balance the assembly or part and also to cool areas of the assembly or part where high temperature is developed, where the area corresponding to the cavity comprises two asymmetrical areas about a symmetry plane or a symmetry-axis or rotation-axis of the part or assembly in order to weight balance the assembly or part without a need of using any extra part with a higher weight-density as a counterweight, wherein material removal of the assembly or part is avoided from areas where weight of such material is necessary to counterbalance the assembly or part; and wherein expanding the cavity configuration close to areas where high temperatures are developed, the cavity configuration creates one or more walls on the assembly or part having a thickness that favors faster cooling of those hot areas.

A rotary machine or mechanism described herein, in some embodiments, that is weight-balanced with any one method described above or any combination of methods described above.

A labyrinth sealing method for liquid and gaseous working fluids, comprising of at least one metal or non-metal labyrinth fin or knife; a layer of a softer metal or non-metal material; where one or more free edges of the at least one fin or knife comes into contact or forced contact with the softer metal or non-metal material during assembling of the labyrinth seal; the at least one fins or knife, as well as the layer of the softer metal or non-metal material are both stationary or both rotating parts, or where one is stationary and the other is rotating.

In some embodiments, a labyrinth sealing method based on above described labyrinths, wherein at least one screw that moves the at least one knife or fin away from the layer and, at least one other screw that moves the at least one knife or fin towards the layer, so as to arrange a distance between the at least one fin or knife and the layer.

A labyrinth sealing system for liquid and gaseous working fluids between two rotating or two stationary parts, or a stationary and a rotating part, comprising of at least one labyrinth system; and at least one shaft seal or seal ring operatively coupled with a labyrinth system of the at least one labyrinth system and configured to prevent or reduce an amount of a working fluid of the working fluids from escaping to a surrounding environment and/or to protect other components from a high-pressure of the working fluid.

A labyrinth sealing system for liquid and gaseous working fluids between two rotating or two stationary parts, or a stationary and a rotating part, comprising of at least two labyrinths systems in fluid communication, at least one having a vertical configuration, and at least one having a horizontal configuration (e.g., as shown in FIG. 22); and at least one shaft seal or seal ring (such as PTFE shaft seals) operatively coupled with at least one of the two labyrinth systems and configured to prevent or reduce the amount of the working fluid from escaping to the environment and/or to protect other components from the high-pressure of the working medium.

In some embodiments, a labyrinth sealing method based on above described labyrinths, where at least one labyrinth system comprises a small gap in the entrance of a labyrinth chamber that leads the working medium towards a curved wall within the labyrinth chamber; wherein the curved wall leads the working medium to contact an opposite wall and optionally pass through a second small gap, which is located opposite to the opposite wall, having an orientation that is optionally tangential to the end of the curved wall, and is optionally located at a minimum distance from the end of the curved wall, wherein the labyrinth chamber and a second labyrinth chamber comprises a parallel configuration (for example, labyrinth chambers shown in FIG. 22), and the small size and orientation of the second gap delays the working medium to pass through the second gap and enter the second labyrinth's chamber.

In some embodiments, a labyrinth sealing method based on above described labyrinths, where the orientation of the narrow pass between the labyrinth chambers (e.g., the passes (65) shown in FIG. 22) is not tangential to the curved wall (such as (65a)) but has an opposite slope (such as (65b)) than the fluid's stream direction or is perpendicular to the fluid's stream direction (pass (56) in FIG. 23).

In some embodiments, a labyrinth sealing method based on above described labyrinths, where the narrow pass between the labyrinth chambers has an opposite slope orientation and optionally a curved orientation (e.g., the curved pass (65b) shown in FIG. 22) so that the end of the pass becomes tangential to the curved wall (e.g., the curved wall (51a) shown in FIG. 22)

In some embodiments, a labyrinth sealing method based on above described labyrinths, where the limited space close to the shaft seal or ring does not allow for a vertical labyrinth and the latter is replaced by a wall or obstacle between the high-pressure working medium and the seal ring/shaft seal.

In some embodiments, a labyrinth sealing method based on above described labyrinths, where the limited space close to the shaft seal or ring does not allow for a vertical labyrinth and the latter is replaced by a washer or a ring-shaped part and a retaining ring between the high-pressure working medium and the seal ring/shaft seal.

In some embodiments, a labyrinth sealing method based on above described labyrinths, where the one of the two parts (rotating and/or stationary) to seal has a softer material than the other, so as to protect the labyrinth system design in case of a potential contact between the two parts.

In some embodiments, a labyrinth sealing method based on above described labyrinths, where the two parts (rotating and/or stationary) to seal have initially no gap between them but the labyrinth system is used to seal a potential gap between them, wherein the one of the two parts has a softer material than the other.

In some embodiments, a labyrinth sealing method based on above described labyrinths, wherein there is at least one hole on the stationary part and at least one leading wall on the rotating part to protect the bearings of a possible sealing malfunction, by preventing any high-pressure leakage at the end of the sealing system to go against the bearings and, wherein the leading wall leads the leaked high-pressure working fluid through the holes directly to the environment.

A gaseous or liquid sealing method between a stationary and a moving wall that is created by constructing the stationary wall with very low roughness, the rotating wall with a very high roughness (N11 or N12), and putting them at a distance of less than about 1 mm; 50 to 100 microns for small applications and up to 1 mm for heavy-duty applications.

A gaseous or liquid sealing method between a stationary and a moving wall that is created by constructing the stationary wall with very low roughness, and on the rotating wall's surface (internally or externally) are configured very thin knives or fins, wherein free edges of the knives or fins teeth are very close to the stationary wall, less than about 1 mm; 50 to 100 microns for small applications and up to 1 mm for heavy-duty applications.

In a preferred embodiment of the gaseous or liquid sealing method of the invention, the knives or fins are not perpendicular to the outer surface of the rotating wall but in angular orientation (e.g. detail 47 of FIG. 15 or knives of FIG. 20 and FIG. 21).

A sealing method wherein no piston rings are located around the pistons of machines to seal the gap between the pistons and the internal surface of the machine's chambers, but the leakage between these two components is limited by keeping a gap of less than about 1 mm between the piston's sidewall and the housing and by rotating the piston at a very high speed, either by a high shaft's speed or by rotating the piston on a circular orbit of a very high diameter; it is 50 to 100 microns for small size applications and around 1 mm for heavy-duty applications.

A sealing method for rotary sliding ports or rotary valves wherein their sidewalls have their moving walls at a less than 1 mm distance from the stationary walls of the housing; it is 50 to 100 microns for small size applications and around 1 mm for heavy-duty applications

A sealing method between rotating and stationary walls wherein the gap between the moving and stationary walls is between 50 microns to 1 mm; it depends on the size of the application. A small size application requires a distance of 100 microns or less, while larger applications may have a gap of up to 1 mm.

Any machine, wherein the walls of the outer shell (housing) is the thinnest possible to prevent its significant thermal expansion.

A machine with a sealing method between moving and stationary walls that has the moving walls at a less than 1 mm distance from the stationary walls, wherein the materials of the moving parts have a higher thermal expansion than the stationary materials to prevent the gap between the moving and stationary parts from increasing significantly due to their thermal expansion.

A rotary machine with a sealing method between rotating and stationary walls that has the moving walls at a less than 1 mm distance from the stationary walls, wherein the materials of the rotating parts have a higher thermal expansion than the stationary materials to prevent the gap between the rotating and stationary parts from increasing significantly due to their thermal expansion

An assembly method between two stationary parts that come in contact through a sealing flange wherein there is a protrusion along interior configurations of at least one of the two stationary parts to prevent any intersection of the sealing flange with any moving part.

Additional Exemplary Embodiments

Embodiment 1: A rotary concentric machine comprising: at least one piston that rotates on a circular orbit concentrically located with the machine's shaft, wherein the piston is coupled directly on the cylindrical surface of a machine's shaft, thereby forming a piston-shaft assembly; at least one shaft where at least one disc or rotor is coupled to; at least one shell that forms a chamber, wherein the pistons are rotating within the at least one chamber; at least one RSP isolator that periodically separates the at least one chamber into a plurality of sub-chambers; at least one outlet port; and at least one intake port.

Embodiment 2: A rotary concentric machine comprising: at least one piston that rotates on a circular orbit concentrically located with the machine's shaft, wherein the piston is one body with the cylindrical surface of a machine's shaft, thereby forming a piston-shaft part; at least one shaft where at least one disc or rotor is coupled to; at least one shell that forms a chamber, wherein the pistons are rotating within the at least one chamber; at least one RSP isolator that periodically separates the at least one chamber into a plurality of sub-chambers; at least one outlet port; and at least one intake port.

Embodiment 3: A rotary concentric machine comprising: at least one piston that rotates on a circular orbit concentrically located with the machine's shaft, wherein the piston is coupled on at least one disc or rotor that is coupled to any machine's shaft, thereby forming a piston-disc or piston-rotor assembly; at least one disc or rotor where said pistons are coupled to; at least one shaft where at least one disc or rotor is coupled to; at least one shell that forms a chamber, wherein the pistons are rotating within the at least one chamber; at least one RSP isolator that periodically separates the at least one chamber into a plurality of sub-chambers; at least one outlet port; and at least one intake port.

Embodiment 4: A rotary concentric machine comprising: at least one piston that rotates on a circular orbit concentrically located with the machine's shaft, wherein the piston is one body with at least one disc or rotor that is coupled to any machine's shaft, thereby forming a piston-disc or piston-rotor part; at least one disc or rotor where said pistons are coupled to; at least one shaft where at least one disc or rotor is coupled to; at least one shell that forms a chamber, wherein the pistons are rotating within the at least one chamber; at least one RSP isolator that periodically separates the at least one chamber into a plurality of sub-chambers; at least one outlet port; and at least one intake port.

Embodiment 5: The rotary machine of embodiment 1 or 2, where the piston-shaft assembly or part has at least one cavity configuration serving as a weight balance configuration, wherein said cavity has an inclination compared to any horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane (like the one shown in FIG. 19-D) in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part.

Embodiment 6: The rotary machine of embodiment 3 or 4, where the piston-disc or piston-rotor assembly or part has at least one cavity configuration serving as a weight balance configuration, wherein said cavity has an inclination compared to any horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane (like the one shown in FIG. 19-D) in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part.

Embodiment 7: The rotary machine of embodiment 1 or 2, where the piston-shaft assembly or part has at least one cavity configuration serving as a weight balance configuration, wherein the area corresponding to the material removal may comprise of two asymmetrical areas compared to a “symmetry” plane or a symmetry- or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part.

Embodiment 8: The rotary machine of embodiment 3 or 4, where the piston-disc or piston-rotor assembly or part has at least one cavity configuration serving as a weight balance configuration, wherein the area corresponding to the material removal may comprise of two asymmetrical areas compared to a “symmetry” plane or rotation- or symmetry-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part.

Embodiment 9: The rotary machine of embodiment 1 or 2, wherein the piston-shaft assembly or part has a cavity configuration close to areas of the assembly or part where high temperature is developed to create walls with a thickness that favors the faster cooling of those hot areas.

Embodiment 10: The rotary machine of embodiment 3 or 4, wherein the piston-disc or piston-rotor assembly or part has a cavity configuration close to areas of the assembly or part where high temperature is developed to create walls with a thickness that favors the faster cooling of those hot areas

Embodiment 11: The rotary machine of embodiment 1 or 2, wherein the piston-shaft assembly or part has a cavity configuration with a double role: to weight balance the piston-shaft assembly or part but also to cool areas where high temperature is developed, by having an inclination compared to any horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane (like the one shown in FIG. 19-D) in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part; and by expanding the cavity configuration close to areas of the assembly or part where high temperatures are developed to create walls with a thickness that favors the faster cooling of those hot areas.

Embodiment 12: The rotary machine of embodiment 3 or 4, wherein the piston-disc or piston-rotor assembly or part has a cavity configuration with a double role: to weight balance the piston-disc or piston-rotor assembly or part but also to cool areas where high temperature is developed, by having an inclination compared to any horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane (like the one shown in FIG. 19-D) in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part; and by expanding the cavity configuration close to areas of the assembly or part where high temperatures are developed to create walls with a thickness that favors the faster cooling of those hot areas.

Embodiment 13: The rotary machine of embodiment 1 or 2, wherein the piston-shaft assembly or part has a cavity configuration with a double role: to weight balance the piston-shaft assembly or part and to cool areas where high temperature is developed, by having a cavity configuration inside the body of the assembly or part with a double role: to weight balance the assembly or part but also to cool areas of the assembly or part where high temperature is developed, where the area corresponding to the material removal may comprise of two asymmetrical areas compared to a “symmetry” plane or a symmetry- or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part; and by expanding the cavity configuration close to areas where high temperatures are developed to create walls with a thickness that favors the faster cooling of those hot areas.

Embodiment 14: The rotary machine of embodiment 3 or 4, wherein the piston-disc or piston-rotor assembly or part has a cavity configuration with a double role: to weight balance the piston-shaft assembly or part and to cool areas where high temperature is developed, by having a cavity configuration inside the body of the assembly or part with a double role: to weight balance the assembly or part but also to cool areas of the assembly or part where high temperature is developed, where the area corresponding to the material removal may comprise of two asymmetrical areas compared to a “symmetry” plane or a symmetry- or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part; and by expanding the cavity configuration close to areas where high temperatures are developed to create walls with a thickness that favors the faster cooling of those hot areas

Embodiment 15: Embodiment 5: A method to counter balance an assembly or part by creating a cavity configuration inside the body of the assembly or part, wherein said cavity has an inclination compared to any horizontal or “symmetry” plane or any plane parallel to a “symmetry” plane (like the one shown in FIG. 19-D) in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part.

Embodiment 16: A method to counter balance an assembly or part by creating a cavity configuration inside the body of the assembly or part, wherein the area corresponding to the material removal may comprise of two asymmetrical areas compared to a “symmetry” plane or a symmetry- or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part.

Embodiment 17: A method to counter balance an assembly or part by creating a cavity configuration inside the body of the assembly or part, wherein said cavity is close to areas where high temperature is developed to create walls with a thickness that favors the faster cooling of those hot areas.

Embodiment 18: A method to counter balance an assembly or part by creating a cavity configuration inside the body of the assembly or part with a double role: to weight balance the assembly or part but also to cool areas of the assembly or part where high temperature is developed, by having a cavity configuration inside the body of the assembly or part, where the area corresponding to the material removal may comprise of two asymmetrical areas compared to a “symmetry” plane or a symmetry- or rotation-axis of the part or assembly in order to weight balance the assembly or part without the need of using any extra part with a higher weight-density as a counterweight, avoiding the material removal from areas where their weight is necessary to counterbalance the assembly or part; and by expanding the cavity configuration close to areas where high temperatures are developed to create walls with a thickness that favors the faster cooling of those hot areas.

Embodiment 19: The rotary machine of embodiment 1 or 2 or 3 or 4, comprising of a rotary RSP isolator that defines a receptacle configured to receive the piston when the latter reaches the RSP isolator's periphery, wherein the RSP isolator has an extra cavity configuration in fluid communication with said receptacle to keep low the pressure developed at the front side of the piston when the piston is entering into said receptacle.

Embodiment 20: The rotary machine of embodiment 19, wherein said receptacle has an orientation to favor the expansion of the trapped working fluid between the piston and the RSP isolator

Embodiment 21: The rotary machine of embodiment 19, wherein said receptacle has its opening opposite to the piston's front side, when the piston reaches the periphery of the RSP isolator.

Embodiment 22: The rotary machine of embodiment 19, wherein said receptacle has a bigger size than said receptacle.

Embodiment 23: The rotary machine of embodiment 19, wherein the area corresponding to the material removal of said cavity configuration may comprise of two symmetrical or asymmetrical areas compared to a “symmetry” plane or a symmetry- or rotation-axis of the RSP isolator's part or assembly.

Embodiment 24: The rotary machine of embodiment 23, where the area corresponding to the material removal of said cavity configuration may comprise of two asymmetrical areas compared to a a “symmetry” plane or a symmetry- or rotation-axis of the RSP isolator's part or assembly, wherein the largest area of said cavity configuration may be located close to the area of the RSP isolator where high pressure is developed. Each numerical value presented herein, for example, in a table or a chart, is contemplated to represent an exemplary value in a range for a corresponding parameter. Accordingly, when added to the claims, the numerical value provides support for claiming a range around that value, which may lie above or below the numerical value, according to the teachings herein. Absent inclusion in the claims, each numerical value presented herein is not to be considered limiting in any regard.

Description of a concentric rotary machine that can be used as a compressor, expander, pump, or intake-compression and/or the combustion-expansion chamber of an internal combustion engine. This machine has at least one chamber and at least one isolator (sliding port). The latter may be linear or rotary, and it periodically separates the chamber into two sub-chambers. In the case of a compressor, the two sub-chambers are the compression & intake chamber. In the case of an expander, the two sub-chambers are the expansion & removal chamber. In the case of a pump, the two sub-chambers are the intake & removal chamber. In the case of the internal combustion engine, the two sub-chambers may be the intake & compression chamber or the combustion/expansion and exhaust removal chamber. At least one piston lies directly or at a distance from the machine's shaft, and it rotates around the shaft's rotation axis. In some embodiments, the piston rotates around the main shaft's rotation axis. The piston as well as the disc or rotor where the piston is adjusted on may contain a cavity that may have a double role; as a weight balance configuration and/or as a cooling mean. In other embodiments, apart from the at least one piston-pass gap (receptacle to host the piston when the piston reaches the RSP isolator's periphery) that said RSP isolator may have to allow for said piston to pass through the RSP isolator's body, said RSP isolator may contain at least one extra cavity in fluid communication with said piston-pass gap. The role of said cavity is to avoid high pressures developed during the passing of the piston through any piston-pass gaps of said RSP isolator. A central controlling system that controls at least one valve at the intake and outlet port may control the amount of working fluid provided to the machine and the duration of the processes. Last but not least, the same system may also control the opening and closing of the isolator (sliding port) to arrange optimized isolation of the chambers (compression/expansion ratio). Description of a concentric rotary machine that can be used as a compressor, expander, pump, or intake-compression and/or the combustion-expansion chamber of an internal combustion engine. This machine has at least one chamber and at least one isolator (sliding port). The latter may be linear or rotary, and it periodically separates the chamber into two sub-chambers. In the case of a compressor, the two sub-chambers are the compression & intake chamber. In the case of an expander, the two sub-chambers are the expansion & removal chamber. In the case of a pump, the two sub-chambers are the intake & removal chamber. In the case of the internal combustion engine, the two sub-chambers may be the intake & compression chamber or the combustion/expansion and exhaust removal chamber. At least one piston lies directly or at a distance from the machine's shaft, and it rotates around the shaft's rotation axis. In some embodiments, the piston rotates around the main shaft's rotation axis. The piston as well as the disc or rotor where the piston is adjusted on may contain a cavity that may have a double role; as a weight balance configuration and/or as a cooling mean. In other embodiments, apart from the at least one piston-pass gap (receptacle to host the piston when the piston reaches the RSP isolator's periphery) that said RSP isolator may have to allow for said piston to pass through the RSP isolator's body, said RSP isolator may contain at least one extra cavity in fluid communication with said piston-pass gap. The role of said cavity is to avoid high pressures developed during the passing of the piston through any piston-pass gaps of said RSP isolator. A central controlling system that controls at least one valve at the intake and outlet port may control the amount of working fluid provided to the machine and the duration of the processes. Last but not least, the same system may also control the opening and closing of the isolator (sliding port) to arrange optimized isolation of the chambers (compression/expansion ratio).

Number	Date	Country	Kind
20210100798	Nov 2021	GR	national
20220100315	Apr 2022	GR	national

	Number	Date	Country
Parent	PCT/GR2022/000661	Nov 2022	WO
Child	18664602		US

CONCENTRIC ROTARY MACHINE

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Abstract

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Priority Claims (2)

CROSS-REFERENCE TO RELATED APPLICATIONS

Continuation in Parts (1)