JP2007537395A - Rotary engine - Google Patents

Abstract

A first rotor that can rotate about a first axis and that has at least one recess bounded by a curved surface in the periphery; a stator that is disposed around the first rotor to rotate; A second rotor having at least one radial lobe bounded by a curved surface and capable of rotating counter to the first rotor around a second axis parallel to the axis; First and second rotors coupled to rotate in unison to produce a temporary chamber in which the volume defined between the curved recess of the second rotor and the lobe surface increases or decreases in stages; A housing in which the rotor is enclosed, the housing having an end surface joined to the end surface of the internally engaging rotor; so that gas can flow into or out of at least one recess in the concave rotor It is further provided with arranged rotor ports, and a plurality of ports Have dimensions, at least one of the dimensions, long rotary device than a distance between the minimum radius of the concave portion of the outermost limits and the recessed rotor stator.

Description

  The present invention relates to a rotary device for expanding and / or compressing a gaseous fluid and to an engine including, for example, a rotary device. The term gaseous fluid means a compressible fluid containing a mixture of fuel and air inside an internal combustion engine.

  In WO-A-91 / 06747, US 6,168,385B, US 6,176,695B, a rotary device for expanding and / or compressing a gaseous fluid is disclosed. This rotary device is provided with a first rotor and a second rotor that are reversely rotated and coupled to mesh with each other, and a part of the rotation of the rotor is between the first rotor and the second rotor. In addition, a temporary chamber is defined in which the capacity increases and decreases stepwise as the rotor rotates. The valved port allows a compressed gaseous fluid flow.

  The rotary device has two main forms. The first form is an internal combustion engine equipped with separate rotary compression sections and expansion sections, and the second form is a gas compressor. In the first configuration, the internal combustion chamber includes a valved inlet port and an outlet port that communicate with the compression chamber and the expansion chamber, respectively. Each of these sections can be rotated around the first axis and has a first rotor provided with a concave portion delimited by a curved surface around the first axis; around the second axis parallel to the first axis, the first rotor And a second rotor provided with a radial lobe delimited by a curved surface, and these rotors mesh with each other during rotation.

  Between these rotors, a temporary chamber is defined in which the capacity increases in stages (expansion section) or decreases (compression section). The rotor can rotate at a relative speed ratio, preferably a ratio of 2: 3, and has a contour, so that the concave surface is along the lobe tip and the lobe surface while the lobe passes through the recess. Are swept continuously by both a moving location on the lobe moving forward to define a temporary chamber.

The second form relates to a fluid compressor. In this fluid compressor, a pair of rotors function to compress compressible fluid and transport it into the receiver. The receptor pressure within the receptor is substantially greater than the fluid source pressure. Power is supplied by an external prime mover to drive a pair of rotors to compress the fluid and raise its pressure from the source pressure to the receiver pressure.
WO-A-91 / 06747 US 6,168,385B US 6,176,695B

  In both forms of these prior art devices, rotor interaction occurs between a pair of closed mating sidewalls. One of these sidewalls is equipped with a port for carrying a fluid load to or from the rotor, depending on whether it is performing load compression or expansion. By providing a mechanical or liquid seal between the rotor / rotor elements and between the rotor / stator elements, gas leakage during operation of these machines is reduced or substantially eliminated. However, due to the nature of the interaction between the rotors, it is difficult to ensure that such seals are kept in place and operate effectively over the useful life. In any case, the use of such a seal is accompanied by considerable drawbacks caused by the mechanical friction caused thereby.

  In a fluid compressor, multiple pairs of rotors function to compress a compressible fluid and deliver it into a receiver, where the receiver pressure is significantly higher than the pressure of the fluid source. Power is supplied by the external prime mover to drive a pair of rotors, compressing the fluid and raising its pressure from the source pressure to the receiver pressure. For efficient operation of a positive displacement compressor, it is desirable to increase the pressure of the fluid load to a level equal to the pressure of the receiver prior to initiating delivery of the load into the receiver. In the rotor system disclosed in WO-A-91 / 06747, a port that communicates with the conveyance path of the concave rotor is provided on the side wall when the conveyance path passes over the port.

  This arrangement provides a desirable means of controlling the timing of the start of transport through the port, but this limits the maximum size of the port that can be provided. This is because the range that can be used for communication located near the end face of the concave rotor needs to be provided in the rotor with a radius smaller than the minimum radius reached by the concave portion of the rotor. This limits the range available for the port due to its location away from the center of the recessed rotor, without a lobe sweep. It is desirable that the operating speed of the compressor is not unduly limited by the flow capacity regulated at the port. Therefore, it is desirable to provide a means for arranging both ports and their communication.

  In a rotary internal combustion engine equipped with a rotor system as disclosed in WO-A-91 / 06747, the rotor functions as a positive displacement and negative displacement system, so that the capacity in the working fluid throughout the engine's thermodynamic cycle Changes. In such an internal combustion engine, it is desirable that the operating speed of the engine is not unduly restricted by the flow capacity regulated by the combustion chamber port communicating with each of the compressor temporary chamber and the expander temporary chamber. Therefore, it is desirable to provide means for improving the flow capacity of both combustion chamber ports and communicating means for communicating with the temporary and expansion chambers for each.

  According to a first aspect of the present invention, a rotary device is obtained, the rotary device comprising: a first rotor capable of rotating around a first axis and having at least one recess at the periphery delimited by a curved surface; A stator disposed around the first rotor for rotation, the stator having a sufficiently large radius to define a passage for gas flow; a first parallel to the first axis; A second rotor having at least one radial lobe bounded by a curved surface and capable of rotating in opposite directions around the two axes; the first rotor and the second rotation; First and second rotors coupled to rotate in unison to produce a temporary chamber in which the volume defined between the curved recess and the lobe surface of the child increases or decreases in stages; A housing in which a child is enclosed, The ring has an end face joined to the end face of the internal engagement rotor; further comprising a rotor port communicating with the at least one recess in the concave rotor, the port having a plurality of dimensions; At least one of the dimensions is longer than the distance between the outermost limit of the stator and the minimum radius of the recess in the concave rotor.

  Preferably, each of the first and second rotors has an end face spaced along a corresponding axis, and the rotor port is provided inside one of the end faces, and the housing The end face of the rotor has at least one associated port for communicating with the at least one rotor port, the concave rotor port and the housing port being in rotation of the rotor, Barbing is performed by movement of a joint end surface of the concave rotor and housing; the concave rotor includes a valve portion defining the at least one port of the concave rotor and a main portion defining the at least one recess. The valve portion and the main portion are arranged side by side along the axis of the concave rotor, and the at least one port on the concave rotor. And each of the at least one port on the housing extends radially outward from the axis of the concave rotor at least a distance beyond the innermost limit of the recess in the concave rotor. .

  The stator is preferably a stator cylinder with a port. At least one recess is provided with an associated rotor port, and when the rotor rotates relative to the stator cylinder, the port on the stator cylinder and the port on the rotor are periodically aligned; Also, the recess is valved by the interaction between the stator cylinder and the inner cylindrical surface of the first rotor that is rotatably and slidably engaged with the stator cylinder.

  According to a second aspect of the present invention, a rotary device is obtained, the rotary device comprising: a first rotor that can rotate around a first axis and has at least one recess at the periphery delimited by a curved surface; A second rotor having at least one radial lobe that is capable of rotating in a direction opposite to the first rotor around a second axis parallel to the first axis and bounded by a curved surface; First and second coupled to rotate in unison to produce a temporary chamber in which the volume defined between the curved recess and the lobe surface of the first and second rotors increases or decreases in stages. A rotor; and a housing in which the rotor is enclosed, the housing having an end surface joined to an end surface of the internal engagement rotor; and the first shaft includes a hollow cylindrical member The hollow cylindrical member corresponds to the first time. Mounted in a hollow cylindrical bore dimensioned within the child and having a port disposed thereon, through which the communication between the inside and outside of the stator cylinder is possible; A recess in the stator has at least one port that allows communication between the central bore in the rotor and the recess, the port on the first shaft, and the port on the rotor Each is configured such that the ports can be periodically aligned as the rotor rotates relative to the first axis.

  According to a third aspect of the present invention, a rotary device is obtained, the rotary device comprising: a first rotor capable of rotating around a first axis and having at least one recess surrounding the curved surface. The first rotor has an end surface spaced along its axis; a curved surface capable of rotating in a direction opposite to the first rotor around a second axis parallel to the first axis; A second rotor having at least one radial lobe bounded by the second rotor, the second rotor having end faces spaced along its axis; the first rotor and the second rotor First and second rotors coupled to rotate in unison to produce a temporary chamber in which the volume defined between the curved recess and the lobe surface is increased or decreased in stages; An encapsulated housing, the housing comprising the interior An end face joined to an end face of the combined rotor; one of the end faces of the first concave rotor has at least one port communicating with at least one recess of the rotor; One of the end faces has at least one port associated therewith for communicating with the at least one rotor port, the port of the concave rotor and the port of the housing being connected to the rotation of the rotor. In which the concave rotor and the housing are valved by movement of a joint end face; the concave rotor defining a valve portion defining the at least one port of the concave rotor and the at least one recess. A main portion, the valve portion and the main portion being arranged along an axis of the concave rotor, wherein the at least one on the concave rotor And each of the at least one port on the housing extends radially outward from the axis of the concave rotor at least a distance beyond the innermost limit of the recess in the concave rotor. ing.

  The at least one rotor port and the at least one port on the housing are each positioned so as to be disposed only at the radially outermost position of the innermost limit of the recess in the concave rotor. It is much more preferable.

  In a convenient form of construction of the device according to the invention, the valve part of the concave rotor comprises an end wall extending perpendicular to the axis of the concave rotor, and at the closed part of one end of the rotor recess. Has been placed. The other end of the rotor recess is closed by a further end wall of the housing. Conveniently, the at least one rotor port is a port through the first end wall of the concave rotor. Conveniently, the valve portion comprises a disc that is perpendicular to and coaxial with the first axis and rotates with the main portion of the first concave rotor. Has been placed.

  The curved surface is continuously swept by both the tip of the lobe and a movable location on the lobe that advances along the lobe surface while the lobe passes through the recess; Thus, it is particularly preferable to have a contour that defines the temporary chamber.

  The rotor can be uniformly arranged in the axial direction with the recess and the lobe extending uniformly in the axial direction, and each of the at least one recess and the at least one lobe is spiral in the axial direction. It is much more preferable that it extends.

  The rotational speed of the first concave rotor is preferably slower than the rotational speed of the second lobe rotor of the device and less than 1: 1 of the total number.

  Further, each of the first and second rotors has recesses that are equiangularly spaced, and further, as a speed ratio of the rotor with lobes with respect to the concave rotor, the number of recesses with respect to the number of lobes It is preferred to have the same ratio of lobes. In some arrangements, the first rotor comprises three isometrically arranged recesses, the second rotor comprises two diametrically opposed lobes, and the rotational speed ratio is 2: 3. . In some arrangements, two or more of the second lobe rotors can be arranged to interdigitate with the same first concave rotor.

  The rotor is enclosed within a housing, the housing having first and second arcuate recesses that are coaxial with the first and second rotors and form a sliding seal therewith, thereby providing the lobe. For a portion of the rotation before and / or after passing through the recess in the first rotor, an additional temporary chamber is defined between the rotor and the housing to increase or decrease the capacity in stages. Thus, it is preferable that communication with the temporary chamber between the rotors is performed.

  The embodiment of the present invention can be simply constituted by a rotary device that compresses a gas fluid or a rotary device that receives a compressed gas fluid that rotationally drives the rotary device. It should be understood that a particular application in an internal combustion engine composed of a compression section and a rotary expansion section can be obtained. Such an arrangement comprises a separate rotary compression section and expansion section, and a combustion chamber with an inlet port and an outlet port communicating with each of the compression section and expansion section, each of the compression section and expansion section being a preceding paragraph. An internal combustion engine which is a rotary device according to any of the forms described in (1) is obtained.

  According to a fourth aspect of the present invention, an internal combustion engine is obtained, the internal combustion engine comprising separate rotary compression sections and expansion sections, and a combustion chamber having an inlet port and an outlet port communicating with each of them. Each of the compression section and the expansion section is the rotary device described in any one of the first to third aspects of the present invention.

    Embodiments of the present invention will now be described by way of example with reference to the accompanying drawings.

  Referring to FIG. 1, an internal combustion engine embodying the present invention comprises a pair of outer walls 1, 2 and a parallel intermediate wall 3, all of which are fixed to form an established assembly. . In order to accommodate the parallel shafts 10 and 11, a roller bearing 8 is provided inside each of the outer walls 1 and 2, and a ball bearing 9 is provided inside the intermediate wall 3.

  A key gear pinion 12 is provided at one end of the shaft 10, and a key pinion 13 is provided at the end on the same side of the shaft 11. The two pinions are engaged with each other, and the speed of the pinion 13 and the pinion 12 is determined. The ratio is 2: 3.

  Each of the shafts 10, 11 is provided with a respective key compression rotor 14a, 14b (further shown in FIGS. 2a-2c) and a key expansion rotor 15a, 15b (further shown in FIGS. 3a, 3c). . Each rotor has a plurality of end faces spaced along its axis, and each rotor forms a substantially airtight sliding fit between wall 1 and wall 3 and wall 2 and wall 3. is doing. A housing 25 (shown in FIGS. 1b, 7 and 8 and further described below) is arranged around the assembly so that an intake chamber is provided around the compression rotor and around the expansion rotor. Is provided with an exhaust chamber. An internal combustion chamber 16 is provided inside the intermediate wall 3 and communicates with both end surfaces inside the intermediate wall 3. The shape of the internal combustion chamber 16 will be described in more detail below with reference to FIG. As shown in FIGS. 2a, 2b, and 2c, the outer edge of the first compression rotor 14b is formed with three recesses R, S, and T, each of which is bounded by a curved surface. The compression rotor 14a is provided with two radial lobes P and Q that are bounded by curved surfaces. As shown in FIGS. 3a, 3b, and 3c, the outer edge of the first expansion rotor 15b is provided with three recesses W, X, and Y that are delimited by curved surfaces, and the second expansion rotation. The child 15a is provided with two radial lobes delimited by curved surfaces.

  As described in detail below with particular reference to FIGS. 9a-9f, each of the compression rotor 14b and expansion rotor 15b includes a corresponding recess and a port in communication with the combustion chamber. However, first, the entire structure will be described with reference to FIGS. 1, 1a, 4a, 4b, 5, and 6. FIG. In the schematic diagrams of FIGS. 5 and 6, the rotor and a representative portion of the stationary wall 3 are shown in a thinly cut form.

  First, considering the compression section, the concave rotor 14b includes a main portion 19a defining a concave portion, and a disc-shaped valve-shaped portion that is coaxial with the main portion 19a and fixedly attached thereto. 19 is provided. The disk 19 closes a part of one end of each rotor recess, and the other end of each rotor recess is closed by the end wall 1.

  The disk 19 includes three ports 20 for providing communication between each recess of the rotor 14 b and the combustion chamber 16 when the rotor port 20 overlaps the inlet port 21 of the combustion chamber 16. Therefore, the capacity and timing of communication between the recess of the rotor 14 b and the combustion chamber 16 are determined by the size, shape, and location of the port 20 in the disk 19.

  A similar arrangement is used in the extended rotors of FIGS. 15b and 15a. A corresponding disk 19b is fixedly attached to the main portion 19a of the rotor 15b, and this disk 19b is used for passing the expanding combustion gas from the combustion chamber 16 into the recess of the expansion rotor 15b. Three compression ports (not shown in FIG. 1) are included. This will be described in detail later.

  The thickness (in the axial direction) of the disk 19 forming the valve portion of the concave rotor 14b is limited to the minimum necessary for structural support, but this thickness is the axial length of the first rotor 14b. Will be an additional length to. Each member of the pair of rotors (14 b, 14 a) has the same length and is separated from the disk 19. As a result, lobe interaction occurs in the smallest gap between the end surface of the lobe and the inner surface of the disk as it passes through the recess. Since the circular recess is provided in the engine wall 3, the disc 19 can be fitted into the circular recess leaving only a narrow gap between the disc 19 and the port 21. This also allows a narrow gap to be maintained between the end face of the lobe rotor 14a and the wall 3 of the device. For this reason, temporary chambers are formed by the limited clearance between the rotor / rotor components and between the rotor / stator components throughout the rotor-port component interaction that occurs during each operating cycle of the device. And leakage from the combustion chamber 16 can be controlled.

  Arrangement provided with a disk 19 with a port for allowing gas flow into or out of the temporary chamber defined between the recesses and lobes of the rotor pair 14a, 14b as described above. It will be appreciated that any desired sized port can be provided as long as it is defined in the disk 19. The port may have a dimension that at least one is longer than the distance between the central axis of the recessed rotor and the minimum radius of the recessed section in the recessed rotor. In other words, the port can be provided or provided with at least one dimension longer than the radius dimension of the largest port, which can be located within the smallest radius of the recess of a given rotor dimension.

  This is in contrast to the ports provided in the conventional rotary device described in WO-A-91 / 06747. Thus, the port arrangement provided in the example embodiments of the present invention can achieve improved and / or increased gas flow into or out of the temporary room, thereby increasing the rotational speed of the rotary device. Can be achieved.

  Before describing the valve in detail, a general description of the engine operating cycle is given, which is the same as the prior art disclosed in WO-A-91 / 06747. First, the compression rotors 14a and 14b and the compression stage will be described with reference to FIGS. 2a, 2b and 2c. In FIG. 2a, the lobe rotor 14a is a high speed rotor and the recessed rotor 14b is a slow speed rotor. These rotors together constitute a rotary device that realizes the present invention. The rotor 14a is provided with radial lobes “P” and “Q”, and these protrusions have the same shape and engage with the recesses “R”, “S”, “T” of the rotor 14b. It has a shape determined by the computer to work together. In the housing surrounding the rotor 14b, a gaseous working fluid, for example a fuel / air mixture or only air during use of the fuel injection system, is provided and its recesses “R”, “S”, “T ". The compression cycle of the rotor recess starts when the two rotors 14a, 14b are in the position shown in FIG. 2a. At this position, the load of the working fluid is captured between the rotors and between the clearance of the tip portion 17 of the rotor 14 a and the clearance of the heel portion 18 in the recess “R”.

  When the rotor begins to advance to the position shown in FIG. 2b, compression of the load within the recess “R” is performed as the capacity captured between the rotors is reduced by the displacement action of the moving rotor. Is done. When the working gas fluid load is compressed, this load is propagated through the rotor port 20 located in the side facing the inner surface 3 of the rotor 14b. During the entire compression phase, this rotor port 20 communicates with the inlet port 21 of the combustion chamber 16 provided in the intermediate wall 3. The compression phase is complete when the capture volume is reduced to the gap volume between each part of the two rotors in the position of FIG. 2c. At this point, the rotor port 20 stops communicating with the stationary inlet port 21 so that the compressed load is captured in the combustion chamber 16.

  An outlet port 22 is provided at the other end of the combustion chamber 16. During the entire combustion phase, the outlet port 22 is closed by the wall of the adjacent expansion rotor 15b. This will be described in more detail later. Thereby, during the combustion phase, the combustion chamber inlet port 21 and outlet port 22 are effectively closed by the adjacent end faces of each rotor 14b, 15b. This method limits the capacity of the compressed gaseous fluid load to a constant during the combustion phase. Assuming that a fuel / air mixture is used, ignition occurs by means of a spark plug 23 whose tip is exposed into the combustion chamber 16 or into the combustion chamber 16. Those skilled in the art of internal combustion engines will appreciate that instead of spark ignition, fuel injection by thermal ignition can be used to provide a compression ignition version of the engine. By releasing heat by the combustion of the fuel, the pressure in the combustion chamber increases significantly.

  Next, the expansion rotor and the expansion stage will be described with reference to FIGS. 3a, 3b, and 3c. In FIG. 3a, the lobe rotor 15a is a high speed rotor and the concave rotor 15b is a slow speed rotor. These rotors also constitute a rotary device that realizes the present invention. The rotor 15a is provided with radial lobes “U” and “V”, and these protrusions have the same shape and are fitted to the recesses “W”, “X”, and “Y” of the rotor 15b. The shape determined by the computer to work together.

  The expansion phase begins when the two rotors are in the position shown in FIG. At this position, the rotor port (not shown) of the concave rotor communicates with the transfer port 22 of the combustion chamber 16. The volume defined between the two rotors 15a, 15b is in communication with the combustion chamber 16 filled with gaseous fluid under very high pressure after combustion. The gaseous fluid under this pressure in the volume defined between the two rotors forces the rotor to rotate and move it to the position of FIG. 3b, and the expansion process continues, so that both rotors A moment of force is applied to keep both rotors rotating in the same direction. These rotors eventually reach the position shown in FIG. 3c. In this position, if the rotor reaches the limit of fluid capture and the rotor continues to rotate further thereafter, the exhaust moves away from the capture zone by successive rotor displacements.

  Next, referring to FIGS. 7 and 8, the housings of the compression section and the expansion section are shown to operate so as to extend the compression period and the expansion period of the engine. The housing 25 is shaped to match a “sliding” (ie, minimal) clearance with the two rotors in part of its rotational motion. FIG. 7 shows the start of capture of volume “J”. This volume “J” continues to decrease with rotation until the volume of the gaseous fluid is reduced to the volume shown between the lobe “P” and the surface boundary recess “R” in FIG. As a result, generally higher compression can be achieved than in the case of a recess provided only in the rotor.

  FIG. 8 shows that the space “so that further work can be extracted from the expansion gas until the exhaust finally escapes from between the rotor lobe and the rotor recess shown in FIG. It is confined within "K", after which the gas is released to other parts of the housing.

  The description so far has been made with reference to only the cross section of each rotor, and this can be applied to a simple cylindrical rotor or a complicated shape. In a preferred arrangement, each is provided with a helically shaped rotor, which is schematically illustrated in the manner illustrated in FIG. 1b in connection with the compression section of the engine of FIG. For the sake of simplicity, the valve disc 19 is omitted in FIG. 1b.

  A housing is provided around the rotors 14b and 14a. Of course, one or both of the end walls 1, 2 may be part of the housing 25. The housing 25 has a shape in which a first arcuate recess 31 is provided. The recess 31 has a shape in which the rear edge 42 of each recess 14b of the first rotor can be slidably fitted to the first arc-shaped recess 31. Furthermore, the housing 25 has a shape in which a second arc-shaped recess 32 is provided. The second arcuate recess has a shape in which the front edge 62 of the lobe of the second rotor 14 a can be slidably fitted to the second arcuate recess 32 of the housing 25.

  The recesses of the first rotor 14 b, the lobe of the second rotor 14, and the arc-shaped recesses 31, 32 of the housing 25 when the recess and the trailing edge 42 and the front edge 62 of the lobe enter the arc-shaped recesses 31, 32, respectively. In the meantime, a temporary room J (shown with shading in FIG. 7) is formed. The working gas fluid is compressed using the temporary chamber J.

  The capacity of the temporary chamber J is such that the rotation of the rotors 14b, 14a starts from the position immediately before the leading edge 62 of the lobe of the second rotor 14a shown in FIG. The rear edge 42 of the child 14b recess decreases as it advances from the position immediately before entering the first arc-shaped recess 31. As can be seen in FIG. 1b, the rotors extend helically parallel to their respective axes. Since the torsion angles of the rotor coincide with the rotation speed, the ratio of the torsion angles is the same as the ratio of the rotation speed of the rotor. For example, the twist angle of the first concave rotor 14b may be 20 °, and the twist angle of the second lobe rotor 14a may be 30 °. The arc-shaped recesses 31 and 32 are spiral so as to coincide with the spiral shape of the concave lobe.

  In the above description, the entire compression cycle and expansion cycle have been referred to without particularly referring to any type of valve. This will now be described in detail with reference to FIGS. 9a-9f, 4a, 4b, 5, and 6. FIG. 4a shows the end face of the valve position 19 of the concave rotor 14b of the embodiment shown in FIG. 1, and FIG. 4b shows a side view of the wall 3 of the housing 25 of the embodiment shown in FIG. FIGS. 9a to 9f show respectively schematic diameter cross sections of the interacting rotors in the compression section of the internal combustion engine according to the invention. These drawings show successive stages during the compression cycle of the internal combustion engine.

  FIG. 9a shows the position immediately after the start of compression. The tip 17 of the lobe P of the second rotor 14a and the rear edge of the recess R of the first rotor 14b form a temporary chamber within the capacity of the proximity mounting housing 25 (not shown in FIG. 9a). The gas load is captured in this temporary room. The lobe P is about to enter the recess R with its end face close to the disk 19. Since the front edge of the hole 20 of the disk 19 has already passed through the opening edge of the port 21 in the end wall, it is in the combustion chamber 16 (not shown in FIG. 9) between the recess R and the port 21. Communication that continues to is established.

  FIG. 9b shows a slightly later position, in which the load is further compressed and the leading edge of the hole 20 further crosses the port 21, thereby increasing the flow range. The amount of compressed load that is conveyed increases.

  FIG. 9 c shows the position where the flow range has reached its maximum when the usable flow range is reduced by the curved end face of the lobe P.

  9d and 9e show the position towards the end of compression, at which position the remaining capacity of the compressed load is small and the remaining flow range is likewise small.

  FIG. 9f shows the position when a little has elapsed after the end of compression, in which the trailing edge of the hole 20 passes through the closing edge of the port 21 and seals the load in the combustion chamber.

  As already mentioned, it is important to understand that embodiments of the present invention can be constructed to be used as simple gas fluid compressors. In such a case, this structure consists only of the compression section of the internal combustion engine shown in the preceding drawings, and the rotor shaft is driven by an external power source. If the device is a compressor, properly position the leading edge of the hole and the approach end of the port in time so that the opening of the port matches the pressure equalization between the temporary chamber and the receiver Can do. Furthermore, another improvement is that the compression of the gaseous material is not due to the additional compression due to the interaction between the lobed rotor and the recessed rotor, or through the enclosure housing as shown in FIG. It can be limited to the interaction between the lobe and the concave part of the concave rotor. Finally, it should be understood that a lobed rotor may include one or more lobes, and similarly, a concave rotor may include one or more recesses.

  In at least a preferred embodiment of the invention, the concave rotor port and the housing sidewall are arranged to extend radially outward beyond the innermost limit of the recess in the rotor, This is particularly advantageous because a very large flow range can be provided over the housing side wall. The already known arrangement described in WO-A-91 / 06747 could only provide a port inside the innermost limit of the concave part of the concave rotor. Such ports must be in a small range and limit the rotational speed of the internal combustion engine employing the present invention. In a typical example, the rotational speed was limited to about 3000 rpm. The present invention is particularly applicable to an internal combustion engine that operates at a relatively high speed such as, for example, 6000 rpm or more, and preferably in the range of 10,000 to 15,000 rpm.

  In both rotary devices disclosed in WO-A-91 / 06747, a temporary chamber and a stationary wall of the device are provided by a chamfered edge or passage in a recessed rotor that communicates with a port fixed in the stationary wall of the device. A means for gas communication was provided between the fixed port and the port. As the concave rotor rotates, communication between the chamfering groove or passage in the rotor and the fixed port in the stationary wall must be implemented within a limited range near the center of the concave rotor. This limited the maximum flow range possible with such communication. It is desirable to provide a larger diameter port so that the flow capacity does not unduly limit the performance of the rotary device. Further, the capacity of the chamfer groove exhibits a significantly large “dead” volume, whereas in the present invention, this “dead” volume is limited to the range of the transport port 20 and the thickness of the disk 19.

  FIG. 10 shows a schematic diagram of a rotor for use in an example alternative embodiment of the present invention. The arrangement of FIG. 10 includes a rotor 40 and a stator cylinder 42 around the rotation axis of the rotor 40. The stator cylinder has a sufficiently large radius to define a passage through which gas flows. Although the rotor 40 and stator cylinder 42 are shown in an exploded view, in use, the stator cylinder 42 is disposed within a central bore 44 in the rotor 40 and the rotor 40 associated with the stator cylinder 42 is shown. It will be understood that the rotation is possible. The center of the stator cylinder 42 is substantially hollow and this central portion defines a passage for functioning as a gas conduit.

  The stator cylinder 42 is provided with a port 46, and the rotor 40 is provided with a port 48. By combining these, depending on whether the device is operating as an expander or a compressor, the passage 47 from the recess of the rotor 40 to the passage in the stator cylinder 42 or the opposite passage 47 is provided. Communication via this is possible. The ports 46, 48 are sized and positioned so that the ports 46, 48 can be aligned for a period of each rotation period of the rotor 40 as the rotor 40 rotates relative to the stator cylinder 42. .

  FIGS. 11-13 show views of the rotor 40 and stator cylinder 42, respectively, on various stages where the rotor 40 rotates relative to the fixed cylinder 42. FIG. Referring to FIG. 11, at this point in the rotation period of the rotor 40 associated with the stator cylinder 42, the port 46 in the stator cylinder 42 cannot be seen. Referring to FIG. 12, when the rotor is fixed and continues to rotate relative to the cylinder 42, the port 46 in the stator cylinder 42 can be seen through the port 48 in the rotor 40.

  When the port 46 becomes visible through the port 48, communication between the stator cylinder 42 and the recess in the rotor 40 is possible.

  Referring now to FIG. 13, because the rotor 40 continues to rotate, a larger proportion of the ports 46 can be seen through the port 48 in the recess of the rotor 40. As the rotor 40 continues to rotate relative to the stator cylinder 42, there will be a point where the cross section of the passage between the recess of the rotor 40 and the interior of the stator cylinder 42 is maximized in the range where the ports 48 and 46 overlap. . As the rotation continues further, the cross section of this overlapping range starts to decrease. In other words, the port 46 is closed by the rotor 40.

  In the example shown in FIGS. 10-13, the dimensions of the ports in the rotor (and on the stator cylinder) achieve sufficient gas flow between the rotor recesses and the interior region of the stator cylinder 42. It will be understood that you can choose what you can. The port extends axially relative to the longitudinal axis of the stator cylinder 42 and the rotor 40. In other words, at least in the axial direction, the port is not restricted by the radial distance between the stator cylinder 42 and the innermost volume of the recess.

  14A to 14H show the shape of the rotor end portion in each stage during one cycle of the rotary device when used as an expander. Referring to FIG. 14A, the period of the expander is such that the lobe surface U and the recessed surface W of the pair of engaged rotors pass through the maximum penetration point of the lobe, that is, the lobe tip is the minimum of the recessed surface W. Starts when passing the radius. At this stage, the leading edge of the recessed rotor passage 47 approaches the opening edge of the port 46 in the stator cylinder 42 through which pressurized fluid supply can flow. Referring to FIG. 14B, when the port 46 is opened, the pressurized fluid flows through the recessed rotor passage 47 and flows into a temporary capacity newly formed between the lobe and the recessed portion.

  Referring to FIG. 14C, at this point, the port 46 is fully open, allowing the maximum flow capacity of pressurized fluid to pass through the temporary volume defined between the lobe surface U and the recess surface W. Yes. This minimizes the difference between the pressure of the fluid supply and the pressure generated within the temporary capacity. The pressure of the pressurized fluid acts on the lobe surface U and the recess surface W to force the rotor to move further in the direction of rotation. In FIG. 14D, the trailing edge of the recessed rotor passageway 47 approaches the closed edge of the port 46, which begins to stop the supply of pressurized fluid to the chamber defined between the lobe and the recessed portion.

  Referring to FIG. 14E, the trailing edge of the recessed rotor passage 47 reaches the closing edge of the port 46, thereby stopping the supply of pressurized fluid and isolating the fluid that has already entered the temporary capacity. As seen in FIG. 14F, the rotation of the rotor increases the isolation capacity, thereby maintaining some pressure on the surfaces of the lobe U and recess W and also connecting the rotor to it. The captured fluid can be expanded while energizing rotation with the shaft.

  Referring to FIG. 14G, the temporary capacity has reached its maximum capacity and the fluid has reached ambient pressure. At this point, the fluid prior to release to the housing surrounding the rotor pair stops applying net pressure to the lobe U and recess W surfaces.

  Finally, in FIG. 14H, fully expanded fluid is released from the temporary capacity to the drainage system under the natural pumping action of the pair of rotors in the housing.

  15A to 15H show the shapes of the rotor end portions in a plurality of stages in one cycle of a rotary device used as a compressor. Each of FIGS. 15A to 15H shows a cross section of the shape of the lobe, the pocket rotor, and the movable contamination wall at a point near the intake end of the rotary device. In the example presented, intake air can be passed by the lobe rotor shaft, which is released into the central region of the compressor plenum via a radially directed passage. The recessed rotor also has a hollow center and rotates around a tight stator cylinder. The stator cylinder is provided with a port 46, and each recess of the pocket rotor is provided with a passage 47 for communicating with each port 46 in the stator cylinder.

  Referring to FIG. 15A, when the rotor rotates in the indicated direction (the lobe-equipped rotor turns clockwise and the recessed rotor rotates counterclockwise), the lobe P and the recessed portion R approach each other. When the lobe P, the recess R, and the movable contamination wall 101 are engaged, the temporary capacity J is captured in the movable wall section 101.

  Referring now to FIG. 15B, here the fluid contained in the temporary volume J is captured and compressed as the rotor continues to rotate.

  Referring now to FIG. 15C, the temporary volume J is substantially compressed, but the fluid is still trapped because the rotor passageway 47 has not yet been rotated to the position associated with the port 46. is there.

  In FIG. 15D, the temporary capacity J is completely enclosed by the surface of the lobe P and the surface of the recess R. Here, the front edge of the concave rotor passage 47 reaches the opening edge of the port 46, and fluid begins to flow into the port. At this stage, the pressure of the trapped fluid reaches the pressure of the receptor, and the rotor further rotates, so that the gas load compressed in the variable volume chamber between the lobe R and the recess P is stepped. To be transported.

  In FIG. 15E, the leading edge of the recessed rotor passage 47 crosses the port 46 approximately half way, thereby increasing the variable flow range at the throat portion of the port 46. In FIG. 15F, since the recessed rotor passage 47 is aligned with the port 46, the maximum flow range for carrying the load is obtained.

  In FIG. 15G, the trailing edge of the recessed rotor passage 47 is close to the closing edge of the port and the closing of the port has begun. Since the temporary capacity other than this is very small, the load that has not yet been conveyed through the port is extremely small.

  Finally, in FIG. 15H, the temporary capacity is eliminated from between the surface of the lobe P and the surface of the recess R, and only the gap capacity remains. The closing of the port 46 and the completion of the compression operation occur simultaneously, which occurs when the lobe tip reaches the minimum radius point of the pocket. At this point, a new temporary capacitance is formed between the next pair of lobes and recesses.

  The dimensions of the port 46 in the stator cylinder and the corresponding port dimensions in the rotor appear to be necessary both when the rotary device functions as an expander and as a compressor. In addition, a sufficient gas flow is selected between the rotor recess and the interior region of the stator cylinder 42. As described above with reference to FIGS. 10-13, the ports extend axially relative to the longitudinal axis of the stator cylinder 42 and the rotor 40. In other words, the port is not limited by the maximum radial distance between the stator cylinder 42 and the minimum radius of the recess, at least in the axial direction.

  FIG. 16 shows a two-dimensional end view of a pair of rotors provided for both radial and axial ports. The illustrated arrangement includes a lobed rotor 14A and a concave rotor 14B. An end plate 19 is disposed on the end face of the concave rotor 14B. As shown in FIGS. 9A to 9F and described with reference to these figures, the end plate 19 includes a number of ports 20. Further, the stator cylinder 42 arranged in the central bore of the concave rotor 14B is provided with a hollow passage having a port 46. A large number of radial passages 47 are provided between the cylindrical inner surface of the bore in the rotor 14B and each recess (indicated by a dotted line in the figure) of the rotor 14B. Usually, the end wall of the housing in which the pair of rotors are arranged in use is not shown. However, it will be understood that such a housing wall is provided with a port 21 as shown in FIG. 4B and described above with reference to FIG. 4B.

  In use, the pair of rotors shown in FIG. 16 defines a variable capacity temporary chamber between the concave curved surface of the concave rotor 14B and the lobe of the lobe rotor 14A. Port 20 (in end plate 19) and port 46 (in shaft 42) provide two separate means. By these means, a gas flow can be supplied to or received from the temporary chamber defined between the matching lobes and recesses.

  The direction in which the gas flows, that is, whether the gas enters or exits the temporary chamber, depends on whether the rotary device is operating as a compressor or an expander. In both cases, it is possible to provide a portion that communicates with the temporary chamber in both the axial and radial directions as shown in FIG.

  Those skilled in the art will appreciate that numerous modifications to the preferred embodiments described above and departures from the preferred embodiments are possible. Accordingly, the present invention is intended to cover modifications and applications as long as they fall within the scope of the appended claims and their equivalents.

1 is a schematic longitudinal sectional view of a part of an internal combustion engine that implements the present invention, taken on a plane that passes through the axes of a rotor of a compression section and an expansion section equipped with a rotary device that implements the present invention; The enlarged view of the combustion chamber shown in FIG. 1 is shown. FIG. 2 is a side view showing a part of the compression section of the internal combustion engine shown in FIG. 1 in a perspective view, showing a housing surrounding a compression rotor. 2a, 2b and 2c are respectively schematic cross-sectional views of the interacting rotor in the compression section, showing successive stages in the compression cycle of the engine. 3a, 3b, and 3c are schematic cross-sectional views of the interacting rotor in the expansion section, respectively, showing successive stages in the engine expansion cycle. The end surface of the valve part of the concave rotor shown by embodiment of FIG. 1 is shown. 2 shows a side view of the housing wall of the embodiment shown in the embodiment of FIG. FIG. 2 is a diagrammatic cross-sectional view through two compression rotors forming part of the embodiment shown in FIG. 1, as viewed from the compression rotor of this embodiment towards the central wall. FIG. 6 is a diagrammatic cross-sectional view through the two rotors of FIG. 5, showing a state seen from the central wall toward the rotor. Fig. 2 shows a housing shaped to surround the compression rotor and cooperate with the rotor during the compression cycle, corresponding to that of Figs. 2a, 2b, 2c. FIG. 8 is a view similar to FIG. 7, but corresponding to FIGS. 3a, 3b, 3c, showing a housing surrounding the expansion rotor for cooperating with the rotor during the expansion cycle. FIG. 2 is a cross-sectional view of the interacting rotor of the compression section of the embodiment of FIG. 1, showing a stage with a continuous compression cycle of the engine, further illustrating the stage shown in FIGS. 2 a, 2 b, and 2 c. FIG. 2 is a cross-sectional view of the interacting rotor of the compression section of the embodiment of FIG. 1, showing a stage with a continuous compression cycle of the engine, further illustrating the stage shown in FIGS. 2 a, 2 b, and 2 c. FIG. 2 is a cross-sectional view of the interacting rotor of the compression section of the embodiment of FIG. 1, showing a stage with a continuous compression cycle of the engine, further illustrating the stage shown in FIGS. 2 a, 2 b, and 2 c. FIG. 2 is a cross-sectional view of the interacting rotor of the compression section of the embodiment of FIG. 1, showing a stage with a continuous compression cycle of the engine, further illustrating the stage shown in FIGS. 2 a, 2 b, and 2 c. FIG. 2 is a cross-sectional view of the interacting rotor of the compression section of the embodiment of FIG. 1, showing a stage with a continuous compression cycle of the engine, further illustrating the stage shown in FIGS. 2 a, 2 b, and 2 c. FIG. 2 is a cross-sectional view of the interacting rotor of the compression section of the embodiment of FIG. 1, showing a stage with a continuous compression cycle of the engine, further illustrating the stage shown in FIGS. 2 a, 2 b, and 2 c. It is the side view figure which showed the example of the rotor currently used by this invention in a partial perspective view. An example of the rotor of FIG. 10 is shown in a shape during a rotation cycle. An example of the rotor of FIG. 10 is shown in a shape during a rotation cycle. An example of the rotor of FIG. 10 is shown in a shape during a rotation cycle. Fig. 4 shows a schematic cross-sectional view of an expander interacting rotor, showing successive stages within an expansion period. Fig. 4 shows a schematic cross-sectional view of an expander interacting rotor, showing successive stages within an expansion period. Fig. 4 shows a schematic cross-sectional view of an expander interacting rotor, showing successive stages within an expansion period. Fig. 4 shows a schematic cross-sectional view of an expander interacting rotor, showing successive stages within an expansion period. Fig. 4 shows a schematic cross-sectional view of an expander interacting rotor, showing successive stages within an expansion period. Fig. 4 shows a schematic cross-sectional view of an expander interacting rotor, showing successive stages within an expansion period. Fig. 4 shows a schematic cross-sectional view of an expander interacting rotor, showing successive stages within an expansion period. Fig. 4 shows a schematic cross-sectional view of an expander interacting rotor, showing successive stages within an expansion period. FIG. 2 shows a schematic cross-sectional view of an interacting rotor of a compressor, showing successive stages within a compression cycle. FIG. 2 shows a schematic cross-sectional view of an interacting rotor of a compressor, showing successive stages within a compression cycle. FIG. 2 shows a schematic cross-sectional view of an interacting rotor of a compressor, showing successive stages within a compression cycle. FIG. 2 shows a schematic cross-sectional view of an interacting rotor of a compressor, showing successive stages within a compression cycle. FIG. 2 shows a schematic cross-sectional view of an interacting rotor of a compressor, showing successive stages within a compression cycle. FIG. 2 shows a schematic cross-sectional view of an interacting rotor of a compressor, showing successive stages within a compression cycle. FIG. 2 shows a schematic cross-sectional view of an interacting rotor of a compressor, showing successive stages within a compression cycle. FIG. 2 shows a schematic cross-sectional view of an interacting rotor of a compressor, showing successive stages within a compression cycle. FIG. 3 shows a two-dimensional end view of a pair of rotors with both radial and axial ports.

Claims (20)

Rotary device:
A first rotor capable of rotating around a first axis and having at least one recess at its periphery delimited by a curved surface;
A stator disposed around the first rotor to rotate;
A second rotor having at least one radial lobe that is rotatable about a second axis parallel to the first axis and is opposite to the first rotor and bounded by a curved surface;
First and second coupled together to rotate in unison to create a temporary chamber in which the volume defined between the curved recess and the lobe surface of the first and second rotors increases or decreases in stages. With two rotors;
A housing in which the rotor is enclosed, and the housing has an end surface joined to an end surface of the internal engagement rotor;
The rotor further comprises a rotor port arranged to allow gas to flow into or from the at least one recess in the concave rotor, the port having a plurality of dimensions, at least one of the dimensions being A rotary device longer than the distance between the outermost limit of the stator and the minimum radius of the recess in the concave rotor. Each of the first and second rotors has an end face spaced along a corresponding axis, and the rotor port is provided inside one of the end faces, and the end face of the housing One has at least one associated port for communicating with the at least one rotor port, the concave rotor port and the housing port being in rotation of the rotor, Barbing is performed by moving the joint end face of the concave rotor and housing;
The concave rotor has a valve portion defining the at least one port of the concave rotor and a main portion defining the at least one recess, the valve portion and the main portion being the concave rotation. Arranged along the axis of the rotor, each of the at least one port on the concave rotor and the at least one port on the housing being radially outward from the axis of the concave rotor. The rotary device according to claim 1, wherein the rotary device extends at least a distance beyond the innermost limit of the recess in the concave rotor.   The at least one rotor port and the at least one port on the housing are each positioned so as to be disposed only at the radially outermost position of the innermost limit of the recess in the concave rotor. The rotary device according to claim 2.   4. The valve according to claim 2, wherein the valve portion of the concave rotor includes an end wall extending perpendicular to the axis of the concave rotor and is disposed at a closed portion at one end of the rotor concave portion. The rotary device according to claim 1.   The rotary device according to claim 4, wherein the other end of the rotor recess is closed by a further end wall of the housing.   The rotary device according to claim 4, wherein the at least one rotor port is a port that passes through a first end wall of the concave rotor.   The valve portion comprises a disk, the disk being perpendicular to and coaxial with the first axis and arranged to rotate with the main portion of the first concave rotor. Item 7. The rotary device according to any one of Items 4 to 6.   The curved surface is continuously swept by both the tip of the lobe and a movable location on the lobe that advances along the lobe surface while the lobe passes through the recess; The rotary device according to any one of the preceding claims, wherein the rotary device has a contour such that the temporary chamber is defined.   The rotary device according to any one of the preceding claims, wherein each of the at least one recess and the at least one lobe extend in a spiral in the axial direction.   Any of the preceding claims, wherein the rotational speed of the first concave rotor is slower than the rotational speed of the second lobe rotor of the device and less than 1: 1 of the total number. The described rotary device.   Each of the first and second rotors has recesses that are equiangularly spaced from each other, and the ratio of the number of recesses to the number of lobes as the speed ratio of the rotor with lobes relative to the concave rotor. The rotary device according to claim 10, comprising a plurality of lobes.   The rotor is enclosed within a housing, the housing having first and second arcuate recesses that are coaxial with the first and second rotors and form a sliding seal therewith, thereby providing the lobe. For a portion of the rotation before and / or after passing through the recess in the first rotor, an additional temporary chamber is defined between the rotor and the housing to increase or decrease the capacity in stages. The rotary device according to any one of the preceding claims, wherein communication with a temporary chamber between the rotors is performed.   The stator is a cylinder, and includes a port provided on at least one recess, and when the rotor rotates with respect to an axis, the port on the stator cylinder and the rotor port periodically The aligned and recessed portions are valved by interaction of the stator cylinder and an inner cylindrical surface of the first rotor disposed in rotational and slidable engagement with the stator cylinder. Item 2. The rotary device according to Item 1.   The rotary device of claim 13, wherein a port on each of the stator cylinder and rotor extends axially relative to the rotor.   The rotary device according to claim 14, wherein a port on each of the stator cylinder and the rotor extends with a length substantially equal to an axial length of the rotor.   The rotor is enclosed within a housing, the housing having first and second arcuate recesses that are coaxial with the first and second rotors and form a sliding seal therewith, thereby providing the lobe. For a portion of the rotation before and / or after passing through the recess in the first rotor, an additional temporary chamber is defined between the rotor and the housing to increase or decrease the capacity in stages. The rotary device according to any one of claims 13 to 15, wherein communication with a temporary room between the rotors is performed. Rotary device:
A first rotor capable of rotating around a first axis and having at least one recess at its periphery delimited by a curved surface;
A second rotor having at least one radial lobe that is rotatable about a second axis parallel to the first axis and is opposite to the first rotor and bounded by a curved surface;
First and second coupled together to rotate in unison to create a temporary chamber in which the volume defined between the curved recess and the lobe surface of the first and second rotors increases or decreases in stages. With two rotors;
A housing in which the rotor is enclosed, and the housing has an end surface joined to an end surface of the internal engagement rotor;
The first rotor further includes a stator cylinder disposed around the first rotor, wherein the stator cylinder is a hollow cylindrical member, and the hollow cylindrical member corresponds to the first rotor. An internal dimensioned hollow cylindrical bore and having a port disposed thereon, through which the interior and exterior of the stator cylinder can be communicated;
The recess in the first stator has at least one port that allows communication between the central bore in the rotor and the recess, and a port on the stator cylinder and on the rotor Each of the ports of the rotary device is configured such that the ports can be periodically aligned as the rotor rotates relative to the stator cylinder. One of the end faces of the first concave rotor has at least one rotor port in communication with at least one recess of the rotor, and one of the end faces of the housing is associated therewith And at least one port for communicating with the at least one rotor port, wherein the concave rotor port and the housing operate during the rotation of the rotor at the joint end face of the concave rotor and housing. Is rubbed by;
The concave rotor includes a valve portion that defines the at least one rotor port and a main portion that defines the at least one recess, wherein the valve portion and the main portion are the concave rotation. And at least one port on the concave rotor and each of the at least one port on the housing radially outward from the axis of the concave rotor. 18. The rotary device of claim 17, wherein the rotary device extends at least a distance beyond the innermost limit of the recess of the concave rotor. Rotary device:
A first rotor that is rotatable about a first axis and has at least one recess bounded by a curved surface in the periphery, said first rotor having end faces spaced along its axis;
A second rotor having at least one radial lobe bounded by a curved surface and capable of rotating in a direction opposite to the first rotor around a second axis parallel to the first axis; The second rotor has end faces spaced along its axis;
First and second coupled together to rotate in unison to create a temporary chamber in which the volume defined between the curved recess and the lobe surface of the first and second rotors increases or decreases in stages. With two rotors;
A housing in which the rotor is enclosed, and the housing has an end surface joined to an end surface of the internal engagement rotor;
One of the end faces of the first concave rotor has at least one port in communication with at least one recess of the rotor, and one of the end faces of the housing is associated therewith, At least one port for communicating with at least one rotor port, wherein the port of the concave rotor and the port of the housing are joined end faces of the concave rotor and the housing during rotation of the rotor Is balbbed by the action of
The concave rotor has a valve portion defining the at least one port of the concave rotor and a main portion defining the at least one recess, the valve portion and the main portion being the concave rotation. Arranged along the axis of the rotor, each of the at least one port on the concave rotor and the at least one port on the housing being radially outward from the axis of the concave rotor. And a rotary device extending at least a distance beyond the innermost limit of the recess in the concave rotor.   A separate rotary compression section and expansion section, and a combustion chamber with an inlet port and an outlet port communicating with each of the compression section and expansion section, each of the compression section and expansion section being any one of the preceding claims. An internal combustion engine which is a rotary device described in the paragraph.