JP2008504488A - Rotary device and method of operating rotary device - Google Patents

Abstract

The present invention is a rotary expander having a chamber for receiving a charge comprising an air / fuel mixture and oxidizing fuel by detonation, and a temporary chamber of varying volume, the temporary chamber being in the rotational expansion A rotary expander in fluid communication with the detonation chamber in at least a portion of a cycle of rotation of the machine, wherein the rotary expander is caused by expansion of the air / fuel mixture caused by air / fuel mixture detonation. The present invention relates to a rotary device configured to be driven.
[Selection] Figure 1

Description

  The present invention relates to a rotary device and a method for operating the rotary device.

  In certain embodiments, the present invention is directed to International Patent Application No. WO-A-91 / 06747, the entire contents of which are hereby incorporated by reference herein, as well as granted US Patent No. US-B-6168385. And the development of the method and apparatus described in US-B-6176695.

  Detonation is a process in which a gaseous mixture of fuel distributed in air or oxygen is subjected to oxidation, which releases heat in a more rapid manner than occurs in combustion or deflagration caused by a flame. It is a process to accompany. Detonation is usually initiated by the ignition of an air / fuel mixture. The detonation of the air / fuel mixture causes the generation of shock waves as a result of the expansion of the air / fuel mixture due to the heat generated by the process. During detonation, the shock wave travels through a gas mixture (charge gas) at a Mach number much higher than that possible for a flame during deflagration, typically greater than one.

  It has been demonstrated that detonation can occur in a cylinder that is closed at one end and open at the other end. Fuel and air charges are introduced into the cylinder through a valve or port at the closed end where the igniter is located. The shock wave passes through the cylinder at a very high rate when initiated by a sudden expansion of the air / fuel mixture ignited in the igniter. As the charge gas exits the open end of the cylinder at high speed as a result of the expansion caused by the release of detonation heat, a large thrust is generated. Multiple cylinders can be arranged to form a thrust generation engine that sequentially generates detonation. See, for example, US Pat. No. 5,345,758, which describes such a system.

  It is known that charge gas pressure and density changes occur in each detonation cycle. The gas density is maximum at the front of the forward shock wave where the thermochemical reaction of the air / fuel mixture is initiated. In contrast, a dilute wave with a very low gas density occurs immediately after the shock wave. The expansion of the gas resulting from the release of heat in the reaction zone functions to drive the gas out of the open end of the chamber, leaving behind a low density or quasi-vacuum region. In a pulse detonation engine, this quasi-vacuum is used to quickly fill the cylinder again with the next air and fuel charge.

U.S. Pat. No. US-47441154 discloses a rotary detonation engine. The engine has a detonation chamber and a plurality of turbine blades arranged to be driven by a charge of the post-detonation air / fuel mixture received from the detonation chamber. This engine relies on the catherine-wheel effect to drive the rotor. This engine does not allow efficient conversion of energy from detonation into rotational force. Furthermore, since the turbine blades are exposed to fluctuating force from detonation, efficient energy conversion cannot be performed, and the turbine blades are easily damaged by fatigue.
WO-A-91 / 06747 US-B-6168385 US-B-6176695 US-A-5345758 US-A-47441154

  According to a first aspect of the invention, there is provided a rotary expander having a chamber for receiving a charge comprising an air / fuel mixture and oxidizing the fuel by detonation and a temporary chamber of varying volume, The temporary chamber having a rotary expander in fluid communication with the detonation chamber in at least a portion of a rotation cycle of the rotary expander, wherein the rotary expander is generated by detonation of an air / fuel mixture. A rotary device is provided that is configured to be driven by the expansion of an air / fuel mixture.

  The present invention provides a rotary device that allows the rotational force to be obtained from the detonation process. In contrast to the devices previously disclosed to be used to obtain rotational force from the detonation process, such as, for example, the device described in US Pat. No. US-47441154, in the present invention in a rotary device A rotary expander is provided that provides an efficient means for extracting power from the generated expanded gas.

  The present invention appears to provide several significant advantages when compared to Otto cycle, diesel cycle, and gas turbine cycle engines, using rotary expanders to release the energy released from the fuel. Provide a rotary device that can be converted into axial force. In all these engines, the process of fuel oxidation begins only after the fuel-air mixture has been compressed, i.e., has reached a temperature and pressure level significantly higher than the atmosphere. In Otto and diesel cycle engines, the release of heat during combustion raises the temperature and pressure to very high levels. This has several drawbacks. First, the engine must be constructed of a material that can withstand large thermal and physical stresses and that can seal the gas charge in the combustion chamber. Because of the large thermal and physical stresses, some thermal and leakage losses are unavoidable in this process.

  Second, in the case of a piston engine, the combustion process is typically 20-90 degrees, but extends to an angle near the top dead center (TDC) position of the piston. This means that the part of the heat release that occurs before TDC adds negative work to the compression, which is this half of the Otto or Diesel cycle (ie, compression-combustion-expansion stage). This means that in order to be able to generate net work on the piston, it must recover upon expansion after TDC. The sealing of the charge during this period creates considerable friction because the piston ring seals the gap between the piston and cylinder wall. This friction is in the intake and exhaust phases of these cycles and constitutes a further loss of internal power in these engines.

  In the case of a gas turbine engine, the release of heat during combustion does not result in a further pressure increase and gas expansion occurs at the pressure generated by the compressor. However, the work done by the compressor represents a significant portion of the work recovered by the expansion turbine system, and the considerable negative work that must be overcome in order for the turbine to deliver the net surplus of power. Constitute.

  The rotary device of the present invention does not suffer from any of these disadvantages. Prior to fuel oxidation, little or no force is applied to the working fluid from external sources, such as flywheel inertia. As a result of the oxidation being achieved by detonation, most or all of the compression is generated locally in the reaction region of the working fluid charge, i.e. by a thermo-chemically derived shock wave. As a result, the pressure and temperature throughout the engine is much lower than the pressure and temperature in piston and gas turbine engines. Because of the smaller heat gradient, the potential for heat loss is greatly reduced.

  Furthermore, since there is no large pressure gradient, leakage loss from the working fluid charge can also be kept at a very low level without the need for a physical or mechanical seal, thus creating internal friction loss. Avoided. Thus, the potential energy of the fuel is converted directly into working fluid expansion with minimal internal loss. Gas expansion is efficiently converted to shaft output by the rotary expander while minimizing losses during the expansion process, thus reducing internal losses resulting in a highly efficient rotary device.

  According to a second aspect of the present invention, there is provided a method of operating a rotary device having a detonation chamber in fluid communication with a temporary chamber of a rotary expander, wherein the detonation chamber comprises a gas / fuel mixture charge. And a step of detonating the mixture to expand the gas / fuel mixture and drive a rotary expander.

  Next, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

  1-3 are diagrams of a portion of an example of a rotary device according to an embodiment of the present invention. In the illustrated embodiment, the apparatus has a compressor 2, a detonation chamber 4, and an expander 6 disposed in a housing defined by walls (not all shown). ing. The detonation chamber 4 is accommodated inside a stator cylinder 3 which will be described in more detail later. An intermediate wall 10 is provided so as to separate the compressor and the expander.

  In general, the compressor 2 is arranged to compress a charge comprising an air / fuel mixture and supply it to the detonation chamber 4. The compressor 2 and the expander 6 are each composed of two rotors (5 and 7 for the compressor; 16 and 18 for the expander) arranged to rotate in opposite directions around a parallel axis. Has been. In FIG. 1, the expander rotors 16 and 18 are clearly visible. In FIG. 2, the expander rotor and intermediate wall 10 have been removed so that the compressor rotor can be clearly seen.

  The rotors 5, 7, 16, and 18 of both the expander and compressor are arranged in the housing, but only one end wall 8 and intermediate wall 10 of the housing are shown in FIG. . An additional wall (not shown) is provided to surround the stator cylinder 3 and the rotor arranged to rotate about the stator cylinder 3.

  Openings 12 and 14 are provided in the wall of the housing. The openings 12 and 14 are provided so that movable and irregularly confined walls can be inserted into the rotary device. As will be described below, the containment wall (shown in cross section in FIGS. 4A-4H and 5A-5H) can vary the maximum volume possible for each temporary chamber of the compressor and expander. To.

  In use, when a charge consisting of an air / fuel mixture is in an appropriate turbulent state in the detonation chamber 4, the mixture is ignited. This causes detonation of the air / fuel mixture, resulting in a supersonic shock wave being propagated through the detonation chamber 4 to the expander 6. As a result, the gas in the detonation chamber and expander expands, causing the expander rotor to rotate. A rotating expander is connected to the drive shaft to extract rotational force from the device.

  More specifically, the rotary device shown in FIG. 1 has a detonation chamber 4 in a stator cylinder having an axial port (not shown in FIG. 1) towards either end. ing. Axial ports 20 and 32 can be seen in FIG. 3 and can also be seen in the cross sections of FIGS. 4A-4H and 5A-5H. One of the axial ports 20 allows communication between the rotor recess with the compressor recess and the detonation chamber. The other of the axial ports 32 allows communication between the recess of the rotor with the recess of the expander and the detonation chamber.

  In the illustrated example, both the compressor and the expander are formed by respective rotor recesses 7 and 18 and protrusions 5 and 16 configured to rotate about their respective axes. Each compressor and expander rotor is most preferably described in WO-A-91 / 06747, the entire contents of which are incorporated herein by reference. Of the form.

  Referring to the expander 6 that can be clearly seen in FIG. 1, the rotor 16 with projections is identical in shape and cooperates with the recesses R, S and T of the rotor 18 with recesses during rotation. It has the radial convex parts P and Q shaped so as to. This functions to define a temporary chamber whose volume changes between the interacting protrusions and recesses. As described below, the temporary chamber is used to receive expanding gases and extract energy from them.

  Referring now to the compressor, a gaseous working fluid, for example an air / fuel mixture, is supplied to the housing surrounding the compressor rotor pairs 5 and 7 and the compressor recessed rotor 7 Fill the recess. In the compression cycle, the convex part from the convex rotor 5 enters one of the concave parts of the concave rotor 7 to charge the air / fuel mixture for cooperating concave rotor. It begins when it is caught in a temporary chamber defined by the surface of the convex part of the rotor 5 with the concave part 7 and the convex part. The cycle of operation of the rotary device is described in more detail below.

  The recessed rotors 7 and 18 of both the compressor and the expander have axial central holes 9 and 11. Further, each of the rotors 7 and 18 with recesses is provided with a passage (shown in FIGS. 4A-4H and 5A-5H) connecting the rotor recesses to the rotor holes. Each of the rotor holes 9 and 11 fit closely adjacent to the outer surface of the stator cylinder 3, and a detonation chamber 4 is defined inside the stator cylinder 3. This allows each of the ports of the stator cylinder 3 to communicate with the inlets of the short passages leading to the respective recesses of the rotor in the appropriate part of the rotating arc, and thus between the respective rotor pairs. Can be communicated to a temporary chamber formed.

  The stator cylinder 3 defining the detonation chamber 4 is supported at each end by two outer walls 8 of the housing (the other not shown), each of the outer walls of the housing being in the compressor The outer end faces of the rotor pairs 5 and 7 and the outer end faces of the expander rotor pairs 16 and 18 provide a tightly fitted support. The end walls are provided to close both ends of the stator cylinder 3 to define a detonation chamber. Preferably, the compressor side end wall of the detonation chamber 4 is a spark plug (not shown) or any other suitable means for igniting a charge in the detonation chamber, such as an ignition device. Provides a place for.

  Both compressor and expander rotor pairs (5 and 7; 16 and 18) can be provided with movable containment walls (shown in cross section in FIGS. 4A-4H and 5A-5H). . The movable confining wall body is preferably a slidable member provided so that the amount of pushing out the working fluid of the rotary device can be varied during operation. The pushing amount of the working fluid can be changed according to, for example, a change in load, or can be changed so as to maintain a constant output even if the altitude changes in a specific application.

  In a preferred embodiment, a grid (discussed in detail below with respect to FIG. 6) is attached to a short passage leading from the compressor temporary chamber to the detonation chamber. The grid is an example of a component that is suitable for creating microscale turbulence in the charge gas as it leaves the compressor temporary chamber and enters the detonation chamber. This micro-scale turbulence creates a very small size turbulent vortex structure in the gas flow while being very strong and produces a higher order local average gas velocity. This unique form of turbulence is a precursor to the detonation process that immediately follows in the detonation chamber.

  The turbulence increases the local gas dynamic energy of the air / fuel mixture to a high level so that the high level of latent reactivity required for effective detonation of charge is produced. The grid also affects the overall flow of charge through the passage, providing good uniformity in micro level turbulence and fuel distribution throughout the charge prior to the onset of detonation. Once in the detonation chamber (and possibly the inflating temporary chamber of a rotating expander), the charge is ignited and detonation occurs. Detonation causes a rapid expansion of the gas, and this expansion is used to drive the rotary expander.

  4A-4H show the shape of the rotor end at each stage of the cycle for the compressor portion of the rotary device. It will be appreciated that the rotary device can operate without a compressor, i.e. the air / fuel mixture may be fed directly to the detonation chamber at atmospheric pressure. 4A to 4H each show a cross-sectional shape passing through a rotor with a convex portion, a rotor with a concave portion, and a movable confinement wall at a point close to the gas intake end of the rotary device. The containment wall is shaped to engage the first and second rotors to define a temporary chamber between the containment wall and the first and second rotors, It is movable so that the maximum volume possible for this temporary chamber can be varied.

  The center of the rotor with the recess is hollow and fits tightly into a stator cylinder having a hollow interior defining a detonation chamber and rotates about the stator cylinder. The stator cylinder has a port 20, and each recess of the rotor with a compressor recess communicates with the stator cylinder port 20 during a portion of the rotor's rotation cycle about the stator cylinder. have. The hollow interior of the stator cylinder functions as a detonation chamber for the rotary device.

  Referring to FIG. 4A, when the rotor rotates in the direction shown (the rotor with the convex portion rotates in the clockwise direction and the rotor with the concave portion rotates in the counterclockwise direction), the convex portion P and the recess R approach each other. The engagement of the convex portion P and the concave portion R and the movable confining wall body 26 functions to capture the temporary volume J in the movable wall body 26. The end of the movable wall is shown. This wall is tapered along the axial length of the rotor. As the wall moves along a path parallel to the axial direction of the rotor, the maximum volume possible for the temporary chamber changes due to the tapered shape of the wall. This is described in detail in US Pat. No. US-B-6176695, the entire contents of which are hereby incorporated by reference herein. Means such as automatic means for moving the wall 26 described therein may be provided.

  Referring now to FIG. 4B, the fluid contained in the temporary volume J is now captured and compressed as the rotor continues to rotate.

  Referring now to FIG. 4C, the temporary volume J is compressed, but the fluid remains captured because the recessed rotor passage 22 has not yet rotated to the position corresponding to the port 20.

  In FIG. 4D, the temporary volume J is now completely sealed by the surface of the convex part P and the concave part R. The leading edge of the recessed rotor passage 22 now reaches the open edge of the port 20, and fluid flow through the port begins to occur. At this stage, the pressure of the fluid being captured reaches the pressure of the receiver, and further rotation of the rotor gradually charges the compressed gas in the variable volume chamber between the ridges R and P. Sent out.

  In FIG. 4E, the leading edge of the recessed rotor passage 22 now traverses the port 20 to about half, increasing the variable flow area at the throat of the port 20. In FIG. 4F, the recessed rotor passage 22 is now aligned with the port 20 to provide maximum flow area for charge delivery.

  In FIG. 4G, the trailing edge of the recessed rotor passage 22 is now approaching the closing edge of the port 20 and the port is beginning to close. The remaining temporary volume is very small and therefore still contains a small amount of charge to be transferred through the port.

  Finally, in FIG. 4H, the temporary volume is now completely gone, leaving only the clearance volume between the surface of the projection P and the surface of the recess R. The closure of the port 20 coincides with the completion of the compression action that occurs when the tip of the projection reaches the point of the pocket's minimum radius. A new temporary volume is now formed between the next pair of protrusions and recesses. At this stage, all of the charge of the air / fuel mixture is compressed and now housed in a detonation chamber, and possibly a temporary chamber of the expander, defined by the interior of the stator cylinder.

  At some point during the compression cycle described above with reference to FIGS. 4A-4H, a temporary chamber is formed between the concave and convex portions of the expander rotor. The volume of this temporary chamber increases in the cycle to allow for detonation gas expansion from the charge. In fact, as described below, in a preferred embodiment, the temporary chamber receives a certain amount of compressed charge so that the temporary chamber of the expander also functions as a chamber where detonation occurs. The relative injection of the expander cycle with respect to the compressor and detonation timing, and the extent to which the expander cycle begins and continues for later stages of the compression cycle, are described in detail below. First, the expander and the expansion cycle will be described in detail.

  5A-5H show the shape of the end of each stage of the cycle for the expander of the rotary device. Referring to FIG. 5A, the cycle of the expander is such that when the convex surface U and the concave surface W of the engaging rotor pair pass the point of maximum entry of the convex part, that is, the convex part tip is concave. Begins when the point of the minimum radius of the surface W is passed. At this stage, the leading edge of the recessed rotor passage 30 approaches the open edge of the port 32 in the stator cylinder 16 to which the supply of pressurized fluid is being accessed. Referring to FIG. 5B, as the port 32 opens, the pressurized fluid enters the rotor passage 30 with the recesses and enters the temporary volume newly formed between the projections and the recesses.

  Referring to FIG. 5C, the port 32 is now fully open, providing maximum flow capacity for the pressurized fluid to pass to a temporary volume defined between the convex surface U and the concave surface W. . This minimizes the pressure difference between the pressure of the fluid supply and the pressure occurring in the temporary volume. The pressure of the pressurized fluid acts on the surface U of the convex part and the surface W of the concave part and pushes the rotor further in the direction of rotation. There is a high possibility that the pressure of the fluid is not large and that it does not have a sufficient effect in driving the expander rotor. The means of driving occurs when detonation occurs in the air / fuel mixture contained in the stator cylinder 18 and the temporary volume of the expander.

  In FIG. 5D, the trailing edge of the rotor passage 30 with the recess approaches the closing edge of the port 32 and begins to shut off the pressurized fluid supply to the chamber defined between the protrusion and the recess. Yes.

  In FIG. 5E, the trailing edge of the recessed rotor passage 30 reaches the closed edge of the port 32, blocking the supply of pressurized fluid and isolating fluid that has already entered the temporary volume. By this stage of the cycle, the air / fuel mixture has generated detonation, creating shock waves, effectively transferring the entire charge to the expander, causing rapid expansion of the charge gas, Drive rotation. At the same time, a dilute wave is formed behind the shock wave. This lean wave creates a low pressure that tends to be filled by the next charge of the air / fuel mixture entering the detonation chamber and the expansion chamber.

  As can be seen in FIG. 5F, the rotation of the rotor causes an increase in the temporary volume, allowing the trapped fluid to expand, and maintaining some pressure on the surface U and the surface W of the recess. Then, energy is continuously applied to the rotation of the rotor and the shaft to which the rotor can be connected.

  Referring to FIG. 5G, the temporary volume reaches a maximum capacity and the fluid reaches atmospheric pressure. At this point, the fluid stops applying net pressure to the convex surface U and concave surface W prior to release to the housing surrounding the rotor pair.

  Finally, in FIG. 5H, the fully expanded fluid can be released from the temporary volume and released to the exhaust system under the natural pumping action of the rotor pair in the housing.

  FIG. 6 shows a schematic diagram of a cross-section through an example of a grid used in the passage between the compressor and the detonation chamber. The grating can be formed of a plurality of elements each having a sharp edge. As the gas flows at high speed through the space between the elements, the sharp edges cause a substantial microscale turbulence of the gas. This is desirable in this context to ensure that the charge of the air / fuel mixture in the detonation chamber has a high potential reactivity required for effective detonation of the charge. In the example illustrated in FIG. 6, the lattice includes a plurality of elements having a triangular cross section. As the gas passes through the space between the elements, the sharp edges of the lattice on the detonation chamber side make the nearby gas flow extremely turbulent and ensure a high potential reactivity of the air / fuel mixture.

  Next, each stage in the operation cycle of the rotary device of FIGS. Reference is made to FIG. In the example cycle described here, the rotary device is equipped with a compressor, but as already mentioned, a compressor is not necessarily required.

  Compression begins when the tip of the compressor protrusion and the leading edge of the compressor recess coincide with the respective outer edge of the compressor movable containment wall. This coincidence is shown at the zero position on the scale of the angular position of the rotor with projections in FIG. A temporary compression chamber is formed and its volume decreases as the compressor rotor continues to rotate.

  After 6 degrees of rotation, the fill port begins to open, allowing communication between the compressor temporary chamber and the detonation chamber. Air or premixed air / fuel then enters the detonation chamber from the compressor temporary chamber. After another 20 degrees, the discharge port begins to open and some of the new charge can enter the temporary chamber of the expander. Thereafter, filling with fresh working fluid continues for an additional 54 degrees and fresh charge is distributed between the detonation chamber and the gradually expanding expander temporary chamber. Then, when the remaining volume in the compressor's temporary chamber reaches zero, the fill port closes and charge detonation begins immediately.

  The detonation shock wave passes through the entire charge located in the detonation chamber and reaches the fresh charge already located in the temporary chamber of the expander through the open discharge port. Due to the expansion action of the detonation process, the charge remaining in the detonation chamber is expelled from the detonation chamber to the temporary chamber of the expander, resulting in a lean wave immediately behind the shock wave. Here, the expansion action of the detonation process has an immediate effect in driving the expander rotor pair to further rotation.

  After 20 degrees, the discharge port closes and the charge, now all trapped effectively in the expander's temporary chamber, expands and releases its pressure energy, which translates into a torque effect on the expander rotor Is done. Expansion occurs until the tip of the rotor with the convex part of the expander and the leading edge of the rotor with the concave part of the expander pass the outer edge of the confinement wall of the expander and the charge is released from the temporary chamber of the expander. Continue. At this point, the charge reaches approximately atmospheric pressure and all of the pressure energy generated by the detonation is converted into shaft work.

  Immediately after closing the detonation chamber exhaust port, the fill port begins to open, allowing fresh charge to enter for the next cycle in which compression has already begun. The state of the detonation chamber at this point is a substantially low pressure below atmospheric pressure because of the lean waves established by the detonation process. This means that the work done by the compressor rotor in delivering fresh charge is canceled out due to the presence of a negative pressure gradient between the temporary and detonation chambers of the compressor. means.

  An additional port (not shown) that has the same axial length but a smaller width than the illustrated port 20 can be placed around the stator cylinder 3. At this stage, these additional ports are aligned with the remaining recess passage 22 of the compressor recessed rotor that is not currently engaged with the protrusion. Thus, these additional ports have a pressure gradient created by lean waves in the detonation chamber 4 and a fresh charge is delivered from the temporary chamber of the newly activated compressor rotor to the detonation chamber 4. In a state before being put, the fresh charge can easily enter the detonation chamber 4 from the space surrounding the compressor rotor. This minimizes the work input required to bring a fresh charge to the engine and is highly efficient with minimal internal losses in operation for the thermal energy released from the fuel contained in the charge A typical engine cycle.

  Due to the presence of relatively low pressure as a result of lean waves, in some cases a compressor is not necessary. In other words, the suction caused by lean waves is sufficient to draw a fresh charge of air / fuel mixture into the detonation chamber.

  FIG. 8 schematically shows a cross section of an example of a rotary device according to a further embodiment of the invention.

  In FIG. 8, the same reference numerals are given to components common to the embodiment of FIGS. The rotary device of FIG. 8 includes an axial port connecting the detonation chamber to the compressor and expander rotor pair, and a radially positioned port on both the compressor and expander. Yes. In configurations with radially arranged ports in addition to or in place of axial ports, the disk with the ports is one of the rotors with each recess in the rotor pair or Attached to both delivery end faces. Each disk is provided with one or more ports, so that each of the disk ports is located at the delivery end of the rotor recess.

  As shown in FIG. 8, the rotary device includes a port 34 disposed on an end surface of the rotor 5 with a concave portion of the compressor. A transfer passage 36 is arranged to provide a path for the gas to pass from the compressor temporary chamber to the detonation chamber 4. Turning to the expander, a port 38 is provided at the end face of the expander rotor with a recess through which the expander temporary chamber can receive gas from the detonation chamber 4. A transfer passage 40 is provided to provide a path through the port 38 from the detonation chamber 4 to the temporary chamber of the expander to the gas. Therefore, in use, in addition to the flow of the working gas through the ports 20 and 32 provided in the stator cylinder 3, the end surfaces of the rotor 7 with the concave portion of the compressor and the rotor 18 with the concave portion of the expander are used. Gas transfer to and from the detonation chamber is possible via transfer passages 36 and 40 between them.

  The passage 36 connecting the port 34 to the detonation chamber 4 is provided with turbulence generating means, such as a grid, in a form similar to that described above with respect to FIG. The grid is related to the charge gas just prior to entering the detonation chamber, as described above in the axial port arrangement. Each compressor and expander recessed rotor disk port is in communication with a corresponding end wall port of the rotor housing that supports the compressor and expander rotor pair. As the rotor rotates, the sliding engagement between the end wall of the housing and the disk located on the rotor provides control over the timing of opening and closing the disk ports. Preferably, it is convenient to manufacture the disc as a separate part and then place it on the end face of each rotor.

  In the configuration shown in FIG. 8, in addition to the ports provided in the stator housing 3, ports are also provided on appropriate end surfaces of the rotary device. Thereby, a larger charge gas flow can be achieved in the rotary device. It will be appreciated that only axial ports or only radial ports may be provided. In one embodiment, one of the expander and compressor is provided with an axial port and the other is provided with a radial port.

  Embodiments of the present invention have been described with particular reference to several examples shown. However, it will be understood that variations and modifications can be made to the above examples within the scope of the invention.

Fig. 2 schematically shows a perspective view of an example of a rotary device according to an embodiment of the invention. FIG. 2 is a diagram of the apparatus of FIG. 1 with some parts removed for clarity. FIG. 2 is a diagram of the apparatus of FIG. 1 with some parts removed for clarity. For the compressor, the shape of the end of the rotor at each stage of the cycle is shown. For the compressor, the shape of the end of the rotor at each stage of the cycle is shown. For the compressor, the shape of the end of the rotor at each stage of the cycle is shown. For the compressor, the shape of the end of the rotor at each stage of the cycle is shown. For the compressor, the shape of the end of the rotor at each stage of the cycle is shown. For the compressor, the shape of the end of the rotor at each stage of the cycle is shown. For the compressor, the shape of the end of the rotor at each stage of the cycle is shown. For the compressor, the shape of the end of the rotor at each stage of the cycle is shown. For the expander, the shape of the end of the rotor at each stage of the cycle is shown. For the expander, the shape of the end of the rotor at each stage of the cycle is shown. For the expander, the shape of the end of the rotor at each stage of the cycle is shown. For the expander, the shape of the end of the rotor at each stage of the cycle is shown. For the expander, the shape of the end of the rotor at each stage of the cycle is shown. For the expander, the shape of the end of the rotor at each stage of the cycle is shown. For the expander, the shape of the end of the rotor at each stage of the cycle is shown. For the expander, the shape of the end of the rotor at each stage of the cycle is shown. FIG. 2 shows a section through a port with a lattice filter used in the rotary device of FIG. FIG. 2 is a graph showing each stage of a detonation cycle for the rotary device of FIG. 1 schematically shows a longitudinal sectional view of an example of a rotary device according to an embodiment of the invention.

Claims (24)

A rotary expander having a chamber for receiving a charge comprising an air / fuel mixture and oxidizing fuel by detonation, and a temporary chamber of varying volume, wherein the temporary chamber is configured to rotate the rotary expander. A rotary expander in fluid communication with the detonation chamber for at least a portion of a cycle;
A rotary device, wherein the rotary expander is configured to be driven by expansion of an air / fuel mixture caused by air / fuel mixture detonation. The rotary device of claim 1, comprising a compressor configured to receive an air / fuel mixture, compress the mixture, and provide the compressed mixture to a detonation chamber. The expander has a first rotor that has a recess and can rotate around a first axis, and a second rotor that has at least one projection and can rotate around a second axis And
When the first and second rotors rotate about the respective axes, the convex part of the rotor with the convex part is the concave part of the rotor with the concave part. The rotary device according to claim 1 or 2, wherein the rotary device is configured so as to enter a temporary chamber in which a volume changes between the two. The compressor has a first rotor that has a recess and can rotate around a first axis, and a second rotor that has at least one projection and can rotate around a second axis And
When the first and second rotors rotate about the respective axes, the convex part of the rotor with the convex part is the concave part of the rotor with the concave part. The rotary device according to claim 2 or 3, wherein the rotary device is configured so as to enter a temporary chamber with a volume changing between the two. The detonation chamber has an inlet port configured to receive a charge comprising an air / fuel mixture through the inlet port;
To ensure that the charge is agitated to ensure that the charge is turbulent in the detonation chamber when the charge comprising the air / fuel mixture passes through the port to the detonation chamber, The rotary apparatus in any one of Claims 1-4 with which the stirring apparatus is arrange | positioned.   The rotary device according to claim 5, wherein the stirring device has a lattice.   5. The rotary device according to claim 3, wherein the detonation chamber is disposed inside the stator cylinder, and the rotor with the recess is configured to rotate about the stator cylinder.   A rotor with a recess has a disk attached to its end face, which disk delivers a charge consisting of an air / fuel mixture from the recess of the rotor with a compressor recess to the detonation chamber. The rotary device according to claim 4, further comprising a enabling port.   A rotor with a recess in the expander has a disk attached to its end face, and the disk has a charge consisting of an air / fuel mixture from the detonation chamber to the recess in the rotor with a recess in the expander. The rotary device according to claim 3, wherein the rotary device has a port that enables the transfer of the device.   The rotary device according to any one of claims 1 to 9, wherein the rotary expander is a positive displacement device.   The charge can be transferred to the expander temporary chamber when the detonation chamber receives the charge or shortly thereafter so that the charge occupies at least a portion of each of the expander temporary chamber and the detonation chamber during detonation. The rotary device according to any one of claims 1 to 10, which is configured as follows. A containment wall that engages the first and second rotors of one or both of the compressor and expander, wherein a temporary chamber is defined between the containment wall and the first and second rotors Has a containment wall,
The rotary device according to any one of claims 5 to 7, wherein the confining wall is movable so that the maximum possible volume of the temporary chamber of the compressor and / or expander can be varied.   The rotary device according to any one of claims 1 to 12, further comprising a detonation generator for driving a rotary expander by generating detonation in a charge composed of an air / fuel mixture. A method of operating a rotary device having a detonation chamber in fluid communication with a variable volume temporary chamber of a rotary expander comprising:
Receiving a charge comprising a gas / fuel mixture in a detonation chamber; and causing the mixture to detonate to expand the gas / fuel mixture and drive a rotary expander. 15. The method of claim 14, comprising supplying the charge to the detonation chamber by pushing the charge into the detonation chamber through a port having a grid arranged across it. 16. The method of claim 15, comprising supplying a charge comprising a gas / fuel mixture from the compressor to the detonation chamber. The method of claim 16, comprising receiving a charge to a compressor, compressing the charge, and then sending the charge to a detonation chamber. When the charge is received into the detonation chamber, it allows the charge to enter the expander's temporary chamber and when the charge occupies at least a portion of both the detonation chamber and the temporary chamber. The method according to claim 14, further comprising a step of initiating detonation. The compressor has a variable volume temporary chamber for receiving and compressing a charge comprising a gas / fuel mixture;
The method is
18. A method according to claim 16 or 17, comprising the step of varying the maximum possible volume of the variable volume temporary chamber of the compressor depending on the rotary device and the work load requirements of the rotary device. 20. The method of claim 19, comprising varying the maximum possible volume of the expander temporary chamber in response to the maximum possible volume of the compressor temporary chamber. 15. A method according to claim 14, comprising the step of changing the maximum possible volume of the temporary chamber of the expander depending on the requirements of the rotary device.   The maximum possible volume of the temporary chamber of the compressor and / or expander is varied by moving a suitably shaped containment wall that functions to define at least a portion of the surface of the temporary chamber or each temporary chamber. 22. The method according to claim 20 or 21, wherein:   A rotary device substantially as shown in any of Figures 1-8 of the accompanying drawings and / or described with respect to any of Figures 1-8 of the accompanying drawings.   A method of operating a rotary device substantially as described with respect to any of Figures 1-8 of the accompanying drawings.