CYCLE ROTOR MECHANISM

专利摘要:
cycloid rotor mechanism. The present invention relates to a rotating mechanism having a cycloid rotor and a sealing net that includes a face seal that rotates with the rotor and that includes other seals that do not rotate with the rotor. as the rotor rotates within a housing, the rotor, housing and sealing net form from at least one working chamber therebetween, the chamber which undergoes a change from the initial volume v1 to v2, which is smaller than v1, thus compressing a working medium and subsequently expanding to volume v3, which can be larger than v1, such that the chamber volume is a smooth and continuous function of the rotor's rotation angle.
公开号:BR112013024765B1
申请号:R112013024765-7
申请日:2012-03-29
公开日:2021-06-22
发明作者:Nikolay Shkolnik；Alexander C. Shkolnik
申请人:Liquidpiston, Inc；
IPC主号:

专利说明:

Priority
[001] This patent application claims priority from United States Provisional Patent Application No. 61/469,009, filed March 29, 2011, entitled "Cycloid Rotor Engine" in the name of Nikolay Shkolnik and Alexander C. Shkolnik as the inventors, the description of which is incorporated herein by reference in its entirety. Technical Field
[002] The present invention relates to mechanisms, and, more particularly, to rotating mechanisms. Background of the Technique
[003] Rotating mechanisms hold the promise of high efficiency, high energy densities and low part count, which has attracted numerous engineers and efforts into this field. Among many configurations existing in the prior art, one of the simplest and most promising is based on the concept of gerotor. Referring to Figures 1(a) - 1(d), depicting the prior art, and more specifically to Figures 1(a), a gerotor includes an external rotor pivotally mounted within the housing cavity (non-housing shown) and which has the female gear profile and inner rotor with the male gear profile. In a course of its operation, both the outer and inner rotors rotate within the housing, forming a plurality of successive chambers of variable volume. These chambers can be used to perform gas compression or expansion in compressors/air motors/mechanisms or movement of liquids in pumps/hydraulic motors. An alternative configuration is for an outer rotor to be stationary while the inner rotor oscillates, driven by an eccentric shaft. The variable volume chambers thus formed behave similarly to the first configuration. The friction losses associated with these designs could be reduced by using the helix-roller gerotor design shown in Fig. 1(b). Instead of direct contact between the outer and inner rotors, rollers are incorporated to form the displacement chambers. In all of these designs, an outer rotor is used not only to form the chambers, but also to guide the inner rotor.
[004] Because it has very few moving parts, it is not surprising that this simple design has attracted the attention of many who have tried to design a rotary engine around it. The main problem that can be attributed to all rotary engines, however, is the difficulty in sealing the working fluid during the compression, combustion and expansion courses of the mechanisms. In theory, although most motors seem possible on paper as they completely cover the working fluid without the use of seals, in practice when machining tolerances and thermal expansion are considered and also when parts start to if it wears out, sealing the working fluid is not possible without the seals. The most famous version of the gerotor-based mechanism and the only one used in production is the Wankel mechanism, in which the 3-lobe rotor moves within the 2-lobe housing as shown in Fig. 1(c). This mechanism was relatively successful for two main reasons. First, the outer rotor was not used to guide the inner rotor, but rather a pair of gears was used to synchronize the movement and rotation of the inner rotor with the movement of the eccentric shaft. Second, the gap between the inner rotor and outer rotor, which is provided to allow for manufacturing tolerances, thermal expansion and wear, has been sealed by a sealing net work, may be known as a "Wankel Net", consisting of front seals located on the flat part of the rotor seal and the apex located at each rotor vertex, and also "buttons" connecting both of these types of seals; all these seals are located on the rotor and therefore will move with the rotor Along with the rotor itself and the housing, in theory these seals are completely covered with the working fluid. Again, in practice, there are still gaps between the seals or seals and the rotor and the seals and housing, but these are relatively small and manageable and allow the mechanism to function. That said, it is well known that these engines have relatively low efficiency and high emissions and are not suitable for the compression-ignition mode of operation due to: 1. Relatively high degree of leakage despite the sealing net. For example, the bounce of fast-moving apex seals as well as holes in the mechanism to accommodate the spark plug(s) contribute to leakage. 2. Large sealing movement. 3. High thermal losses caused by the very high surface to volume ratio of the combustion chamber at the moment of greatest compression. 4. Geometrically achievable low compression ratio. 5. Need to measure the oil in the working chamber to lubricate the apex seals, which cannot be lubricated by any other means, as well as the existence of ports through which this oil escapes, causing emission problems.
[005] Theoretically, gerotor mechanisms with a stationary external rotor have only one main moving part, the rotor. This rotor, which moves within a housing, forms variable geometry cavities that contract and expand in a path of rotation of the rotor. Sealing is achieved by contacting the theoretical line between rotor and housing; such contact must occur in at least two locations. In general, gerotors are designed to have very little sliding contact between the rotor and the housing, however, attempts have been made to implement "no slip roller", see US Patent 7,520,738 to Katz, as an example of a such effort. Another example is described in U.S. Patent 5,373,819 to Rene Linder, which uses the rollers in conjunction with an eccentric to guide a rotor into the housing. Yet another example is described in Russian patent RU 2078221 C1 to Veselovsky, which uses seals within a housing. In practice, as noted above, manufacturing tolerances and thermal expansion cause developers to leave a relatively large gap between rotor and housing or rotor and rollers. If the housing and rotor are not flexible, or if the rollers do not accommodate thermal expansion or preload due to machining tolerance, a seal cannot be achieved. Thus, it becomes meaningless to talk only about the roller contact between the rotor and the housing. This gap needs to be sealed in one way or another with the seal to allow for a viable mechanism. Modalities Summary
[006] In a first embodiment of the invention, an improved mechanism of the type is presented that includes a cycloidal rotor that has N lobes and a housing that has a corresponding set of N+1 lobe reception regions for successive reception of the lobes as the rotor rotates about an axis relative to the housing, the housing having (i) a pair of axially disposed sides on the first and second sides of the rotor, and (ii) a peak disposed between each pair of adjacent lobe receiving regions, and (iii) an inlet port and an outlet port, wherein the enhancement is defined by: a plurality of peak seals, at least one of the plurality of peak seals disposed in each peak and configured to maintain contact with the rotor over a period of rotor rotation, each seal which is angled radially against the rotor throughout the rotor rotation, due to the cycloidal geometry of the rotor and the receiving parts of wolf; a first passage defined in the rotor for cyclically communicating between the inlet port and a working chamber, a working chamber defined as a volume lying between two peak seals, the housing and the rotor; a second passage, distinct from the first passage, defined in the rotor to communicate cyclically between the exit port and a working chamber; a first face seal disposed between the first side and the rotor; a second face seal disposed between the second side and the rotor; where passageways and seals are configured to make each seal maintain contact with both the rotor and one side through all angular positions of the rotor, while avoiding communication with either port.
[007] In another embodiment, each peak seal has a contact region with the rotor, and the contact region is curved with a radius of curvature equal to the radius of curvature of a theoretical roller, whose theoretical roller is uniquely defined by the rotor geometry and the geometry of the lobe reception regions.
[008] In another embodiment, the rotor has a first axial face, a second axial face parallel to the first axial face, and a radial surface between the first axial face and the second axial face, and normal to the first axial face and the second face axial face, and wherein the first axial face and radial face define a first rotor edge and the second axial face and radial face define a second rotor edge, and wherein the first face seal is disposed on the first rotor edge .
[009] In an additional embodiment, the second face seal is arranged on the second edge of the rotor.
[0010] In another embodiment, the rotor has a first axial face, a second axial face parallel to the first axial face, and a radial surface between and normal to the first axial face and the second axial face, and in which the first axial face and the radial face define a first edge of the rotor, and wherein the first face seal is disposed on the first axial face offset from the first edge of the rotor, so as to define a first annular rest on the first axial face between the first edge and the first face seal, the mechanism further comprising and a button seal arranged to be in contact with the rotor and the first face seal on the first annular rest.
[0011] In another embodiment, at a first angle of the rotor within the housing a working chamber forms a compression chamber having a maximum compression chamber volume, and at a second angle of the rotor within the housing a working chamber forms an expansion chamber that has a maximum expansion chamber volume, the maximum expansion chamber volume that is greater than or equal to 1.0 times the maximum compression chamber volume.
[0012] In another embodiment, the maximum expansion chamber volume is at least 3 times the maximum compression chamber volume.
[0013] Another embodiment further includes a plurality of lubrication channels on at least one side, each of the plurality of lubrication channels arranged so as to release lubricant to those corresponding to the plurality of peak seals.
[0014] Another mode further includes a lubrication channel on at least one side, the lubrication channel arranged to continuously release the lubricant to those corresponding to the face seals.
[0015] In another embodiment, an improved mechanism of the type is presented that includes a rotor that has N lobes and a housing that has a corresponding set of N+1 lobe reception regions for successively receiving the lobes to measure that the rotor rotates about its axis and rotates about an axis relative to the housing, the housing having (i) a pair of axially disposed sides on the first and second sides of the rotor, and (ii) a peak disposed between each pair of adjacent lobe receive regions, and (iii) an inlet port and an outlet port, wherein the enhancement includes: a first passage defined in the rotor to cyclically communicate between the inlet port and a working chamber defined as a volume that lies between two peak seals, the housing and the rotor; a second passage, distinct from the first passage, defined in the rotor to communicate cyclically between the exit port and a working chamber; a sealing network comprising a plurality of peak seals, at least one of the plurality of peak seals disposed at each peak and configured to maintain contact with the rotor, which seal is inclined radially against the rotor; and one of: a face seal disposed on the rotor and configured to maintain contact with the sides of the housing such seal that is axially inclined against the housing side, where by the course of rotation of said side seal it does not cross the port inlet and outlet, and 2 x button seals (N + 1), one to each side of each peak, arranged inside the housing side, angled axially towards the rotor and configured to maintain contact with the peak seal and side seal, and a face seal disposed on the rotor and configured to maintain contact with the sides of the housing and a chamfered portion of the rotor, which seal is inclined axially against the housing side; wherein the doors, passages and face seal are configured to make said seal maintain contact with both the rotor and one side through all angular positions of the rotor while preventing said seal from cross any of the doors.
[0016] In another embodiment, the face seal is a wire seal.
[0017] In another embodiment, the face seal is disposed on an edge of the rotor, whose edge is defined by the intersection of an axial face of the rotor with a radial face of the rotor.
[0018] In another embodiment, the face seal profile is generated as a cycloidal curve in which the theoretical roller radius used to generate the cycloidal curve is the radius of the button on the button seal.
[0019] In another embodiment, the rotor is of a cycloidal geometry defined by a set of N+1 theoretical rollers, and each peak seal has a contact region with the rotor, and the contact region is curved with a radius of curvature that approximates a radius of curvature of the theoretical roller that the peak seal replaces.
[0020] Another embodiment includes a housing having a working cavity, and a combustion chamber in fluid communication with the working cavity; a piston disposed over the housing and configured to controllably enter and withdraw from the combustion chamber; a rotor rotatably mounted within the working cavity so as to form a working chamber of variable volume with the housing at different angles of rotation of the rotor within the working cavity; and a controller synchronized to the angle of rotation of the rotor to cause the piston to controllably enter and withdraw from the combustion chamber so as to make the combined volume of a working chamber and combustion chamber constant. by a range of rotor rotation angles.
[0021] Another embodiment includes a housing that has a work cavity; an axis, the axis having an eccentric part; a rotor having a first axial face, and a second axial face opposite the first axial face, the rotor disposed on the eccentric part and within the working cavity, the rotor comprising a first cam on the first axial face, the first cam which has an eccentricity that corresponds to the eccentricity of the eccentric part of the shaft; and a cover integral with, or fixedly attached to the housing, the cover comprising a plurality of rollers, each roller engaged with the cam, the cam guiding rotation of the rotor as the rotor rotates within the working cavity and rotates around the axis.
[0022] Another embodiment includes a second cam on the second axial face of the rotor. Brief Description of Drawings
[0023] The aforementioned characteristics of the modalities will be more readily understood by reference to the following detailed description, considered with reference to the attached drawings, in which:
[0024] Figures 1(a) to 1(d) schematically illustrate the rotary mechanisms of the prior art with the use of gerotors;
[0025] Fig. 2(a) to 2(b) schematically illustrates one embodiment of an embodiment of a cycloid rotor mechanism;
[0026] Fig. 3 schematically illustrates an embodiment of a cycloid rotor mechanism at various points in execution of a mechanism cycle;
[0027] Figures 4(a) to 4(d) schematically illustrate the geometries of the forming components of a cycloidal mechanism;
[0028] Fig. 5 schematically illustrates various components of an embodiment of a cycloid rotor mechanism;
[0029] Fig. 6 schematically illustrates a rotor assembly of one embodiment of a cycloid rotor;
[0030] Figures 7(a) to 7(d) schematically illustrate the interaction between the arrangements of mechanism housings and the entry and exit passages in a rotor;
[0031] Figures 8(a) to 8(b) schematically illustrate the embodiments of a sealing net, along an embodiment of a piston in the combustion chamber;
[0032] Fig. 9 schematically illustrates the position of a face seal with respect to inlet ports at a variety of rotor angles;
[0033] Figures 10(a) and 10(b) schematically illustrate the modalities of a face seal;
[0034] Figures 11(a) to 11(c) schematically illustrate the modalities of a face seal;
[0035] Figures 12(a) to 12(g) schematically illustrate the modalities of components of a sealing net;
[0036] Figures 13(a) to 13(g) schematically illustrate the modalities of a face seal;
[0037] Fig. 14 schematically illustrates an embodiment of a face seal;
[0038] Figures 15(a) to 15(c) schematically illustrate the modalities of components of a sealing net;
[0039] Figures 16(a) to 16(d) schematically illustrate the modalities of components of a sealing net;
[0040] Fig. 17 schematically illustrates an embodiment of a peak seal;
[0041] Fig. 18 schematically illustrates an embodiment of a peak seal;
[0042] Fig. 19(a) to 19(b) schematically illustrates one embodiment of a peak seal;
[0043] Fig. 20(a) to 20(c) schematically illustrate the modalities of a peak seal;
[0044] Fig. 21 schematically illustrates one embodiment of a housing of gerotor mechanism and rotor;
[0045] Figures 22(a) to 22(c) schematically illustrate one embodiment of a gerotor mechanism;
[0046] Fig. 23 schematically illustrates an embodiment of a rotor of a rotating mechanism;
[0047] Fig. 24 schematically illustrates an embodiment of a rotor of a rotating mechanism;
[0048] Fig. 25 schematically illustrates an embodiment of a rotor of a rotating mechanism;
[0049] Fig. 26 schematically illustrates an embodiment of a rotor of a rotating mechanism;
[0050] Fig. 27 schematically illustrates an embodiment of a rotor of a rotating mechanism;
[0051] Fig. 28 schematically illustrates an embodiment of a rotor of a rotating mechanism;
[0052] Fig. 29(a) to 29(b) schematically illustrate the embodiments of a rotor of a rotating mechanism;
[0053] Figures 30(a) to 30(c) schematically illustrate one embodiment of a swivel mechanism;
[0054] Fig. 31 schematically illustrates an embodiment of a rotor of a rotating mechanism;
[0055] Figures 32(a) to 32(f) schematically illustrate the rotor positions during the execution of a mechanism cycle. Detailed Description of Specific Modalities
[0056] Various modalities provide improved swivel mechanisms that operate more efficiently, with lower exhaust emissions than traditional piston or swivel mechanisms. These features will allow for better fuel efficiency, and also make the mechanisms more environmentally friendly than traditional swivel mechanisms, such as the Wankel swivel mechanism, for example, as used for decades by the Mazda corporation.
[0057] Unlike previous internal combustion mechanisms, illustrative embodiments use a cycloid (or cycloidal) rotor that rotates within a fixed housing.
[0058] As used in this description and the accompanying claims, the following terms shall have the meanings indicated, unless the context imposes a different interpretation:
[0059] Cycloid: the term "cycloidal" refers to the geometry of a rotor in some of the embodiments of a rotating mechanism. The rotor (which can be described as a "cycloid disk") has Z1 number of lobes. The rotor geometry is generated based on Z2 theoretical rollers, where Z2 = Z1+1, and the theoretical rollers have radius Rr and are located at a distance R away from a center point.
[0060] The rotor profile (cycloid disk) can be generated mathematically using the equations derived by Shin and Kwon (see Shin, JH, and Kwon, SM, 2006, " Lobe Profile Design in a Cycloid Reducer Using Instant Velocity Center ", Theory of Mech. Mach., 41, pp. 596 to 616):

[0061] A rotary mechanism or even a rotary compressor can be built using this geometry for any Z1 from 1 to infinity. For example, the various modalities described below have rotors in which Z1=2 and Z2=3, an understanding that any Z1 can be used, as well as that the application is not limited to mechanisms, but is also applicable to compressors, pumps and hydraulic or pneumatic motors.
[0062] The maximum volume of a compression chamber, the maximum volume of the compression chamber is the volume of the compression chamber (which is a working chamber, at that stage of a mechanism cycle when the working medium inside the chamber (working is fresh, eg air, and is being compressed before combustion) at the time of the engine cycle when the chamber is first cut from the external environment of the engine. For example, in mechanism 200, the maximum volume of the compression chamber is the volume of that chamber just after the inlet passage has been omitted, so that there is no longer a fluid passage from the compression chamber to the outside environment. mechanism housing.
[0063] The maximum volume of the expansion chamber: the maximum volume of an expansion chamber is the volume of an expansion chamber (which is a working chamber at that stage of a cycle of the mechanism when the working medium inside a work chamber has been burned and is doing work on the rotor) at the last moment in the mechanism cycle before the chamber is exposed to the environment outside the mechanism. For example, in mechanism 200, the maximum volume of the expansion chamber is the volume of that chamber just after the exhaust passage ceases to be omitted, so that there remains, at the last moment, no fluid passage from the exhaust chamber to the environment outside the engine housing.
[0064] The angle, or angle of rotation. A mechanism rotor is configured so that it can rotate and orbit within the motor. In some embodiments, a rotor rotates around the motor shaft, defined by its input/output axis, driven by the eccentric shaft and with the angular velocity of the shaft, while at the same time the rotor rotates around its own axis, at some angular velocity of the axis and in the opposite direction through synchronization, defined below. In various positions, the rotor forms several working chambers, and engages the intake and exhaust ports, etc. References to the angle of a rotor, or the angle of rotation of a rotor, are references to the position of the rotor within the housing. For example, in Fig. 3(f), if the rotor position is assumed to be 0 degrees, then the rotor position in Fig.3(c) would be offset 60 degrees counterclockwise.
[0065] The working medium: the term "working medium" refers to a gas within a mechanism, and may include, for example, air that passes into a suction chamber, air that is compressed within a compression chamber, the gas within a combustion chamber and the gas within an expansion chamber. The working medium may contain fuel (eg gasoline or diesel fuel), or may include combustion by-products.
[0066] Eccentricity: the distance between a center of rotation of an axis, and the geometric center of a circular eccentric fixed to the axis. Overview of Illustrative Mechanism Modality
[0067] Fig. 2(a) schematically illustrates an embodiment of a cycloid swivel mechanism 200, Fig. 2(b) schematically illustrates the cycloid swivel mechanism 200 in an exploded view, and Fig. 2(c) ) schematically illustrates the cycloid swivel mechanism 200 in a sectional view. Mechanism 200 includes a housing 201 that has a body 201A (which may be known as a "circumferential body") that has an opening 201B, an inlet cover 201C, and an exhaust cover 201D. In some embodiments, the inlet cap 201C and/or the exhaust cap 201D are an integral part of the body 201A, and form a flat surface displaced axially from and facing the rotor 202. Thus, the inlet cap 201C and/or the exhaust cover 201D can simply be called a flat part of the housing 201. The body 201A, the intake cover 201C and the exhaust cover 201D have a fixed spatial relationship to each other, and together they define a cavity for the cycloid rotor housing 202.
[0068] In addition to housing 201, Figures 2(a) and 2(b) include numerous other elements of mechanism 200. An optional fan 203 provides airflow to mechanism 200 to cool, and/or may provide a load of fresh air for use in cycling the engine. If a fan is not used, a charge of fresh air will be provided by the induction action of the rotor which, in a course of its rotation, creates a vacuum during certain parts of the cycle. An optional oil pump 204 supplies oil to the internal components of the mechanism as further described below. Engine 200 also includes intake and exhaust lines 205 and 206, along with fuel pump 207 and fuel injectors 208 to supply fuel for combustion in engine 200.
[0069] Within the mechanism 200, the rotor is pivotally coupled to an eccentric shaft 201, best seen in Fig. 6, which can simply be called a "shaft". Eccentric shaft 210 is configured to rotate about center point (or axis) 210A of shaft 210, and includes an eccentric portion 210B, which is offset relative to the shaft by eccentricity "e". A force applied to the eccentric portion of shaft 210 will act on shaft 210, causing shaft 210 to rotate.
[0070] In this embodiment, the rotor 202 has two lobes 202A, 202B, and the aperture 201B has three lobe receiving regions 250, 252 and 253, as shown schematically in Figure 3.
[0071] Lobes 202A, 202B are curved and have a curvature. Lobe receiving regions 220, 221 and 222 are defined by an equal number of intersection curves, which form an equal number of peaks 205, 206, 207, one peak at each intersection. The curves 208, 209 and 201 defining the lobe receiving regions have a curvature of a similar shape to the curvature of the lobes, so that the inner curve of the lobe receiving regions 220, 221 and 222 are equal to the outer curves of a lobe 202A, 202B, with the exception that a small clearance must exist between the two curves to accommodate manufacturing tolerances and for the thermal expansion components so that either lobe can completely occupy any of the receiving regions of wolf, as explained more fully below.
[0072] Each peak 205, 206, 207, in turn, has a peak seal 251A, 251B, 251C, and each peak seal is inclined radially so as to be in continuous seal contact with the rotor 202, to form numerous working chambers, as described more fully below.
[0073] Figures 3(a) to 3(f) schematically illustrate the mechanism 200 at various times of its operation, during which the geometric center of the rotor 202 rotates around the center 210A of the shaft 210 and the rotor 202 it rotates around its center at half the angular velocity, and in the opposite direction of the shaft 210. The synchronizing mechanism, in this case an inner gear 211 fixed on the cover and the pinion 212 fixed on the rotor in a 3:2 ratio makes the shaft 210 rotates in a direction opposite to the direction of rotation of rotor 202. For example, in Figures 3(a) through 3(f), rotor 202 rotates counterclockwise, and shaft 210 rotates clockwise.
[0074] As the rotor 202 rotates within the opening 201B, the housing 201 and the rotor 202 cooperate to form three working chambers 250, 252, 253 for cycling the mechanism. More specifically, each working chamber is defined by the circumferential housing 201A, the rotor 202, numerous seals and the sides 201C, 201D of the housing.
[0075] For example, a working chamber 250 is formed by rotor 202, circumferential housing 201A and seals 251A and 251B, along with sides 201C and 201D, and other seals between a rotor and sides. For ease of illustration, the other seals are not shown in Figures 3(a) to 3(f).
[0076] As illustrated in figure 3(a), a working chamber 250 has a finite volume and is not coupled to the external environment for the mechanism 200. As the rotor 202 rotates counterclockwise, a gas or medium work (eg, air that was induced into a work chamber 250 before that time) is compressed from its initial volume (V1). As the rotor 202 continues to rotate, a lobe 202A of the rotor 202 continues to progressively occupy more of the lobe 221 receiving region, thereby progressively compressing the gas within a working chamber 250. Thus, the chamber 250, at this stage of the mechanism cycle, can be referred to as a "compression chamber."
[0077] Finally, lobe 202A completely occupies lobe receiving region 221, as illustrated schematically in Figure 3(c). In this position, lobe 202A forced all the gas into the compression chamber into a combustion chamber 260 within circumferential body 201A. Combustion chamber 260 has a fixed volume (V2).
[0078] This position of rotor 202 within lobe receiving region 221 may be known as "top dead center" or "TDC". At this point in the engine cycle, the fuel inside the combustion chamber ignites, causing heat to be added to the gas, thereby greatly increasing the pressure of the gas.
[0079] Ignition can be initiated in a variety of ways known in the art. However, in this embodiment, the ratio of the initial volume of the compression chamber (V1) and the volume of the combustion chamber (V2) at top dead center may be greater than 30 or more. As such, the fuel and gas mixture inside the working chamber can be ignited by compression ignition. In fact, fuel can be injected into the working chamber before the combustion chamber closes (eg during compression), or during or after the moment when the combustion chamber is closed.
[0080] As rotor 202 continues to rotate, lobe 202A is substantially stationary for a brief period of time (or for a small angle of rotation) within lobe receiving region 221. In other words, as long as the lobe 202A is at top dead center, rotation of shaft 210 causes lobe 202A to rotate effectively within lobe receiving region 221 before finally beginning to withdraw from lobe receiving region 221 (Fig. 3(d)). Thus, the volume of a working chamber (i.e., the combustion chamber) in and around the top dead center is substantially constant for a portion of the angular rotation of the rotor 202. work captured in the combustion chamber above about 5 to 10 degrees of rotation, due to the aerodynamic properties of the gas moving through a very small gap between the rotor and the housing is less than one-half of a percent (0.5 %) of the volume of the combustion chamber can be considered an effectively constant volume or a substantially constant volume.
[0081] Some embodiments have a substantially constant volume for a longer period of time (or greater angle of rotation of a rotor) than could be provided by the rotating rotor. For example, as illustrated schematically in Fig. 8(a), some embodiments include a piston 850 that controllably extends into combustion chamber 820. For example, in some embodiments, piston 850 may extend into combustion chamber. combustion 820. As the rotor 821 reduces the volume of the compression chamber, the working medium within the compression chamber is forced into the combustion chamber 820. At a predetermined time in the mechanism cycle, the piston 850 begins to withdraw of the combustion chamber 850 in order to provide the additional volume within the combustion chamber 850 to exactly match the reduction in compression chamber volume. Similarly, as rotor 821 rotates past combustion chamber 852, piston 850 can begin to progressively occupy more of combustion chamber 850. In this way, the combined volume of compression chamber and combustion chamber 820 can be held constant for a given range of rotor motion.
[0082] In various modes, the small piston 850 can be spring loaded, or externally actuated by a cam, or electrical or hydraulic actuations synchronized with the mechanism cycle. Any such drive mechanism can be known as a "controller". If externally actuated, piston 850 extends to combustion chamber 820 and can be controlled to maintain a constant volume of combustion chamber 820 for a much longer duration. Alternatively, the piston 850 can aid in very fast compression or variable compression ratio mechanisms, all of which are useful in different engine operating modes, for the purpose of increasing engine efficiency, or allowing the engine to run smoothly. a multitude of fuels. Alternatively, the volume (and composition) of gases during the combustion phase could be controlled by water injection.
[0083] Again, referring to Figures 3(a) to 3(f), after combustion, the gas within a working chamber 250 begins to expand, thus forcing the rotor 202 to recur from the lobe receiving region 221 , as shown schematically in figure 3(d). During this phase of the mechanism cycle, a working chamber 250 may be known as an "expansion chamber". At this moment of maximum expansion, the expansion chamber has a volume (V3) that is greater than the maximum volume (V1) of the compression chamber. In some modalities, the maximum volume of the expansion chamber (V3) can be equal to the maximum volume of the expansion chamber and, in other modalities, the volume of the expansion chamber (V3) can be greater than the maximum volume (V1) of the compression chamber. In some modalities, the volume of the expansion chamber (V3) can be 1.1 to 3 times larger than the maximum volume (V1) of the compression chamber. For example, Figures 32(a) to 32(f) schematically illustrate an embodiment in which the inlet and exhaust ports have been configured such that volume V3 is greater than volume V1. In some embodiments, the configuration of the inlet and exhaust passages can be described as "asymmetric", meaning that the inlet passage engages a working chamber at a different angle of rotation of the rotor, and/or by a band lesser of rotor rotation angles than the angle (or range of angles) at which the exhaust passage engages a working chamber.
[0084] The expansion gas within the expansion chamber 250 exerts force on the rotor 202, thus causing the rotor 202 to continue its rotation around the eccentric shaft 210, and thus causing the eccentric shaft 210 to rotate about its shaft 210A in a direction opposite to the direction of rotation of rotor 202. In this mode, shaft 210 rotates clockwise, as indicated by the arrow on cam 210B.
[0085] As the expansion ends, and the rotor 202 continues to rotate, the exhaust passage (see Figures 7(a) to 7(d)) in the rotor 202 communicates with the working chamber 250. The exhaust port faces the outlet port, thus exposing a working chamber 250 to the external environment of the mechanism 200, so that exhaust gases can exit the mechanism 200. As the rotor 202 continues to rotate, the volume of the working chamber is reduced and exhaust gases are expelled.
[0086] As the rotor 202 continues to rotate, an inlet passage (see Figures 7(a) to 7(d)) in the rotor is exposed to a working chamber, this inlet passage communicates with a port of admission on the accommodation side. In this way, a working chamber 250 is ultimately exposed to the environment outside the mechanism 200, so that fresh air (which may be known as a "fresh" charge) can be induced into a working chamber 250 once that this volume increases with the additional rotation of the rotor. When a working chamber is exposed to the external environment of the mechanism 200, the volume of a working chamber 250 can be characterized as not having a finite volume. Nevertheless, by escaping the exhaust gases, chamber 250 may be known as an "exhaust chamber" and, while inducing a fresh charge, chamber 250 may be known as an "aspiration".
[0087] Although the above discussion focuses on the working chamber 250, Figures 3(a) to 3(f) also reveal that the mechanism 200 also forms two other working chambers 252 and 253. Each working chamber performs a cycle that includes inlet, compression, combustion, expansion and exhaust, as described above in conjunction with chamber 250. In this mode, the phases of the mechanism cycle for each of the working chambers are 120 degrees out of phase with each other. the others from the working cameras. At a certain point in the cycle, the chamber in the expansion phase not only transforms the eccentric shaft, but also feeds the execution phases into the other two working chambers.
[0088] Numerous remarks about the 200 mechanism and its operation may be helpful at this point. First, the rotor 202 is in contact with all three of the peak seals 251A, 251B, 251C at all angles of rotation of the rotor 202. In fact, this is a feature of the cycloid rotor that has the beneficial consequences, such as as described more fully below.
[0089] Furthermore, although the present embodiment has a rotor with two lobes 202A, 202B and a stationary aperture 201B with three lobe receiving regions 220, 221, 222, other embodiments may have different numbers of lobes and receiving regions of lobe, with the number of lobe receiving regions being one more (N+1) than the number of lobes (N) in the corresponding rotor. Also, in other modes, both the "housing" (N+1)-lobe and the N-lobe rotor rotate around another fixed housing, or the N-lobe rotor can be stationary and the "housing" (N+1)-with lobe rotates around rotor. Accommodation
[0090] More detailed views of the housing and rotor arrangements are provided in Fig. 5 and Fig. 6. Fig. 5 schematically illustrates an exploded view of the housing 201 and the rotor 202, showing the circumferential body 201A between the 201C intake cover and the 201D exhaust cover. Two of the three peaks 205, 206 are visible in Fig. 5, along with two of the three combustion chambers 205 and 215. The third peak 207 and the third combustion chamber 217 are not visible in Fig. 5 as they are blocked by the rotor 202. However, all three peaks 215, 216, 217 are illustrated schematically in the embodiments of Figures 7(a) to 7(c). Fig. 6 is discussed below. Circumferential Body
[0091] Body 201A has three lobe receiving regions that are closely related to rotor 202. For a given rotor coupled to an eccentric with the known eccentricity "e", the opening geometry in a corresponding circumferential body is determined by specifying a set of theoretical rollers 410, 411, 412 arranged over a generation curve 413, as shown in Figures 4(a) to 4(d). The theory rollers 410, 411, 412 each have a cylindrical shape with a radius Rr, and the theory rollers 410, 411, 412 are equidistantly spaced around a circle generating 413 of the radius R. of rotor 401 is determined by radius Rr and radius R, according to the cycloid equations cited above.
[0092] The opening geometry is then determined by positioning the rotor 401 at top dead center of each of the theoretical rollers 410, 411, 412. The opposite end of the rotor 401 then defines the curve 420, 421, 422 of a lobe reception region. As a practical matter, the construction of a practical curve of a lobe reception region should be considered, by avoiding a gap between the rotor and the housing in the regions receiving the rotor that will take into account manufacturing tolerances and thermal expansion of the components. Since this process is repeated for each of the theoretical rollers 420, 421, 422, the geometry of the opening 430 is defined. The locations of the theoretical rollers correspond to the peaks of the circumferential body. It is noted that, in some embodiments, actual rollers 420, 421, 422 can be manufactured having the dimensions of a "theoretical" roller, and such rotors actually exist and are not theoretical.
[0093] Thus, there is a unique relationship between an opening 430, the rotor 401 and the theoretical rollers 410, 411, 412. As a consequence, the geometry is of the rotor and the opening is completely defined by R and Rr. Radius Rr can be useful in determining the geometry of peak seals or peak rotors as discussed below.
[0094] The cycloid geometry provides numerous beneficial features. For example, the cooperating lobe and lobe receiving region geometries yield a very high compression ratio (i.e., the ratio between a maximum and minimum volume of a compression chamber, where the minimum volume of the combustion chamber defines a constant volume of the combustion chamber). In mechanism 200, the compression ratio is on the order of at least 12 to 25, although higher ratios are also possible. This is an improvement on the prior art swivel mechanisms. For example, it is well known that for the Wankel engine, the practical limit is on the order of about 10, which is not sufficient for compression ignition. That's why there are no naturally aspirated Wankel diesel engines.
[0095] Practically, it is desirable to minimize the gap between a rotor and the housing when the rotor is located at its "top dead center", i.e. when geometrically, a working chamber volume is at its smallest. Covers and Rotor
[0096] Inlet cover 201C includes openings forming inlet ports 260 to allow air to enter various working chambers within mechanism 200. For consideration of symmetry, 3 openings are chosen in the three-lobe housing configuration , although a different number can also be chosen.
[0097] In this embodiment, the rotor 202 includes an intake passage 261 between an intake face 202F of the rotor 202 and the radial face 202R of the rotor 202. In other embodiments, the intake passage may pass through the shaft while still in sometimes these two methods could be mixed and matched. For example, some arrangements may have exit ports on a cover or on one side of the housing, as in figure 7(d), and an inlet port through the shaft, as in figure 30(a).
[0098] Inlet passage 261 is intermittently exposed to inlet port 260. By a range of rotation angles within the housing, inlet passage 261 will be exposed to a working chamber, creating a temporary inlet conduit 262 from the external environment of the mechanism 200 to the working chamber. Temporary inlet conduit 262 will exist for a range of angular rotations of rotor 202 within housing 201, provided inlet passage 261 is at least partially exposed to a working chamber. At other angular rotations of rotor 202 within housing 201, the same inlet passage 261 will cylindrically align with each other of the work chambers to create a temporary inlet conduit for each of these other work chambers.
[0099] The exhaust cover 201D includes the openings that form the outlet port 265 to allow spent working medium to exit the various work chambers within the mechanism 200. Similar to the inlet cover, for symmetry consideration, three openings are chosen in the three-lobe housing configuration, although a different number can also be chosen.
[00100] In this embodiment, the rotor 202 includes an exhaust passage 270 between an exhaust face 202G of the rotor 202 and the radial face 202R of the rotor 202. In other embodiments, the exhaust passage passes through the shaft, while in still others , these two methods could be mixed and matched. For example, some arrangements might have inlet ports on a cover or on one side of the housing, as in Fig. 7(c), and an outlet port through the shaft, as in Fig. 30(a).
[00101] In some embodiments, the exhaust port 270 is intermittently exposed to the outlet port 265, while in other embodiments the exhaust port is continuously exposed to the outlet port 265. By a range of angles of rotation within the housing, the exhaust passage 266 will align with one of the work chambers, creating a temporary exhaust conduit from a given work chamber to the external environment of the mechanism 200. The temporary exhaust conduit will exist per a range of angular rotations of the rotor within the housing, provided the exhaust passage is at least partially aligned with the working chamber. At other angular rotations of the rotor within the housing, the same passage will cyclically align with each of the other work chambers to create a temporary exhaust conduit from each of these other work chambers. The exhaust port 270 may optionally contain a check valve to prevent backflow of exhaust to the mechanism during the intake process, while both the exhaust port and the intake port may be exposed to a working chamber. at the same time for a brief overlapping period.
[00102] One or both of the covers 201C and 201D include a bearing (650, Fig. 6) to support the shaft. Bearing 650 could be any of the conventional types, including the periodic (hydrodynamic) type, this can be specifically valuable as it specifically provides a simple configuration as shown in Fig. 30(a). Additionally, in this configuration, the input/output shafts that eccentrically and rotationally hold the rotor shafts are also used as counterbalances. So they can be produced from heavy metals like tungsten or have heavy metal inserts.
[00103] Fig. 6 schematically illustrates an exploded view of rotor 202 and eccentric shaft 210. To accommodate face seals 801, rotor 202 has two grooves 802 (one on each rotor face) in which two seals of face 801 are arranged. These grooves 802 are generated such that a face seal 801 within groove 802 will be in constant contact with button seal 810. Thus, in some embodiments, rest 811 over rotor 821 has a constant width, while at the same time in other embodiments, rest 811 may have a width that varies at different points on rotor 821. In addition, the mechanism has three points (in general, N+1 points for a mechanism with an N-lobe rotor on each side of housing (cover), 201C, 201D near each peak 205, 206, 207 where such a point on housing side 201C or 201D is in continuous contact with face seal 801. The oil supply ports (such as 270 and 271 in Fig. 2(b), for example) on the side of housings 201C, 201D are located over at least one of these points. Thus, the design ensures that the entire face seal 801 will, like rotor 821, ultimately rotate, pass through an oil port. In other words, the 801 face seals each have their own own lubrication channels located on each side of housing 201C, 201D. Furthermore, the face seals 801 and the inlet port 260 and the outlet port 265 are constructed so that the face seal 801 is never exposed to the fixed ports260, 265 - this prevents oil from escaping through the ports. Oil not only works to reduce wear and cool the seals, it helps to prevent leaks.
[00104] The movement of the rotor 202 is defined by the eccentric shaft 210 and a pair of timing gears: a pinion gear 212 fixed to the rotor 202 (the shafts pass through this pinion without contacting it), and a gear of inner ring 211 secures to one of inlet cover 201C. Inner ring gear 211 has a 3:2 mesh with pinion 212.
[00105] Shaft 210 has an eccentric 210B with eccentricity e. Some embodiments include a bearing positioned between the eccentric portion of the shaft 210 and the rotor 202. Other embodiments, as in Fig. 30, for example, omit such a bearing, so it has an shaft 3210 fixed to the rotor 3202 and having the shaft of inlet/outlet that eccentrically supports the rotor in hydrodynamic bearings, these are capable of much higher loads.
[00106] The operation of the inlet ports 260, the outlet ports 265, the inlet port 261 and the exhaust port 270 can be further understood with reference to Fig. 7(a) and Fig. 7(b), which include two views of the circumferential body 201A, along with the inlet cover 201C and the exhaust cover 201D. In Fig. 7(a), the rotor 202 is aligned with one of the inlet ports 260 on the inlet hood 201C, creating an inlet path through which air (a "fresh charge") 710 enters a working chamber of expansion 711. Air passes through inlet port 260 and enters inlet passage 261 in rotor 202. Air passes through rotor 202 and exits through radial face 202R of rotor 202, to a working chamber 711. As the rotor 202 rotates, a working chamber 711 expands, extracting air.
[00107] As the rotor 202 continues to rotate, the opening of the inlet passage 260 will ultimately pass through the peak 206. At the angle of rotation, the opening in the inlet passage 260 will be emitted by the peak, so that the inlet path or conduit cease to exist. At this angle, the compression chamber is established and, in fact, at that angle, the compression chamber is at its maximum volume (V1).
[00108] In the rotor angle shown, Fig. 7(a) also schematically illustrates the opening of the exhaust passage 270 at the radial face 202R of the rotor 202 in an adjacent lobe receiving region 720. from a working chamber 720 to the exhaust passage and finally to the external environment to the mechanism 200 through the outlet ports 265 in the exhaust hood 201D. This can be useful for compression ignition as it bypasses the need for exhaust gas recirculation and thus reduces emissions. For spark ignition operation, check valves could be installed to eliminate interference, which could be valuable for a spark ignition mode of operation, for example.
[00109] As indicated in the embodiment of Fig. 7(a), the inlet passage 261 and the exhaust passage 270 may, at some angle or range of angles of the rotor 202, both open into a working chamber from the which exhaust gases leave the engine, resulting in a mixture of fresh air and exhaust gases.
[00110] An alternative embodiment 750 is illustrated schematically in Figure 7(c). In this embodiment 750, the opening 751 in the radial face 202R of the rotor 202 is smaller than the corresponding opening in Fig. 7(a). Thus, inlet passage 261 does not open both the suction chamber and the exhaust chamber as in figure 7(a). A similar small opening leads from the exhaust chamber to the exhaust passage, but is not shown in Fig. 7(c) as it is not visible in the illustrated orientation of the rotor 202. As such, some embodiments include an inlet passage and a exhaust passage configured in such a way that the inlet and exhaust passages do not open simultaneously (either at a certain angle of rotation or for a range of rotation angles) in the same working chamber, and such that neither does the passage inlet or exhaust open the passage of more than one working chamber at a time.
[00111] Fig. 7(d) schematically illustrates airflow in another embodiment, which includes a housing view of the body 760, along with the inlet cover 761 and the exhaust cover 762. The inlet passages 260 are, in communication with an expansion working chamber 763, creating an inlet path by which a fresh charge 764 enters a working chamber 763. Air passes through inlet port 260 and enters inlet passage 261 at rotor 202. Air passes through rotor 202 and exits through radial face 202R of rotor 202 to a working chamber 263. As the rotor 202 rotates, a working chamber 263 expands, withdrawing the air. Similarly, Fig. 7(d) schematically illustrates the flow of exhaust gases 765 (e.g., combustion by-products in the form of flue gases) out of a working chamber through outlet ports 765 . Sealing Network
[00112] During the operation of a mechanism, including mechanism 200, for example, the work medium under pressure will escape from the work chambers through any available route. Accordingly, the mechanisms contain the seals to prevent or at least delay the escape of the working medium from the various working chambers. For this purpose, seals within a mechanism may be known as a "sealing net" or "sealing net". A sealing net system for rotary mechanisms is defined as a sealing system of flat joints, axial surfaces of the rotor to the plane, axial surfaces of the housing (covers), called side seals or face seals, and the radial surfaces of the rotor to the radial surfaces of the housing, called peak seals. In some embodiments, the sealing net may include buttons, which seal between the side seals and the peak seals. A sealing net system is constructed such that, together with the rotor and housing, a working chamber during compression, combustion and expansion is substantially closed such that the high pressure of the working medium does not leak into the low regions. pressure gauges including inlet and exhaust. In practice, there is always a leak path due to manufacturing tolerances, as well as a need to maintain a distance between the elements of the mesh itself or the members of the mesh and the rotor or housing to accommodate the thermal expansion of the components; if properly designed, these leaks could be minimized.
[00113] Consider, for example, the Wankel swivel mechanism, the only commercially successful swivel mechanism. Mechanism geometry is well known before Wankel. Wankel's contribution was that he developed a theoretical fence net, which made this mechanism technically and commercially viable.
[00114] One embodiment of a sealing net is illustrated schematically in Fig. 8(a), although other Figures described above also illustrate parts of various embodiments of a sealing net. The sealing network in Fig. 8(a) includes a face seal 801, a peak seal 205, and a button seal 810. Together, these seals prevent the working medium from escaping from the working chamber to a working chamber. adjacent, or to the external environment to the mechanism 200. For example, the peak seal 205 prevents the leakage of working medium from one working chamber to another from crossing the radial surface 821R of the rotor 821. The face seal 801 prevents that the leakage of working medium from a working chamber crosses the axial face 821A of the rotor 821.
[00115] With the exception of face seals, all members of the sealing network (eg peak seals and button seals) are stationary. This is a big advantage over Wankel, in which seals (eg apex seals in the rotor move with the rotor; see Figures 1(c) and 1(d)). In contrast to Wankel, due to the fact that the sealing network elements are stationary, it is possible to hold them with the lubricant directly (eg through the oil ports in a side cover), instead of injecting/granting the oil in the inlet port as in a Wankel mechanism. This will significantly reduce oil consumption and engine emission when compared to the Wankel engine.
[00116] Although the face seals are moving with the rotor, they are also constantly being filled with oil through the dedicated oil ports inside the covers and since the seals are never exposed to either the inlet or exhaust ports, Oil leakage from these seals is minimized if not completely eliminated. The face seal itself could have one or more small grooves, channels, ribs that can hold oil, such as oil supplied from the oil ports located within the covers near the button seals. The shape of the face seals is generated by the equation for the cycloidal curve such that the neutral plane of the seal always passes through three points (for the 3-lobe housing) on the cover, regardless of the angular position of the rotor. Any or all of these points determine the location of the oil ports. Thus, the face seals will be continuously exposed to the oil ports, while the oil ports are only exposed to the face seals, so no oil leakage will occur. In addition, the face seal is always adjacent to the virtual rollers that match the optional button seals. This allows the optional button seals, which take up space on the virtual button roller, to be positioned between the seal and the roller/seal. The button seal, as stated above, is stationary and extends on the flat surface, or rotor rest, closing the gap between the face seal and the peak seal. Face Seals
[00117] In the embodiment of Fig. 8(a), the face seal 801 is positioned behind the edge 821E of the rotor 821, where the axial face 821A of the rotor 821 meets the radial surface 821R of the rotor 821. The axial face portion 821A of rotor 821 between edge 821E and face seal 801 may be known as rest 811. In the embodiment of Fig. 8(a), the rest may have a width of one-tenth (1/10) of an inch, for example. Thus, the sealing net of Fig. 8(a) includes a button seal 810 which prevents the working medium from leaking from the axial face 821A of the rotor 821 between a peak seal 205 and the face seal 801. each of these seals are described in more detail below.
[00118] Each of the face seals described here may be of a cast iron material. However, other materials suitable for use as a face seal include, for example, alloy steel and other alloys. In general, a sealing face and the material from which it is made must have sufficient strength to perform in the most demanding environments of an internal combustion engine, as described herein, and must also have low friction, low wear and a low coefficient of thermal expansion. A face seal must also have some ability to hold lubricant (eg oil) and must have high thermal conductivity.
[00119] Although Fig. 8(a) schematically illustrates one embodiment of a face seal 801 on inlet face 821A of rotor 821, another face seal is disposed on an exhaust face of rotor 821, see, by For example, the face seals 801 in Fig. 6. These face seals 801, together with the opposite inlet cover 201C and the exhaust cover 201D, respectively, operate to articulate or prevent the escape of the working medium from the faces of the rotor 821. To that end, face seals 801 are disposed on rotor 821 such that face seals 801 are never exposed to inlet ports 266 or exhaust ports 265 at any angle of rotation of the rotor. Exposing face seals 801 to inlet ports 266 or exhaust ports 265 would mean that the seals are exposed to the external environment of mechanism 200, and could result in the loss of any lubricant at the seals. For example, Fig. 9 schematically illustrates the location of a face seal shown against inlet ports 260 of an inlet cover 201C. As shown, at no time does the face seal 801 appear in or through any of the inlet ports 266 or the exhaust ports 265.
[00120] One embodiment of a face seal 1001 is illustrated schematically in Figures 10(a) and 10(b). A face seal 1001 may be a continuous drop of material as in Fig. 10(a), or i may include several pieces of material coupled together as in Fig. 10(b). Some embodiments 1001 include multiple bands, as shown schematically in Fig. 11(a), for example, in which face seal 1001 includes three bands within a recess 1102 in rotor 202: inner band 1101A, outer band 1101C and the middle range 1101B.
[00121] An illustrative embodiment of such a strip 1101A is illustrated schematically in Fig. 11(b). Band 1101A includes spring portions 1103 which, when installed in recess 1102 in rotor 202, exert force against the bottom of recess 1102B so as to incline band 1101A in an axial direction from face 202F of rotor 202 and so , tilt the 1101A face seal against an opposite inlet cover or exhaust cover. This is useful for creating initial seal-to-bonnet contact. In operation, the air passes through the channel between the outer edge of the groove 1102 and the seal 1101A, is under the seal 1101A and generates an axial movement of the seal towards and in contact with the corresponding cover, generating a seal for high pressure operation. This is called a gas-actuated seal.
[00122] An alternative embodiment of a segmented track 1150 is illustrated schematically in Fig. 11(c). Segmented band 1150 includes a plurality of segments (1150A, 1150B) that are joined to form a band, and also includes spring portions 1150C.
[00123] Alternative face seal embodiments are illustrated schematically in Figures 12(a) to 12(g). In one embodiment, face seal 1201 is disposed on a beveled or beveled edge 1203 of rotor 1202. Thus, face seal 1201 has a roughly triangular cross section 1203. This configuration eliminates the need for a once button seal. that there is no rest space in the rotor 1202. In these types of seals, there is no groove and as such there is no channel between the rotor and the seal; gas cannot penetrate under the seal. However, the seal is still considered to be air activated, as the radial surface can be exposed to the gases, and thus receives the force that is converted by the bevel edge of the rotor into axial force and therefore the axial movement of the seal. towards the cover, thus facilitating the sealing function.
[00124] The above seal may have an axial (flat) surface 1210 in Fig. 12(d)) which could be a very short distance from the surface of the cover. This creates a gap for the gas to pass through and creates the pressure/force in a direction opposite to the axial force mentioned above. By varying the surface area of this gap, control of the axial force is allowed, which can serve as an unwanted rupture, thus reducing friction between the face seal and the cover.
[00125] If the beveled surface 1201B of the peak seal 1201 has the same bevel angle as the 1220 wedge seal the small portion of the peak seal could be developed to move along with the 1220 wedge seal, thereby reducing or eliminating fully the gap between pico seal 1201 and wedge seal 1202.
[00126] A column 1230 is disposed on rotor 1202 adjacent to face seal 1201 and serves to prevent face seal 1201 from rising to sloping edge 1203 and over axial face 1203F of rotor 1202. Wedge seal 1220 is disposed on another side of face seal 1201, opposite column 1230 and serves to prevent face seal 1201 from moving away from rotor 1201.
[00127] Fig. 12(d) also schematically illustrates the top profile 1205 of the 1201 face seal, which includes the grooves or channels 1206 that retain lubricant provided for the 1201 face seal. An alternative approach is apply a pattern to the face surface seal.
[00128] An alternative structure for maintaining a 1250 face seal on the 1202 rotor is illustrated schematically in Fig. 12(e). In this embodiment, face seal 1250 includes a locking spring arm 1251 that extends from face seal 1250 parallel to axial surface 1202A of rotor 1202. Spring arm 1251 extends into a cavity 1252 in rotor 1202 and around a pin 1253 within cavity 1252. Pin 1253 is thus used to allow a spring arm 1251 to pull face seal 1250 inward towards the center of the rotor. This will create a preload condition necessary to pull the face seal against the housing side, thus allowing the seal operation to begin. Under pressurized condition, gas pressure will take over.
[00129] Yet another approach to maintaining a 1260 face seal to the 1202 rotor is illustrated schematically in Fig. 12(f). In this embodiment, the sloping edge 1201 of the rotor 1202 includes a second opposing sloping area 1261A, such that the edge has a peak 1261B. Face seal 1260 includes a notch 1261A with a cross section configured to correspond with peak 1261B. A tongue portion 1260B of face seal 1260 engages opposite sloping area 1261 so as to prevent face seal 1260 from going away from edge 1261 and onto axial face 1260F of rotor 1202. A wedge seal 1220 secures the opposite side of face seal 1260.
[00130] Yet another alternative structure for maintaining a 1270 face seal on the 1202 rotor is illustrated schematically in Fig. 12(g). Again, as in previous configurations, the function of the latches and support mechanisms 1203 is to provide an initial preload on the seal.
[00131] Alternative approaches to face seals are illustrated schematically in Figures 13(a) to 13(g). In a first embodiment, a wire seal 1301 resides in a groove 1302 disposed in the rotor 1303. When the mechanism is cold, as in Fig. 13(a), the wire seal 1301 is between a rotor groove 1302 and the cover. side 1304, which can be an inlet cover or an exhaust cover, for example. Wire seal 1301, which could have a circular or triangular cross section, makes physical contact with both rotor 1303 and cover 1304 to form a seal. When the mechanism becomes hot, as in Fig. 13(b), the components expand due to thermal expansion. Thus, the gap between the components decreases, even though wire 1301 makes physical contact between a rotor 1302 and cover 1304.
[00132] Any high temperature steel or tungsten wire could be used for the 1301 wire seal. The leakage path for cold start conditions is calculated to be 0.11 mm2 in cross section for a wire diameter of 0.020 " ; for hot operating conditions, the cross section is 0.03 mm2. There are four locations for the leak path, two sides of the rotor x 2 pounded the apex seals; therefore, the total leak path for these types of side seals is 0.33 mm2 for cold start and 0.12 mm2 for hot operating conditions. This should be compared to the leakage area of ~4 mm2 for Wankel mechanisms [see "Performance and Combustion Characteristics of Direct-Injection Stratified-Charge Rotary Engines", Nguyen, Hung Lee, NASA 1987).
[00133] In another embodiment, illustrated in Figures 13(c) and 13(d), groove 1302 may be on edge 1305 of rotor 1303. In this embodiment, wire seal 1301 is held in place by wedge seal 1220.
[00134] In another embodiment, illustrated in Figures 13(e) and 13(f), the rotor 1303 includes a cavity 1310 below its axial face, which cavity opens to the radial surface 1306 of the rotor 1303. cantilever beam 1301 on axial surface 1303A of rotor 1303, whose beam 1311 may bend slightly in the axial direction. A wire seal 1301 is disposed in the cavity between two chamfered surfaces 1310A, 1310B and serves to incline the beam 1311 in the axial direction when gas exerts pressure on it, towards a forward facing cover (such as an inlet cover or an exhaust cover, for example). In some embodiments, the cantilever portion 1311 of the seal could be completely separated from the rotor.
[00135] An alternative embodiment is illustrated schematically in Fig. 13(g). It is very similar to the embodiment described above, except that the face seal 1370 could be aligned with respect to the axial surface 1303A of the rotor 1303. Such an embodiment allows multiple "layers" 1370A, 1370B of the face seal to be positioned on the rotor 1303. Oil will collect between the "layers" and will aid in sealing and lubrication.
[00136] An alternative embodiment is illustrated schematically in Fig. 14, and includes a face seal metal 1401. In this embodiment, the face seal metal 1401 reduces, but does not fully widen, the gap between the rotor and an adjacent cover . For example, in some embodiments, the microscopic gap between the seal and the cover can still be larger than the size of the gas molecules by 3 orders of magnitude.
[00137] To facilitate a seal, an oil film is provided to fill the gap mentioned above. Due to capillary forces, the oil will completely fill the gap and will resist the temperature of the working medium (eg gases) within the mechanism. Furthermore, the oil film will drastically decrease the friction between the seal and the cover, and thus increase the cooling of the mechanism.
[00138] As mentioned above, a beneficial feature of the cycloidal rotor geometry of the mechanism 200 is that, for at least three points on the cover, the lubrication ports (holes) can be moved such that they are always above the seal of face. Furthermore, the intake/exhaust ports on the covers are positioned such that the side seals never interfere with these ports. Thus, this geometry allows for the creation of a permanent oil layer on top of the face seals. To augment this layer, the top surface of the face seal may have grooves and/or oil pads of various designs to create the elastohydrodynamic lubrication conditions required to lessen friction between a face seal and an adjacent cover. rollers
[00139] As described above, in conjunction with the other embodiments, each spike 1505 in the circumferential body 1501 of a housing 1502 has a spike seal, but alternative embodiments, shown schematically in Figures 15(a) to 15(c) ) include rollers 1503 at each peak 1505. In such embodiments, cylindrical surface 1503A of roller 1503 is in sealing contact with radial surface 1511R of rotor 1511; in other words, the contact creates a seal between a roller 1505 and the rotor 1511. Each roller must have a radius equal to the theoretical roller radius (Rr) that corresponds to the rotor and the opening of the circumferential body.
[00140] In the embodiment of Figures 15(a) to 15(c), the roller 1505 is disposed within a cavity of the roller 1510, which is filled with 1520 oil or other lubricant to lubricate the roller 1503 and also to tilt the roller 1503 in a radial direction to engage rotor 1511. One or more housings 1520 are disposed in roller cavity 1510 to contain lubricant within roller cavity 1510 and help secure roller 1505 within roller cavity 1510. button 1530 and a face seal 1540, as discussed below, complete the seal net in this embodiment.
[00141] Alternative embodiments of a sealing net are illustrated schematically in Figures 16(a) to 16(d), and include a face seal 1601 and a button seal 1602 as discussed above. These embodiments, however, also include a wedge seal 1610. The wedge seal 1610 is disposed on a peak (i.e., is a peak seal), and is angled against the circumferential housing (omitted for clarity) by the element. spring 1611 so as to engage radial surface 1611R of rotor 1611. Fig. 16(d) schematically illustrates an alternative embodiment of wedge portion 1612 of a wedge seal 1611. Pico Seals
[00142] A variety of surge seals are available for use in various mechanism modes. As shown in Fig. 8(a), for example, the peak seals are disposed over the housing 880. In this embodiment, the peak seal 205 is disposed in a peak seal channel 825 at the peak 822. In some embodiments, the peak seal may be inclined in a radial direction towards rotor 821 so as to engage rotor 821.
[00143] To that end, each peak seal may include a spring that engages the peak seal channel 825, resulting in a radial force on the peak seal toward the rotor 821. Two such arrangements are illustrated so schematic in Fig. 17 and Fig. 18. Spike seal 1701 includes a spike seal body 1702 and a spring member 1703. Similarly, spike seal 1801 includes a spike seal body 1802 and an element spring 1803. In other embodiments, a peak seal may be biased into the peak seal channel by oil or other liquid disposed in the peak seal channel.
[00144] Another embodiment of a 1901 peak seal is illustrated schematically in Figures 19(a) and 19(b). Peak seal 1901 includes two pairs of seal elements 1902 and 1903 arranged side by side as shown in Fig. 19(a). Each pair would consist of a small 1903 and a large 1902 segment supported by the 1904 springs. A 1910 lubrication channel between the segments supplies lubricant (such as oil) to the seal/rotor interface directly. This is distinguishable from prior art swivel mechanisms, which inject oil into the mechanism to reach seals in the rotor. By supplying oil directly to the seal and seal/rotor interface, less oil is required and less oil is burned in the mechanism, thus reducing oil consumption and emissions.
[00145] The edges of the peak seals 1925 where the peak seal meets the rotor are preferably curved, as illustrated schematically in Fig. 19(b). In some embodiments, the peak seals are curved with a radius of curvature Rr, the theoretical roller radius. This will minimize apex sealing movement.
[00146] Still other peak sealing modalities 2001, 2010, and 2020 are illustrated schematically in Figures 20(a) to 20(c). These seals are split or perforated 2020 to allow gas to enter below the seal surface to equalize pressure from outside the seal gas. To minimize leakage, the space between the seal and the rotor or insert must be filled with 2003 high temperature metal wool.
[00147] It should be noted that, unlike Wankel apex seals, which require approximately 0.070 to 0.110 inch of movement for seals on their rotor (for an approximately 100 kW mechanism), no peak seals in the various described modalities above moves more than 0.01 inch (0.0254 centimeters) at most and, in some modes, possibly much less. Button Seals
[00148] A simple button seal 810 is illustrated schematically in Fig. 8(a) and may be of a known type, such as the button seals used in Wankel mechanisms, for example. However, when rotor 821 expands due to heating, face seal 801 located in a groove in rotor 821 moves in a radially outward direction. Depending on the choice of materials and operating temperatures, the 801 face seal may interfere with the 810 knob. A solution to this problem may be to undersize the knob or allow the knob to move along with the face seal during thermal expansion of the rotor 821.
[00149] To that end, the button 810 in Fig. 8B is disposed in a button sleeve 856. The button sleeve 856 allows the button 870 to move slightly in the radial direction in conjunction with the thermal expansion of the rotor 821. The button 870 of the button seal 810 has a circular cross section and a button radius. Alternative Modalities
[00150] Although the above modalities have been described in the context of a cycloidal rotor, many of the features can be used in a variety of mechanisms.
[00151] For example, a housing of the rotating mechanism 2100 which has a three-lobe rotor 2102 is illustrated schematically in Fig. 21 in which both the inner rotor 2102 and the outer rotor 2103 rotate at constant speed around fixed axes inside housing 2100. Inner rotor 2102 has one tooth less than outer rotor 2103. Rotor 2102 could include a face seal in accordance with the embodiments described above. An alternative embodiment of a mechanism 2300 with a three-lobe rotor 2301 is illustrated schematically in Fig. 23.
[00152] In the embodiment of Fig. 21, a substantially constant volume is created when the inner rotor 2102 engages the corresponding lobes 2104 of the outer rotor 2103.
[00153] Inner rotor 2102 rotates and drives the outer rotor. Spring-loaded or oil-supported 2110 rollers help seal and reduce friction. The intake ports and exhaust ports are shaped and located so that the intake volume is less than the expansion volume. A combustion chamber of substantially constant volume is possible due to the relatively slow rate of volume expansion that exits shortly after combustion.
[00154] During the operation of this mode, the variable volume cavities, or work chambers, are created by the internal and external rotors and the housing covers. Each chamber rotates and in a course of its movement changes the volume from the minimum, V2, which corresponds to the constant volume combustion chamber volume, to a maximum, V4, which corresponds to an exhaust volume. Fuel is injected through stationary fuel injectors (not shown) located inside blankets. Operation is typically according to an HEHC-S cycle where air is purged (eliminated and induced), air is compressed, fuel is injected and combusted, and combustion products are expanded. Although a 3/4 setting is shown, 2/3, 4/5, etc. settings. are also possible. This mechanism can also be operated in a digital mode.
[00155] Another embodiment includes a single propeller blade configuration. A mechanism assembly with such a rotor is illustrated schematically in Figures 22(a) to 22(c). This modality includes a housing (the external gerotor) 2201 and a single propeller blade 2202 (an internal gerotor) 2202, which rotate around its axis, while the axis rotates simultaneously (in the eccentric 2203) with relation to housing 2201. Inner gerotor 2202 uses one less tooth (or lobe) than the outer one that has the lobe reception regions. A substantially constant volume (2200) is created when the inner gerotor lobe engages with the corresponding outer gerotor lobe. Rotor 2202 could include a face seal in accordance with the embodiments described above.
[00156] The housing 2201 of this modality together with the propeller blade 2202, forms 4 (in this case) variable volume cavities, or chambers, which are analogous to the four-cylinder stud mechanism. The blades 2202 that engage each chamber, in turn, simulate a 4-stroke operation. The working medium will be induced, compressed, burned, expanded and escaped.
[00157] The housing will house a combustion chamber of constant volume which can be situated in a suitable housing, not on the roof. Seat valves or conventional ball valves or disc valves can be used to control the intake and exhaust stroke time. Valves are not shown in this Fig. If the constant volume combustion chamber 2220 is situated within the housing as shown, then cylinder valves may be employed. These valves could be concentric with the combustion chamber and would rotate exposing the constant volume combustion chamber opening to the intake and exhaust ports. Having the inlet valves open while the chamber volume is being turned down allows for a smaller volume than the exhaust volume, thus achieving a part of the Atkinson cycle. This mode can also be operated in a digital mode of operation and can be used with a fuel injection system.
[00158] An alternative embodiment of a mechanism 2301 with a three-lobe rotor 2300 is illustrated schematically in Fig. 23.
[00159] Fig. 24 schematically illustrates another embodiment of a mechanism 2401, in which a two-lobe rotor (generally N-lobe) 2402 is rigidly coupled to an input/output shaft 2403. The shaft 2403 rotates within housing 2404 along with the second external 3-lobe rotor (usually N+1-lobes) 2405 which is mounted eccentrically to the 2-lobe rotor. The side covers contain the inlet/outlet ports through which the fresh cargo is blown through an air outlet mode, thus achieving exhaust and inlet at the same time and performing a 2-stroke operation. In addition to the simplicity of kinematics and fewer counting parts, this configuration can perform a cycle of the mechanism known as the "HEHC" cycle, as described in US Patent No. US 2001/023814 A1, the disclosure of which is incorporated herein in in its entirety, by way of reference.
[00160] Fig. 25 schematically illustrates yet another embodiment of a mechanism 2501. In the embodiment, a 2-lobe inner rotor (generally N-lobe) 2502 is stationary, and a 3-lobe outer rotor (in (general, N+1-lobe) 2503 is configured to rotate and turn around the stationary inner rotor 2502. A drive rod 2504 with the rollers 2505 above the 3-lobe rotor 2503. This is a kinematically simple configuration that has few movable parts.
[00161] Fig. 26, Fig. 27 and Fig. 28 schematically illustrate in which the suppression or synchronization, rotation and which orbit of the rotor can be achieved without the gears
[00162] Fig. 26 schematically illustrates a cam 2601 attached to a rotor 2602 and three rollers 2603 attached to the cover (the cover is omitted for clarity). Alternatively, a symmetrical configuration, such as two cams/6 rollers, with a second one coming on the outside of the rotor, and the fourth, fifth and sixth rollers on the other cover, can also be used. It is observed that the cam profile is calculated by the same formulas as the 2602 rotor itself, except that the formation radius (R) and the roller radius (Rr) are different, while the eccentricity is equal to that of the 2602 rotor.
[00163] Fig. 27 schematically illustrates a different configuration where the cam 2701 is fixed to the cover, while the two rollers are fixed to the rotor.
[00164] Fig. 28 schematically illustrates an embodiment known as the W plate. In this embodiment, the rollers 2803 are fixed in a separate central part 2802 such that the rollers "capture" the movement of the rotor and translate it into purely movement rotation of the central part.
[00165] Such a motor has a housing that has a working cavity, a shaft with an eccentric part, a rotor disposed on the eccentric part and inside the working cavity, a central part comprising a plurality of rotors, a coupled plate fixedly to the shaft, the plate having several openings, such that each of the rollers passes through a corresponding one of the plurality of openings. In operation, the rotation of the rotor causes the rollers to circulate around the openings, such that the eccentric movement of the rotor is transferred to the circular movement in the plate.
[00166] It is observed that the characteristic of the modalities of Figures 26 to 28 could be mixed and matched as desired to avoid dead spots. Furthermore, many other modalities should be apparent to those skilled in the art.
[00167] Another embodiment 2901 is illustrated schematically in Figures 29(a) to 29(b). In a cycloid engine, the eccentric takes most of the charge from the gas pressure. The function of the gear pair is to eliminate the rotor in relation to the casing. Having a relatively small pinion size limits the shaft size and therefore the rotor thickness - leading to most pancake similar geometries. Fig. 29 shows an alternative approach including additional chamber(s), 2903 built into rotor 2901. Three (or six, with three on each side of rotor) 2905 cam followers rigidly attached to cover(s) will eliminate rotor without the gears. The cam 2904 and cam followers 2905 are described by the same equations and eccentricity as the rotor 2902 itself. Of course, the radii R and Rr are different from those of the rotor. The added benefit is that potentially higher speeds are possible, as three rather large rollers accept inertial loads as opposed to a single tooth.
[00168] An alternative embodiment of a mechanism is illustrated schematically in Fig. 30(a), Fig. 30(b), and Fig. 30(c). In this embodiment, rotor shaft 3210 is rigidly connected with rotor 3202. Rotor shaft 3210 is eccentrically supported by two input/output 3050 shafts, one input/output shaft located in each axial direction of the rotor. Each 3050 input/output shaft has two roller surfaces 3050A, 3050B, where the outer surface of the 3050A bearing is centered with the center of the motor, and the inner roller surface 3050B is eccentrically configured, and therefore has the shaft of the motor. rotor 3210 eccentrically. Due to the eccentricity of the 3050 input/output shafts, these can serve as counterweights to dynamically balance the rotor, eliminating the need for separate counterweights while allowing roller and counterweights to be close to the rotor. The 3.050 input/output axes translate the orbital motion of the 3202 rotor into purely rotary motion. Rotor synchronization, however, still needs to be done by gears or other means discussed above, for example with the 3051 train. The 3060 roller may be hydraulic instant or other type.
[00169] An alternative configuration for exchanging gas (inlet and exhaust) is also shown in Fig. 30(b), and Fig. 30(c). This alternative can also be applied, totally or partially (for one of the toll intake and exhaust strategies), with the embodiment shown in Fig. 2. In this modality, the engine air intake, and the exhaust gases of the medium of work from the motor, takes place through the shaft (3210), where the shaft is rigidly connected with the rotor. Specifically, the inlet port (3110), communicates with passages through the shaft inlet/outlet holes, the passage then continuing through a hallowing in the rotor shaft (3210). This passage continues through the channel (3260) in which the rotor is rigidly connected, and, in turn, periodically communicates with a working chamber (3225). The exhaust passage is similarly constructed at the axially opposite end of the rotor and shafts, allowing for communication between the periodically (exhaust) working chamber and the environment. Additional elements shown are exhaust channel in rotor (3161), exhaust channel in shaft (3111), exhaust port (3112).
[00170] The various modalities described above can be operated at a partial load, with the use of conventional fuel modulation or skip fuel cycle methods, as described below. For example, to operate at part load, especially with heavy fuels like diesel, JP8, etc., a number of options are available. For example, the amount of fuel supplied to the engine can be modulated as in conventional engines.
[00171] Alternatively, the motor can be run in "digital mode", executing each burn cycle at full load, but ignoring the percentage of cycles. For example, jumping every three cycles would allow the engine to run at less than 70% of full power; skipping eight out of ten cycles will allow the engine to run at less than 20% load, etc. The skipping cycle can be implemented simply by cutting off the fuel supply. In this case, the compressed air in the compression chamber will expand into an expansion chamber even if no combustion took place in the interlayer. This will not only occur with a minimal loss of energy, as working medium (air in this case) acts as an air spring, but some energy recovery is possible, as heat is transferred from the walls of the working chamber to the air, thus cooling the engine internally, while increasing the temperature and therefore the pressure of the expanding gases, thus some of the losses associated with cooling, the engine can be partially recovered as useful work.
[00172] Fig. 31 schematically illustrates a mode 3100 including an internal gear and pinion with a 3:2 ratio, or alternately 2:1 if intermediate(s) are moved by the eccentric shaft 3101.
[00173] Fig. 32 schematically illustrates a mode configured to run the high-efficiency hybrid cycle ("HEHC").
[00174] In analogy with HEHC conventional piston engines can be called 4-stroke cycles, as they have four distinct strokes: intake, compression, combustion and expansion and exhaust. An elimination variant of the HEHC (HEHC s) is equivalent to a 2-stroke cycle in which the engine, at the end of expansion, the cavity is blown out through ambient air, which removes the combustion gases and recharges the cavity with a fresh air or a responsible air/fuel mixture.
[00175] A HEHC pressure-volume diagram is shown in Figures 1 and 2 of the US patent application publication 201110023814 Al. In the initial state, only air is compressed, as in the diesel cycle, during the compression stroke. Fuel can be added near the end of the compression stroke, or just after the compression stroke. As the air is already compressed at this point to a relatively high pressure (~55 bar), high injection pressures similar to those used in modern diesel engines are needed to achieve complete combustion and exhaust pollutants. Operation is similar to Diesel engines except for the fact that combustion takes place at constant volume, as achieved in Otto cycle engines that are spark ignited. However, unlike ignition engines, combustion takes place due to the injection of fuel into a very hot compressed air. That said, however, a spark plug can be used as well. Expansion occurs in this cycle of environmental pressures, similar to the Atkinson cycle.
[00176] Part load operation can be achieved by modulating fuel, as in diesel engines, or ignoring some of the injections together, as will be described below.
[00177] Due to similarities of the aforementioned diesel cycle, Otto and Atkinson, this cycle is referred to as a "Hybrid Cycle". It may also possible to inject water during combustion and/or expansion strokes as this can improve engine efficiency while cooling mode from within the engine. If leakage between moving components and housing is kept at a low level, the maximum efficiency of this cycle should be around 57%, while the average efficiency should be above 50%.
[00178] The modality illustrated schematically at 3201 in Figures 32(a) - 32(f) comprises a rotor inside a casing 3202 3203. As the rotor rotates at 3202, several chambers are formed that work with housing 3202 to run a HEHC cycle.
[00179] The cycle begins with the beginning of the fresh air intake stroke, at which point the rotor 3202 is within lobe revive region 3210, as illustrated schematically in Fig. 32(a). In this position, an intake duct is opened inside the 3201 engine, for example, as illustrated in the previous embodiments. At the point where consumption is complete, the air inlet is closed and the air (which may be referred to as a working medium) is confined within the working chamber 3250, as illustrated schematically in Fig. 32(b). As the rotor continues to rotate, the air inside the working chamber is compressed 3250, in the compression phase of the HEHC cycle. As such, at this point in the cycle, the working chamber 3250 is a compression chamber. When the compression chamber is initially cut from the outside environment of the 3201 engine, it has a volume of V1.
[00180] As the rotor continues to rotate 3202, it eventually completely occupies the 3210's receiving region lobe, and the working medium is confined within a 3251 combustion chamber, as illustrated schematically in Fig. 32(c) . Combustion chamber 3251 has a volume V2, which is less than volume V1. At this point, the working medium includes both compressed air and a fuel and combustion starts. Combustion can be initiated by any means, but in this mode of combustion it is initiated by the degree of compression of the working medium.
[00181] Combustion increases the pressure of the working medium, which in turn exerts a force on the rotor 3202, causing the rotor 3202 to continue its rotation, and thus allowing the working medium to expand into an expansion phase of the HEHC cycle, as illustrated schematically in Fig. 32(d). The volume of the working chamber, and therefore the volume of the working medium, expands until the volume (V3) exceeds the input volume of V1, as schematically illustrated in Fig. 32 (e).
[00182] Finally, at the end of the expansion phase, the working medium is expelled to the outside environment of the 3201 engine, as illustrated schematically in Fig. 32(f).
[00183] Although the above modalities have been described in terms of internal combustion engines, some modalities can be used as an expander, such as in a steam engine, for example. In fact, several modes can be configured as an external heat engine (eg an external combustion engine). For example, heat can be supplied to a working chamber by placing a heat pipe into the volume described above, such as a combustion chamber, to allow the transfer of external heat from solar, combustion, nuclear, etc. into that chamber.
[00184] Indeed, disclosure here will support a wide variety of possible claims. For example, in arrangements with a wedge seal, and/or with a sealing face on a beveled edge of a rotor, pressure (such as gas pressure, for example) will generate a radial force on the face. of sealing, and that the will power, in turning, polarization of the face seal to mount the bevel edge, thus converting the force to the axial movement of the seal of the bevel edge of the rotor. Also, in some embodiments, a face seal may have an axial (flat) surface which could be a very short distance from the surface of the cover. This creates a space for the gas to pass through and create a pressure/force in the opposite direction to the axial force mentioned above. The surface area of this gap controls the axial force - which often serves as an unwanted brake, thus reducing friction between the face seal and the cover.
[00185] If a surface of the peak seal has the same bevel angle as the wedge seal, the small portion of the peak seal could be developed to move together with the wedge seal, thus reducing or totally eliminating the gap between the peak and wedge seal.
[00186] A variety of seals, such as face and peak seals, are described above, and or all of which can be claimed, either alone or in the context of a seal network.
[00187] In addition, the modality mechanisms described here can be operated in a variety of modes. For example, the modalities can be operated in a two-cycle mode, or a variety of 4-cycle modes, which include, but are not limited to, performing one cycle of HEHC (i.e., the HEHC operation).
[00188] Some other possible claims are listed below. P1. Rotating mechanism, comprising:
[00189] a housing having a work cavity;
[00190] a shaft having an integral eccentric rotor with, or fixedly attached to the shaft, the eccentric rotor disposed within the working cavity;
[00191] at least one hydrodynamic bearing that supports the shaft, so as to allow the eccentric rotor to rotate within the working cavity. P2. Rotating mechanism, comprising:
[00192] a housing having a working cavity;
[00193] an axis, the axis having an eccentric part;
[00194] a rotor disposed on the eccentric part and inside the working cavity;
[00195] a central part comprising the plurality of rotors;
[00196] a plate fixedly coupled to the shaft, the plate comprising a plurality of openings, each of the plurality of rollers passing through that corresponding one of the plurality of openings;
[00197] in which the rotation of the rotor causes the rollers to circulate around the openings, such that the eccentric movement of the rotor is transferred to the circular movement in the plate. P3. Rotating mechanism, comprising:
[00198] a housing having a work cavity;
[00199] a sealing net;
[00200] a rotor shaft having an integral rotor with, or fixedly attached to the shaft, the rotor disposed within the working cavity; and
[00201] at least one input/output shaft disposed in the mechanism so as to eccentrically support the rotor shaft. Q4. The mechanism of potential claim P3, wherein the input/output shaft is configured to serve as a counterweight to dynamically balance the rotor. Q5. The mechanism of potential claim P3, the rotor shaft and the input/output shaft further comprising the inlet and exhaust passages (e.g. a swivel mechanism having a gas exchange system comprising the inlet port and output and passages through the input/output shaft and rotor). P6. The mechanism of potential claim P3, further comprising a hydrodynamic bearing that supports the input/output shafts.
[00202] The embodiments of the invention described above are intended to be exemplary only; numerous variations and modifications will be evident to those skilled in the art. All such variations and modifications are intended to be within the scope of the present invention as defined in any appended claims. For example, any of the various seals presented above can be used with any of the various rotors described here. Similarly, any one of several inlet and exhaust ports can be used with any of the rotors and/or shafts described herein.

权利要求:
Claims (11)
[0001]
1. Mechanism (200) of the type that includes a cycloidal rotor (202) having N lobes (202A, 202B) and a housing (201) having a corresponding set of N+1 lobe receiving regions (250, 252, 253) for successively receiving the lobes as the rotor rotates about an axis relative to the housing, the housing having (i) a pair of axially disposed sides on the first and second sides of the rotor, and (ii) a peak (205, 206, 207) disposed between each pair of adjacent lobe receiving regions; and (iii) an inlet port (260) and an outlet port (265), the mechanism characterized by: a plurality of peak seals (251A, 251B, 251C), at least one of the plurality of peak seals disposed at each peak and configured to maintain contact with the rotor over a period of rotor rotation, each peak seal being inclined radially against the rotor along the rotor rotation, due to a cycloidal geometry of the rotor and the l-receiving parts. obo; a first passage (261) defined in the rotor to cyclically communicate between the inlet port and a working chamber (711), the first passage configured to allow air to enter from the radial face (202R) of the rotor into the working chamber, the working chamber defined as a volume that lies between two peak seals, the housing and the rotor; a second passage (270), distinct from the first passage, defined in the rotor to cyclically communicate between the outlet port and a working chamber, the second passage configured to allow exhaust gas to exit from the working chamber. through the radial face (202R) of the rotor; a first face seal (801) disposed between the first side of the housing and the rotor configured to seal the working chamber; and a second face seal (801) disposed between the second side of the housing and the rotor configured to seal the working chamber; wherein the first face seal is disposed near an outer edge of the rotor, the outer edge defined by an intersection of an axial face (821A) of the rotor with a radial face of the rotor, wherein the passages and face seals are configured to make each face seal maintain contact with both the rotor and one side of the housing through all angular positions of the rotor while avoiding communication with either port.
[0002]
2. Mechanism according to claim 1, characterized in that each peak seal has a contact region with the rotor, and the contact region is curved with a radius of curvature equal to a radius of curvature of a roller theoretical, in which the theoretical roller is uniquely defined by the rotor geometry and the geometry of the lobe receiving regions.
[0003]
3. Mechanism according to claim 1, characterized in that the second face seal is disposed near a second outer edge of the rotor, the second outer edge defined by an intersection of a second axial face of the rotor with the face rotor radial.
[0004]
4. Mechanism according to claim 1, characterized in that the first axial face is disposed on the axial face of the rotor, and the axial face includes a rest on the outer edge, where the rest is between the outer edge and the first face seal, the mechanism further comprising a button seal arranged to contact the rotor and the first face seal on the rest.
[0005]
5. Mechanism according to claim 1, characterized in that at a first angle of the rotor inside the housing the working chamber forms a compression chamber that has a maximum compression chamber volume, and at a second angle of the rotor inside the housing the working chamber forms an expansion chamber which has a maximum expansion chamber volume, the maximum expansion chamber volume which is greater than or equal to 1.0 times the maximum compression chamber volume.
[0006]
6. Mechanism according to claim 5, characterized in that the maximum expansion chamber volume is at least 3 times the maximum compression chamber volume.
[0007]
7. Mechanism according to claim 1, characterized in that it further comprises a plurality of lubrication channels on at least one of the sides, each of the plurality of lubrication channels arranged so as to release the lubricant to those corresponding to the plurality of peak seals.
[0008]
8. Mechanism according to claim 1, characterized in that it further comprises a lubrication channel on at least one side, the lubrication channel arranged to continuously release the lubricant to those corresponding to the face seals.
[0009]
9. Mechanism according to claim 1, characterized in that a housing has a working cavity, and a combustion chamber (820) in fluid communication with the working cavity, wherein the mechanism further comprises: a piston (850) disposed over the housing and configured to controllably enter and withdraw from the combustion chamber; a rotor rotatably mounted within the working cavity so as to form a working chamber of variable volume with the housing at different angles of rotation of the rotor within the working cavity; and a controller synchronized with the angle of rotation of the rotor to cause the piston to controllably enter and be withdrawn from the combustion chamber so as to make the combined volume of the working chamber and the combustion chamber constant for a range of rotor rotation angles.
[0010]
10. Mechanism according to claim 1, characterized in that: the housing has a working cavity, wherein the mechanism further comprises: an axle (210), having an eccentric part (210B); a rotor (2602) having a first axial face, and a second axial face opposite the first axial face, the rotor disposed on the eccentric portion and within the working cavity, the rotor comprising a first cam (2601) on the first axial face, the first cam that has an eccentricity that corresponds to the eccentricity of the eccentric part of the shaft; and a cover integral with, or fixedly attached to the housing, the cover comprising a plurality of rollers (2603), each roller engaged with the cam, the cam guiding rotation of the rotor as the rotor rotates within the cavity. and rotates around the axis.
[0011]
11. Rotary mechanism according to claim 10, characterized in that it further comprises a second cam (2903) on the second axial face of the rotor.

类似技术:

---

公开号 | 公开日 | 专利标题

---

BR112013024765B1|2021-06-22|CYCLE ROTOR MECHANISM

---

JP2015222077A|2015-12-10|Rotary machine with roller controlled vane

---

CA2844015C|2021-01-26|Rotary internal combustion engine with pilot subchamber

---

JP2011530044A|2011-12-15|Equal volume heat addition engine and method

---

US20140020384A1|2014-01-23|Positive displacement rotary vane engine

---

CA2179468C|2007-09-04|Rotary internal combustion engine and rotary internal combustion engine cycle

---

RU2478803C2|2013-04-10|Rotary piston internal combustion engine

---

US20190178084A1|2019-06-13|Rotary energy converter with retractable barrier

---

US10184392B2|2019-01-22|Single chamber multiple independent contour rotary machine

---

RU2538990C1|2015-01-10|Rotor-piston internal combustion engine

---

CN107709703B|2021-06-04|Single-chamber multi-independent profile rotary machine

---

JP2003505632A|2003-02-12|Rotary piston engine / positive displacement device

---

US11078834B2|2021-08-03|Rotary valve continuous flow expansible chamber dynamic and positive displacement rotary devices

---

US3716989A|1973-02-20|Rotary jet twin-propulsion engine

---

US20120134860A1|2012-05-31|"turbomotor" rotary machine with volumetric expansion and variants thereof

---

JP4729041B2|2011-07-20|Rotary device and method of operating rotary device

---

JP6169784B2|2017-07-26|Advanced alternate piston type rotary engine

---

RU2659639C1|2018-07-03|Rotary piston internal combustion engine

同族专利:

---

公开号 | 公开日

---

EP2691607A2|2014-02-05|

---

JP2014514492A|2014-06-19|

---

BR112013024765A2|2019-08-13|

---

RU2013142838A|2015-05-10|

---

US9810068B2|2017-11-07|

---

US20180066520A1|2018-03-08|

---

WO2012135556A2|2012-10-04|

---

EP2691607B1|2016-07-20|

---

ES2590777T3|2016-11-23|

---

WO2012135556A3|2013-10-03|

---

JP2018168856A|2018-11-01|

---

CA2830653C|2019-11-05|

---

CN103477030A|2013-12-25|

---

US20120294747A1|2012-11-22|

---

US8523546B2|2013-09-03|

---

US10221690B2|2019-03-05|

---

CA2830653A1|2012-10-04|

---

JP6370214B2|2018-08-08|

---

EP3173579B1|2019-05-08|

---

KR20140022029A|2014-02-21|

---

EP3173579A3|2017-09-06|

---

JP2017150495A|2017-08-31|

---

KR102039448B1|2019-11-01|

---

EP3173579A2|2017-05-31|

---

RU2609027C2|2017-01-30|

---

US20140003988A1|2014-01-02|

---

US9353623B2|2016-05-31|

---

JP6416319B2|2018-10-31|

---

CN103477030B|2016-11-16|

---

US20160341042A1|2016-11-24|

---

JP6718917B2|2020-07-08|

引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

---

BE349425A|

---

US813018A|1902-04-25|1906-02-20|Moses S Okun|Rotary engine and motor.|

---

US748348A|1902-06-16|1903-12-29|Cooley Epicycloidal Engine Dev Company|Rotary fluid-engine.|

---

US902585A|1907-05-27|1908-11-03|Friedrich Carl Krueger|Rotary engine.|

---

US939751A|1909-02-27|1909-11-09|George Schulz|Rotary engine.|

---

US1061142A|1909-10-21|1913-05-06|Nikola Tesla|Fluid propulsion|

---

US1144921A|1914-06-24|1915-06-29|Chester N Stever|Gas-engine.|

---

US1329559A|1916-02-21|1920-02-03|Tesla Nikola|Valvular conduit|

---

US1225056A|1916-05-02|1917-05-08|Lewis W Riggs|Rotary internal-combustion engine.|

---

US1409986A|1918-02-25|1922-03-21|American Rctary Engine Co|Packing for rotary engines and compressors|

---

US1406140A|1919-11-24|1922-02-07|Anderson Axel Julius|Rotary engine|

---

US1424977A|1920-05-01|1922-08-08|Price Quesenberry|Packing means for rotary engines|

---

US1976042A|1929-06-12|1934-10-09|George W Skouland|Rotary internal combustion engine|

---

US2091411A|1936-06-15|1937-08-31|Mallory Marion|Internal combustion engine|

---

US2175265A|1936-10-15|1939-10-10|Gustave J Ornauer|Rotary engine|

---

US2154456A|1937-01-30|1939-04-18|Rudolph A Riek|Rotary machine|

---

US2366213A|1942-08-28|1945-01-02|William E Hughes|Internal-combustion motor|

---

US2344496A|1943-08-26|1944-03-21|Conradt Walter|Internal combustion engine|

---

US2762346A|1952-12-08|1956-09-11|Robert S Butts|Rotary internal combustion engine|

---

US2766737A|1954-06-08|1956-10-16|Sprinzing William|Injection valve for rotary type internal combustion engine|

---

FR1153857A|1955-04-14|1958-03-28|Rotary motor|

---

US3064880A|1957-09-19|1962-11-20|Nsu Motorenwerke Ag|Sealing arrangement for rotary mechanism|

---

US3010440A|1957-12-18|1961-11-28|Roth Adolf|Internal combustion engine with double acting pistons|

---

US3098605A|1960-05-27|1963-07-23|Curtiss Wright Corp|Cooling and lubrication system for rotary mechanisms|

---

FR78955E|1960-11-21|1962-10-05|Renault|Improvements to rotary engines|

---

US3102682A|1961-02-10|1963-09-03|Nsu Motorenwerke Ag Neckarsulm|Liquid cooling for the rotor of a rotating-piston engine|

---

US3205872A|1961-05-23|1965-09-14|Pomasanow Nikolay|Rotary internal combustion engine|

---

DE1175942B|1961-06-13|1964-08-13|Nsu Motorenwerke Ag|Air-cooled housing for rotary piston internal combustion engines|

---

FR1301866A|1961-06-29|1962-08-24|Renault|Rotary motor with rotating distributor|

---

US3120921A|1961-07-25|1964-02-11|Royalty Holding Corp|Automatically adjusting and compensating seal means for rotary machines|

---

GB988161A|1961-07-26|1965-04-07|Rota Societa Meccanica Italian|Improvements in or relating to rotary internal combustion engines|

---

US3139233A|1962-04-30|1964-06-30|Curtiss Wright Corp|Seal construction for rotary mechanisms|

---

DE1401994A1|1962-07-25|1968-11-21|Daimler Benz Ag|Rotary piston internal combustion engine in trochoid design|

---

US3245388A|1962-09-05|1966-04-12|Nsu Motorenwerke Ag|Combustion means for rotary combustion engine|

---

DE1224982B|1963-03-07|1966-09-15|Nsu Motorenwerke Ag|Liquid cooling for pistons of rotary piston engines|

---

DE1233199B|1963-03-09|1967-01-26|Daimler Benz Ag|Rotary piston internal combustion engine in trochoid design|

---

US3220388A|1963-06-21|1965-11-30|Dwight M Brown|Rotary internal combustion engine|

---

FR1372662A|1963-08-09|1964-09-18|Renault|Improvements to rotary engine lobe rotors|

---

FR1395578A|1963-10-11|1965-04-16|Internal combustion engine|

---

FR1398965A|1964-04-04|1965-05-14|Renault|Rotary motor rotor|

---

US3301193A|1965-01-28|1967-01-31|Moorex Ind Inc|Alternating piston engine|

---

US3316887A|1965-05-24|1967-05-02|William M Melvin|Rotary engine|

---

US3422801A|1965-11-15|1969-01-21|Kiyoshi W Mido|Rotary combustion engines|

---

DE1526392A1|1966-03-17|1970-04-23|Kloeckner Humboldt Deutz Ag|Rotary piston internal combustion engine, in particular rotary piston internal combustion engine|

---

US3441007A|1966-11-10|1969-04-29|Johannes Kwaak|Rotary piston engine|

---

US3503374A|1967-02-20|1970-03-31|Ehrlich Eng Ltd|Oscillating vane machines|

---

US3408991A|1967-07-12|1968-11-05|William B Pritchett Jr|Oscillating machine|

---

US3557813A|1968-05-10|1971-01-26|Western Electric Co|Cam actuated fluidic timing system|

---

GB1313842A|1969-02-07|1973-04-18|Jones A A|Rotary engines|

---

US3595014A|1969-12-30|1971-07-27|Mcmaster Harold|Rotary engines|

---

US3658447A|1970-04-09|1972-04-25|Charles Bancroft|Pressure sealing assemblies for rotary vane piston devices|

---

US3687117A|1970-08-07|1972-08-29|Viktor Mitrushi Panariti|Combustion power engine|

---

US3872838A|1970-11-30|1975-03-25|Volkswagenwerk Ag|Combustion engine having a rotary type piston arrangement|

---

US3692002A|1971-02-08|1972-09-19|Robert H Williams|Rotary internal combustion engine|

---

US3815555A|1971-03-19|1974-06-11|Europ De Propulsion Sa|Hydraulic heat engine|

---

US3797464A|1971-12-06|1974-03-19|H Abbey|Balanced rotary combustion engine|

---

US3754534A|1971-12-23|1973-08-28|Gen Motors Corp|Rotary combustion engine ignition|

---

US3769788A|1972-03-09|1973-11-06|Conservor Inc|Low pollution, high efficiency prime mover system and process|

---

US3891359A|1972-03-24|1975-06-24|George W Meacham|Rotary engine|

---

US3845745A|1972-07-03|1974-11-05|C Dunlap|Water injection system for an internal combustion engine|

---

US3844117A|1972-08-04|1974-10-29|T Ryan|Positive displacement brayton cycle rotary engine|

---

US3809024A|1972-08-14|1974-05-07|H Abbey|Four-stroke and two-stroke rotary internal combustion engine|

---

CA977686A|1972-10-13|1975-11-11|Lloyd D. Chisholm|Rotary engine|

---

US3851999A|1972-12-05|1974-12-03|William H Bibbens|Sealing assembly|

---

US3885799A|1972-12-05|1975-05-27|William H Bibbens|Sealing assembly|

---

US3811804A|1972-12-29|1974-05-21|L Roth|Rotary engine with interengaging rotating members and reversing valve|

---

US3845562A|1973-08-16|1974-11-05|Mobil Oil Corp|Method and apparatus for determining the thickness of a gap between elements|

---

US3884600A|1973-11-08|1975-05-20|Gray & Bensley Research Corp|Guidance means for a rotary engine or pump|

---

JPS5217187B2|1973-12-21|1977-05-13|

---

US4083663A|1974-01-11|1978-04-11|Lionel Morales Montalvo|Rotary engine with pistons and lenticular valves|

---

US3899875A|1974-01-16|1975-08-19|Robert A Oklejas|Gas regeneration tesla-type turbine|

---

JPS50102711A|1974-01-25|1975-08-14|

---

DE2405557A1|1974-02-06|1975-08-07|Volkswagenwerk Ag|ROTATING PISTON INTERNAL ENGINE|

---

US3872839A|1974-03-28|1975-03-25|Charles R Russell|Rotary piston engine|

---

US4059068A|1974-06-10|1977-11-22|Rhone-Poulenc-Textile|Apparatus for treating filamentary products|

---

DE2438410A1|1974-08-09|1976-02-19|Ind Empresa De Const|Rotary IC engine - has lens shaped main piston with smaller lens shaped auxiliary pistons|

---

US3921596A|1974-09-11|1975-11-25|John E Schulz|Concentric rotary engine|

---

US4178900A|1975-11-19|1979-12-18|Larson Dallas J|Rotary internal combustion engine|

---

JPS5175810A|1974-12-25|1976-06-30|Masafumi Osada| 4 setsuperitokoroidokotenkaitenpisutonkikan|

---

JPS5318648B2|1975-05-28|1978-06-16|

---

US3998049A|1975-09-30|1976-12-21|G & K Development Co., Inc.|Steam generating apparatus|

---

US4047856A|1976-03-18|1977-09-13|Hoffman Ralph M|Rotary steam engine|

---

US4083446A|1977-04-25|1978-04-11|Schuchman Sr Frederick E|Combination card holder and decorative element|

---

US4187062A|1978-07-17|1980-02-05|Traut Earl W|Bypass rotary gas expansion motor|

---

US4297090A|1979-10-29|1981-10-27|Trochoid Power Corporation|Rotary expansion power unit with valve disc connected to crankshaft|

---

JPS5698501A|1980-01-05|1981-08-08|Kaoru Ohashi|Double cylindrical rotary engine|

---

JPS634056B2|1980-02-15|1988-01-27|Sumitomo Heavy Industries|

---

GB2072750B|1980-03-28|1983-10-26|Miles M A P|Rotary positive-displacement fluidmachines|

---

US4381745A|1980-04-10|1983-05-03|Firey Joseph C|Porous burner diesel engine|

---

US4446829A|1981-01-07|1984-05-08|Yeager Zema O|Rotary internal combustion engine|

---

US4401070A|1981-03-31|1983-08-30|Mccann James L|Rotary engine|

---

SE445064B|1981-06-24|1986-05-26|Peter James Griffin|MOVEMENT CONVERSION DEVICE AND ROTATION MECHANISM|

---

US4712516A|1982-03-15|1987-12-15|Hale Fire Pump Company|Fuel supply for a rotary piston engine|

---

JPS5979002A|1982-10-27|1984-05-08|Akira Suzuki|Pendulum type power device|

---

CN85203161U|1985-08-02|1986-04-30|梁之桓|Four-stroke epitrochoidal engine with exhaust nozzle|

---

JPS62276201A|1986-05-22|1987-12-01|Mazda Motor Corp|Lube feeder for rotary piston engine|

---

CN86207054U|1986-09-11|1987-05-13|裘伟江|End sealing mechanism for rotary piston compressor|

---

NL8602404A|1986-09-23|1988-04-18|Veg Gasinstituut Nv|PROCESS FOR PERFORMING A GAS COMBUSTION PROCESS, RECOVERING A PART OF HEAT PRESENT IN COMBUSTION GASES.|

---

US4778362A|1986-12-29|1988-10-18|Compression Technologies, Inc.|Outer envelope trochoidal rotary device having a two piece rotor assembly|

---

DE3705313A1|1987-02-19|1987-10-08|Franz Josef Knott|Oscillating piston engine|

---

US4817567A|1987-12-30|1989-04-04|Wilks Ronald C|Rotary piston engine|

---

US4898522A|1988-04-07|1990-02-06|Teledyne Industries, Inc.|System for cooling the rotary engine rotor|

---

GB8813088D0|1988-06-03|1988-07-06|Bell A|Liquid piston i c engine|

---

KR900003511A|1988-08-29|1990-03-26|양기와|Rotary piston engine|

---

BE1002364A4|1988-12-30|1991-01-15|Schmitz Gerhard|TWO - STAGE INTERNAL COMBUSTION ENGINE.|

---

US5127369A|1991-05-21|1992-07-07|Goldshtik Mikhail A|Engine employing rotating liquid as a piston|

---

CN1072239A|1991-11-04|1993-05-19|王长顺|Synchronous birotor combination engine|

---

DE4140316A1|1991-12-06|1993-06-09|Peter 5780 Bestwig De Nagel|Rotary piston engine - has rotating piston with single lobe profile and valves with sliders at pre and post ignition stages|

---

JPH05175810A|1991-12-20|1993-07-13|Nec Corp|Reset device|

---

EP0560709A3|1992-03-05|1993-12-08|Rene Linder|Rotary piston machine|

---

JP3030480B2|1992-06-18|2000-04-10|本州化学工業株式会社|Novel polyphenol and method for producing high purity product thereof|

---

US5228414A|1992-09-10|1993-07-20|Robert D. Hall|Valveless two-stroke-cycle oscillating engine|

---

AU5127493A|1992-09-18|1994-04-12|Klein Bicycle Corporation|A high efficiency bicycle suspension|

---

RU2078221C1|1993-02-02|1997-04-27|Валерий Борисович Веселовский|Rotor|

---

JPH06323159A|1993-05-10|1994-11-22|Yoshiaki Yonekawa|Reciprocating engine|

---

US5501162A|1993-07-19|1996-03-26|Kravets; Alexander|Method of fuel combustion|

---

CN1045119C|1993-09-16|1999-09-15|枢轴转动工程技术有限公司|Internal combustion engine|

---

DE4432688C2|1993-09-24|1995-08-24|Josef Schmidt|Rotary piston engine|

---

US5433179A|1993-12-02|1995-07-18|Wittry; David B.|Rotary engine with variable compression ratio|

---

IT1272806B|1994-09-13|1997-06-30|Pomezia Srl|"CRANK SYSTEM FOR THE TRANSFORMATION OF THE ALTERNATE RECTILINEAR MOTOR INTO A ROTARY MOTOR, IN PARTICULAR SUITABLE FOR ALTERNATIVE ENDOTHERMAL MOTORS".|

---

NL9401729A|1994-10-19|1996-06-03|Lambertus Hendrik De Gooijer|Combustion engine.|

---

US5595059A|1995-03-02|1997-01-21|Westingthouse Electric Corporation|Combined cycle power plant with thermochemical recuperation and flue gas recirculation|

---

DK0839266T3|1995-07-18|2003-09-08|Revolution Engine Technologies|Combustion engine with opposing pistons|

---

US5623894A|1995-11-14|1997-04-29|Caterpillar Inc.|Dual compression and dual expansion engine|

---

US5799636A|1996-03-16|1998-09-01|Fish; Robert D.|Split cycle engines|

---

FR2748776B1|1996-04-15|1998-07-31|Negre Guy|METHOD OF CYCLIC INTERNAL COMBUSTION ENGINE WITH INDEPENDENT COMBUSTION CHAMBER WITH CONSTANT VOLUME|

---

US5755197A|1996-04-26|1998-05-26|Oplt; Frank G.|Rotary engine|

---

JP3763166B2|1996-07-10|2006-04-05|株式会社デンソー|Reduction gear|

---

GR1002755B|1996-09-06|1997-08-27|Μελετης Γεωργιου Ελευθεριος|Rotary piston engine with internal fuel preheating|

---

US5865608A|1997-04-21|1999-02-02|Goodman; William A.|Air flow system for circular rotary type engines|

---

JP3912556B2|1997-06-27|2007-05-09|東洋紡績株式会社|Fine void-containing polyester film|

---

FR2769949B1|1997-10-17|1999-12-24|Guy Negre|METHOD FOR CONTROLLING THE MOVEMENT OF A MACHINE PISTON, DEVICE FOR IMPLEMENTING AND BALANCING THE DEVICE|

---

US5950579A|1998-01-05|1999-09-14|Ott; Vern D.|Internal combustion engine|

---

DE19812853A1|1998-03-21|1999-09-23|Ernst Juraschka|Epi- and hyop-cycloidic rotary piston machine for pump, compressor, gas or steam engine|

---

US5961302A|1998-04-22|1999-10-05|Isocomp Ltd.|Liquid-sealed vane oscillator|

---

JP2000034969A|1998-07-15|2000-02-02|Ngk Spark Plug Co Ltd|Combustion state detecting device using spark plug|

---

JP2003517526A|1998-08-13|2003-05-27|ユナイテッドステイツエンバイロメンタルプロテクションエージェンシー|Dual-cylinder expander engine and combustion method having one cycle and two expansion strokes|

---

AU4933899A|1998-09-04|2000-03-27|Tadashi Yoshida|Adiabatic internal combustion engine|

---

WO2000022286A1|1998-10-15|2000-04-20|Jesus Vazquez|Rotary piston engine, pump and motor|

---

JP2000130101A|1998-10-29|2000-05-09|Nikko:Kk|Four-stroke internal combustion engine|

---

US6230671B1|1998-11-02|2001-05-15|Raymond C. Achterberg|Variable compression and asymmetrical stroke internal combustion engine|

---

US6058901A|1998-11-03|2000-05-09|Ford Global Technologies, Inc.|Offset crankshaft engine|

---

US6112522A|1998-11-10|2000-09-05|Wright; Harlow|Total flow liquid piston engine|

---

US6955153B1|1999-05-13|2005-10-18|Gyroton Corporation|Asymmetric compete expansion rotary engine cycle|

---

IT1314514B1|2000-03-24|2002-12-18|Cefla Coop|DEVICE FOR CLEANING A CONVEYOR BELT SENT ON ROLLERS, FLUID SUBSTANCES SPRAYED ON ITSELF.|

---

SE521262C2|2000-06-28|2003-10-14|Volvo Lastvagnar Ab|Combustion engine with exhaust gas recirculation|

---

US6575719B2|2000-07-27|2003-06-10|David B. Manner|Planetary rotary machine using apertures, volutes and continuous carbon fiber reinforced peek seals|

---

US6318309B1|2000-11-30|2001-11-20|Southwest Research Institute|Opposed piston engine with reserve power capacity|

---

US6668769B1|2001-06-11|2003-12-30|Henry P. Palazzolo|Two stroke hybrid engine|

---

US6722127B2|2001-07-20|2004-04-20|Carmelo J. Scuderi|Split four stroke engine|

---

US6543225B2|2001-07-20|2003-04-08|Scuderi Group Llc|Split four stroke cycle internal combustion engine|

---

US6752104B2|2001-12-11|2004-06-22|Caterpillar Inc|Simultaneous dual mode combustion engine operating on spark ignition and homogenous charge compression ignition|

---

KR100995231B1|2002-02-28|2010-11-17|니콜라이 시콜닉|Liquid Piston Internal Combustion Power System|

---

JP2003314205A|2002-04-24|2003-11-06|Ishikawajima Harima Heavy Ind Co Ltd|Structure of preventing tubing blade from coming off turbine disk|

---

US6772728B2|2002-07-10|2004-08-10|Osama Al-Hawaj|Supercharged radial vane rotary device|

---

FR2844312B1|2002-09-05|2006-04-28|Centre Nat Rech Scient|ROTATING MACHINE WITH CAPSULISM|

---

GB2402974A|2003-06-17|2004-12-22|Richard See|Rotary device in which rotor has sectors of different radii|

---

US7117839B2|2003-06-20|2006-10-10|Abraham H. Horstin|Multi-stage modular rotary internal combustion engine|

---

US8365698B2|2004-01-12|2013-02-05|Liquidpiston, Inc.|Hybrid cycle combustion engine and methods|

---

IL170165A|2005-08-08|2010-12-30|Haim Rom|Wankel and similar rotary engines|

---

US8033265B2|2005-12-16|2011-10-11|Reisser Heinz-Gustav A|Rotary piston internal combustion engine|

---

JP2007239727A|2006-03-06|2007-09-20|Sumiyuki Nagata|Four-cycle rotary engine|

---

BRPI0621488A2|2006-05-09|2013-02-13|Okamura Yugen Kaisha|rotary piston internal combustion engine|

---

CN101506472B|2006-08-02|2012-12-12|流体活塞有限公司|Hybrid cycle rotary engine|

---

US8037862B1|2007-06-03|2011-10-18|Jacobs Richard L|Simplified multifunction component rotary engine|

---

JP4433043B2|2007-12-05|2010-03-17|株式会社デンソー|Fuel supply device|

---

GB2457456A|2008-02-13|2009-08-19|David Walker Garside|A Rotary Piston Internal Combustion Engine Cooling Arrangement|

---

WO2010017199A2|2008-08-04|2010-02-11|Liquidpiston, Inc.|Isochoric heat addition engines and methods|

---

JP5196163B2|2008-11-14|2013-05-15|日立工機株式会社|Engine tools|

---

WO2011130285A2|2010-04-12|2011-10-20|Liquidpiston, Inc.|Internal combustion engine and components therefor|

---

US8087242B2|2010-04-27|2012-01-03|Hanson Goodwin F|Stirling cycle epitrochoidal heat engine|

---

KR102039448B1|2011-03-29|2019-11-01|리퀴드피스톤 인크.|Cycloid rotor engine|

---

AU2012283747B2|2011-07-08|2015-09-24|Greystone Technologies Pty Ltd|Rotary fluid machine|

---

SG11201700480XA|2013-01-25|2017-02-27|Liquidpiston Inc|Air-cooled rotary engine|US8365698B2|2004-01-12|2013-02-05|Liquidpiston, Inc.|Hybrid cycle combustion engine and methods|

---

CN101506472B|2006-08-02|2012-12-12|流体活塞有限公司|Hybrid cycle rotary engine|

---

WO2010017199A2|2008-08-04|2010-02-11|Liquidpiston, Inc.|Isochoric heat addition engines and methods|

---

MX2010002024A|2010-02-22|2011-08-30|Amc Medicion Y Control S A De C V|Electrical energy microgenerator with magnetic coupling.|

---

KR102039448B1|2011-03-29|2019-11-01|리퀴드피스톤 인크.|Cycloid rotor engine|

---

KR20140138270A|2012-03-14|2014-12-03|루메니엄 엘엘시|Idar-ace inverse displacement asymmetric rotating alternative core engine|

---

SK6803Y1|2013-01-06|2014-06-03|Kujovic Jozef|Workspace with rotary moving piston|

---

SG11201700480XA|2013-01-25|2017-02-27|Liquidpiston Inc|Air-cooled rotary engine|

---

DE102013002311A1|2013-02-07|2014-05-08|Brands & Products IPR-Holding GmbH & Co.KG|RB rotary engine|

---

US10087758B2|2013-06-05|2018-10-02|Rotoliptic Technologies Incorporated|Rotary machine|

---

JP6784688B2|2015-03-10|2020-11-11|リキッドピストン， インコーポレイテッド|High power density and efficiency epitrochoidal rotating engine|

---

KR101813925B1|2015-12-23|2018-01-02|엘지전자 주식회사|Rotary engine|

---

CN108779672B|2016-02-14|2020-12-25|北京艾派可科技有限公司|Compressed air energy power system and power method|

---

KR101866558B1|2016-04-25|2018-06-11|인하대학교 산학협력단|Six Cycle Rotary Engine|

---

KR101886867B1|2016-06-20|2018-08-09|인하대학교 산학협력단|Twin Rotary Engine|

---

KR101944024B1|2016-07-27|2019-01-31|인하대학교 산학협력단|Mini-CHP System using Six Stroke Rotary Engine|

---

US10429817B2|2016-12-19|2019-10-01|Honeywell International Inc.|Voice control of components of a facility|

---

US10815877B2|2017-01-18|2020-10-27|Pratt & Whitney Canada Corp.|Method of operating a rotary engine|

---

WO2018184035A1|2017-03-27|2018-10-04|Chi Dien NGUYEN|Two-stroke cycle rotary internal combustion engine|

---

KR102331644B1|2017-04-04|2021-11-30|엘지전자 주식회사|Rotary engine|

---

KR20180120526A|2017-04-27|2018-11-06|엘지전자 주식회사|Rotary engine|

---

KR102282775B1|2017-05-22|2021-07-28|엘지전자 주식회사|Rotary engine|

---

US10994840B1|2017-08-16|2021-05-04|United States Of America As Represented By The Secretary Of The Air Force|Thrust vectoring control of a cyclorotor|

---

CN109751120A|2017-11-01|2019-05-14|王为民|The chamber structure and cycloid rotor engine of cycloid rotor engine|

---

KR102004081B1|2018-01-08|2019-07-25|엘지전자 주식회사|Rotary engine|

---

US10907531B1|2018-07-24|2021-02-02|Rotary Research Group LLC|Heavy fuel rotary engine with compression ignition|

---

WO2020051692A1|2018-09-11|2020-03-19|Rotoliptic Technologies Incorporated|Sealing in helical trochoidal rotary machines|

---

CN111140344A|2018-11-05|2020-05-12|谭波|Rotor engine|

---

US10770996B1|2019-05-21|2020-09-08|General Electric Company|System for anticipating load changes|

---

US11268476B2|2019-05-21|2022-03-08|General Electric Company|Energy conversion apparatus|

---

CN110242407B|2019-06-28|2021-06-25|中国航发南方工业有限公司|Four-petal plum blossom-shaped rotor engine and unmanned aerial vehicle|

---

KR102201762B1|2019-07-03|2021-01-12|엘지전자 주식회사|cycloid type rotary engine|

---

WO2021126766A1|2019-12-17|2021-06-24|Cummins Inc.|Flexible crescent for low pressure fuel pump|

---

RU199412U1|2020-04-13|2020-08-31|Николай Сергеевич Лапшин|ROTARY FOUR-STROKE INTERNAL COMBUSTION ENGINE "ROLAN"|

---

CN111594311B|2020-04-22|2021-05-11|北京航空航天大学|High-sealing quasi-elliptical rotor engine|

---

CN112594057A|2020-12-10|2021-04-02|江苏方霖动力科技有限公司|Triangular rotor engine movement mechanism|

---

CN113006934A|2021-03-12|2021-06-22|北京工业大学|Ignition type diesel rotor machine and control method thereof|

法律状态:
2019-08-27| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

---

2020-01-07| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

---

2021-05-04| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

---

2021-06-22| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 29/03/2012, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

---

申请号 | 申请日 | 专利标题

---

US201161469009P| true| 2011-03-29|2011-03-29|

---

US61/469,009|2011-03-29|

---

PCT/US2012/031324|WO2012135556A2|2011-03-29|2012-03-29|Cycloid rotor engine|

---