JP2009517600A - Rotary motor using intermittent rotor motion - Google Patents

Abstract

  The present invention includes a first rotor member that can rotate around a first axis, a second rotor member that can rotate around a second axis, a first rotor member, and a second rotor member. A rotary motor comprising a transmission device for rotation, wherein the first rotor member and the second rotor member rotate at a variable angular velocity.

Description

  The present invention relates to a novel rotary motor.

  It is well known that rotary motors are used in a wide variety of applications including internal combustion engines, compressors, pumps and the like for vehicles.

  A wide variety of rotary internal combustion engines have been proposed and developed so far. In particular, the Wankel rotary engine is well known. This includes a substantially laminar rotor member that rotates about a moving axis. The rotor member is a triangular layer plate having three convex sides. The plate rotates around the movement axis in the room, and the chamber has a configuration and dimensions slightly larger than the width of the plate member, and the inner shape complements the rotation shape of the plate member.

  Furthermore, various compressors and engines are known that incorporate rotor members having a blade shape.

[Object of invention]
It is an object of the present invention to provide a novel rotary motor that provides a useful and functional alternative to the prior art. As used herein, the term “rotary motor” includes both internal combustion engines and compressors, pumps, and the like.

According to the present invention,
A first rotor member rotatable about a first axis;
A second rotor member rotatable about a second axis;
A rotary motor comprising a transmission device for rotating the first rotor member and the second rotor member,
A rotary motor is provided in which the first rotor member and the second rotor member are configured to rotate at a variable angular velocity.

  Similarly, according to the present invention, the angular velocity of the first rotor and the angular velocity of the second rotor are different from each other during the rotation period of the motor. Preferably between 360 degrees for each rotor.

  Further in accordance with the present invention, the first rotor member and the second rotor member may be sized and configured to seal the compression chamber between each other when rotating.

  Accordingly, each of the first rotor member and the second rotor member includes blades extending outward in the radial direction and having a receiving structure portion therebetween, and the receiving structure portion of the first rotor member is formed of the rotor member. Sized and configured to receive blades from the second rotor member during rotation, and the receiving structure of the second rotor member is configured to receive blades from the first rotor member during rotation of the rotor member Can be dimensions and configurations.

  The first rotor member and the second rotor member may be rotationally coupled to each other by a transmission.

  The transmission may comprise a plurality of gears that may partially have a first radius and partially may have a second radius.

  The gear may have a variable radius.

  In one configuration of the present invention, the transmission device drives the first rotor member at the first angular velocity and the second rotor member at the second angular velocity during at least part of the rotation, and then complements the rotation. In the target portion, the first rotor member may be driven at the second angular velocity, and the second rotor member may be driven at the first angular velocity.

  The first axis is parallel to the second axis, and the first rotor member and the second rotor member may be sealed on both sides by the housing to form a chamber within the housing.

  Furthermore, according to the invention, the free end of each vane terminates in a radially extendable portion adapted to follow the contour of the chamber in the housing. In such a configuration, the housing can be expanded radially outward in its opposing area to form a generally elliptical structure.

  A rotary motor in the form of an internal combustion engine includes an inlet passage for introducing air into the compression chamber, an outlet passage for discharging gas from the compression chamber, means for introducing fuel into the compression chamber in a predetermined area, and fuel introduced into the compression chamber It may further comprise ignition means for igniting.

  These and other features of the invention are described in more detail below without limiting the scope of the invention.

  An embodiment of the present invention will be described below by way of example only with reference to the accompanying drawings.

[Detailed description of the drawings]
Referring to the drawings, like numerals indicate like features, and a rotary motor, in this case an internal combustion engine, is indicated generally by the reference numeral 10. In a different configuration (not shown), the rotating member may be applied as a compressor, a pump, or the like.

  The internal combustion engine 10 is embodied by a first rotor member 20 that can be rotated around a first axis that is embodied by a first rotor shaft 30 and a second rotor shaft 50 that is parallel to the first rotor shaft 30. A second rotor member 40 rotatable about a second axis, and a first rotor member 20 and a gear mechanism 60 for rotating the second rotor member 40, the first rotor member 20 and The second rotor member 40 rotates at a variable angular velocity and different angular velocities.

  3a-3f, in the illustrated embodiment, the first rotor member 20 and the second rotor member 40 are sized and configured to seal the combustion chamber 200 between each other when rotating. It is. Both the first rotor member 20 and the second rotor member 40 have engaging surfaces 21 and 41 on the opposing surfaces of the respective rotors. In operation, to prevent combustion exhaust gases from escaping from the sides of the rotors 20 and 40 during operation, the rotors 20 and 40 are sealed on both sides by a housing shown schematically at 55. The housing may include a pair of plate members 56 on both sides of the rotors 20 and 40. It is envisioned that the flat sides of the rotor members 20 and 40 are sealed to this plate by suitable sealing means (not shown). The housing 55 includes a pair of circular chambers 56 that intersect as shown in FIG. 8, in which the rotor members 20 and 40 rotate. Referring to FIG. 8, the generally circular chamber 56 can be modified in its outer circumference, for example by a radially outward extension 57, to change the compression and expansion of the combustion chamber 200, as will be described in more detail below. .

  Each of the first rotor member 20 and the second rotor member 40 includes a plurality of blades 25 and 45 extending radially outwardly, and has receiving structures 26 and 46 therebetween. Receiving structures 26 and 46 are sized and configured to operably receive vanes from the other rotor member. In one embodiment of the invention, the free ends of the vane structures 25 and 45 are provided with radially extendable end portions 25a and 45a adapted to follow the curvature of the receiving structures 26 and 46. Such an extendable end portion can also follow the periphery of the inner chamber 56 of FIG. 8 being expanded radially outward as indicated by region 57. As described above, the expansion region 57 affects the intake of air into the chamber 57, air compression, and combustion gas expansion.

  Referring to FIG. 1, since the gear mechanism 60 couples the first rotor member 20 and the second rotor member 40 to each other, they can move only in a predetermined order of movement relative to each other. The gear mechanism 60 includes a drive gear device 70 installed on the drive shaft 73, a first timing gear device 80 installed on the first timing shaft 100, and a second timing installed on the second timing shaft 110. A plurality of gears and shafts including a gear device 90 are provided.

  The drive gear device includes a large gear 71 and a small gear 72 that are installed next to each other on the drive shaft 73. The tooth group of the large gear 71 extends only 180 degrees around the drive shaft, and the tooth group of the small gear 72 extends 180 degrees of the drive shaft 73 in a complementary manner.

  Similarly, the first timing gear device 80 includes a large gear 81 and a small gear 82 that are installed adjacent to each other on the first timing shaft 100, and the second timing gear device 90 includes a second timing shaft. 110 consists of a large gear 91 and a small gear 92 installed next to each other. The teeth of each of the large gears 81 and 91 extend over 90 degrees around the first timing shaft 100 and the second timing shaft 110, and the teeth of each of the small gears 82 and 92 are Extends about 270 degrees (complementary angle) around the timing axis 100 and the second timing axis 110.

  Since the first timing gear device 80 and the second timing gear device 90 are interlocked with the driving gear device 70 (as shown in FIGS. 4a and 4d), at a certain stage, the large gear 71 of the driving gear device 70 is The small gear 82 of the first timing gear device 80 and the small gear 92 of the second timing gear device 90 are driven, and the small gear 72 of the driving gear device 70 is driven to the large size of the first timing gear device 80 at other stages. The gear 81 and the large gear 91 of the second timing gear device 90 are driven.

  This interaction between the small gear and the large gear at various stages results in the first rotor member 20 and the second rotor member 40 having different angular velocities at different stages during one rotation of the drive gear device 70. . A graph of the angular velocities of the first rotor member 20 and the second rotor member 40 is shown in FIG. The graph shown in FIG. 5 does not have to be a straight line. For example, there may be a curve section on the lower side of the graph before the direction change and on the upper side of the graph before the end. As a result, the maximum volume of the compression chamber and expansion chamber of the motor of the present invention will be uneven.

  The first timing gear device 80 and the second timing gear device 90 drive the first timing shaft 100 and the second timing shaft 110, respectively. The first timing shaft 100 and the second timing shaft 110 further drive the first reduction gear device 120 and the second reduction gear device 130, respectively, which are the first final drive gear 140 and the second The rotor members 20 and 40 are driven in the reverse direction via the final drive gear 150.

  Both the small gear and the large gear of each of the driving gear device 70, the first timing gear device 80, and the second timing gear device 90 may be incorporated into one gear, or a continuously variable transmission is used. It is envisaged that It should be noted that the results achieved by the gears described herein can be achieved by various gear configurations not shown and the present invention is not limited to the gear configurations shown in FIGS. 4a-4d. .

  The second reduction gear device 130 has an additional reverse gear 131 that allows the direction of the second rotor member 40 to be reversed.

  In addition to the timing gears 80 and 90, there are various alternative mechanisms that allow the movement of the rotor members 20 and 40 to be controlled. One such mechanism is schematically illustrated, for example, in FIG. 9, in which a template 63 is provided that can be secured to the shafts 30 and 50 of the rotors 20 and 40, respectively. It includes a cam structure 61 in the form of a groove that matches the movement of the vanes 25, 45. The cam structure 61 is driven by a follower in the form of a pin 62. Therefore, the template 63 and the follower 62 reproduce the movements of the rotors 20 and 40. Other variations are certainly possible.

  The rotary motor operating as the internal combustion engine 10 further comprises an inlet passage schematically shown at 51 in FIG. 6 for introducing air 52 into the combustion chamber 200 formed by the rotors 20 and 40. Further, the internal combustion engine 10 includes an outlet passage schematically shown at 53 in FIG. 6 for discharging the combustion gas 54 from the combustion chamber 200. The internal combustion engine 10 is a fuel for introducing fuel (not shown) into the combustion chamber 200 at a predetermined point by direct injection into the combustion chamber 200 or flowing into the combustion chamber 200 together with air introduced through the inlet passage. It is also contemplated to include means such as an injector (not shown) or a vaporizer (not shown).

  The internal combustion engine 10 also includes ignition means (not shown) such as a spark plug for igniting a mixture of fuel and air in the combustion chamber 200. It is envisioned that high compression in the combustion chamber 200 may allow diesel or other similar fuels to be used for compression and ignition operations.

  In operation, the drive gear device 70 drives the first timing gear device 80 and the second timing gear device 90. The driving gear device 70 and the timing gear devices 80 and 90 are driven at an angular velocity different from that of the second timing shaft 110 for each rotation of the driving shaft 73 while the first timing shaft 100 is at least part of each rotation. After that, as shown in FIG. 5, the first timing axis 100 and the second timing axis 110 are arranged so that the angular velocities are reversed.

  The timing shaft drives the first reduction gear device 120 and the second reduction gear device 130, and drives the first rotor member and the second rotor member, respectively. Since the direction of the second rotor member 40 is reversed by including the reverse gear 131 in the second reduction gear device 130, the first rotor member 20 and the second rotor member 40 are shown in FIGS. Turn in the opposite direction as shown in 3f.

  3a-3f show how the rotor members 20 and 40 rotate relative to each other. In FIG. 3 a, the first rotor member 20 is rotating faster than the second rotor member 40. When the blades 25 of the first rotor member 20 are received by the receiving structure 46 of the second rotor member 40 (between the two blades 45 of the second rotor member 40), a sealed combustion chamber 200 is formed. Is done.

  At this stage, a combustible mixture of air and fuel indicated by 52 in FIG. 6 is introduced into the combustion chamber 200. The air-fuel mixture is introduced through the inlet passage by introducing the air-fuel mixture from the inlet using a vaporizer or by injecting a fine fuel spray into the combustion chamber 200 using a fuel injection device (not shown). It is envisaged that it can be introduced by known means, such as by mixing in the combustion chamber 200. In one configuration, the small auxiliary combustion chamber 22 of FIG. 2 on the vanes 25 and 45 as shown can be provided to enhance the combustion process. It is assumed that the fuel injection is directed to the small chamber 22.

  If the first rotor member 20 and the second rotor member 40 continue to rotate at unequal angular velocities (as shown in FIGS. 3b and 3c), the size of the combustion chamber 200 decreases, resulting in a mixture of fuel and air. Is compressed. At the stage shown in FIG. 3c, the angular speed of the first rotor member and the second rotor member changes, so that the slower rotor member (second rotor member 40) now moves faster between the two rotor members 20 and 40. The first rotor member 20 is reversed.

  The compressed fuel / air mixture 52 in the compressed combustion chamber 200 is then ignited by the ignition means. When the fuel / air mixture is ignited, the gas in the combustion chamber 200 expands. The combustion chamber 200 expands while driving the second rotor member counterclockwise as shown in FIG. 3d. At the same time, another combustion chamber 200 is being formed by the interaction between the blades of the first rotor member 20 and the second rotor member 40 and the receiving structure as shown in FIG. 3e. Prior to the formation of the sealed combustion chamber 200 of FIG. 3a, its volume is reduced and excess air is introduced into the adjacent chamber 201, causing the pressure in the adjacent chamber 201 to rise above the ambient air pressure. I know it. It should be noted that the same effect occurs when the volume of the chamber 201 is reduced by the interaction of the vanes 25 and 45, for example as shown in FIGS. 3c and 3d. As a result of such fluid movement, the efficiency of the internal combustion engine is increased.

  The combustion gas 54 in the combustion chamber 200 is subsequently discharged through the outlet passage 53 of the housing 55. The outlet passage 53 can be installed in the housing 55 beside the rotor members 20 and 40 (FIG. 6).

  The gas expansion of the ignited fuel / air mixture in the first combustion chamber 200 of FIGS. 3a and 3b is the fuel / air mixture for the next combustion chamber 201 formed in FIGS. 3e and 3f. It turns out that it is useful for compression of qi.

  This basic principle of operation can be used in a wide variety of configurations, in order to maximize the volume of the compressed fuel / air mixture 52 or when the ignited fuel / air mixture is impeller 45. It is envisioned that a wide variety of shapes can be used as the rotor members 20, 40 in order to maximize the amount of time acting on the rotor.

  It is envisioned that the gear mechanism 60 may be a planetary gear device. It is further envisaged that because the shape of the combustion chamber 200 is elongated, the mixture 52 can be ignited at both ends of the combustion chamber 200 using two ignition means in the form of spark plugs. For the same reason, it is preferable to use two fuel injectors (not shown) in a spaced relationship for the elongated combustion chamber 200.

  It is further envisioned that the blades 25 and 45 and the receiving structures 26 and 46 of the rotors 20 and 40 may include combustion promoting structures to increase combustion efficiency.

  It should be understood that the above is only one embodiment of the present invention, and that many variations can be made in detail without departing from the scope of the present invention. For example, a set of rotor members may be arranged in a circle around one inlet passage 51 or outlet passage 53. Further, in order to increase the strength or reliability, the rotor members 20 and 40 having various shapes and the blades 25 and 45 extending not so long may be used. In a further embodiment, it is envisioned that a plurality of rotor members 20, 40 may be installed around a central rotor member to form a plurality of combustion chambers with the central rotor member. In yet another embodiment, one of the interacting rotor members 20, 40 is held fixed, and the one or more rotating rotor members again interact with the fixed rotor member in the same manner as described above, and the fixed rotor member. It is envisaged that it may rotate around. In such an embodiment, the timing of the plurality of rotor members rotating about one fixed rotor member may be shifted so that combustion is not performed simultaneously in all the combustion chambers but at regular intervals. Further assumed.

  In yet another embodiment, it is envisioned that multiple rotors may be installed on the same axis and each rotor may interact with a corresponding rotor as a group of rotors. Each of these rotor groups may be synchronized with each other or may be offset in timing so as to be asynchronous with each other.

1 shows a schematic perspective view of an internal combustion engine according to the invention without a housing. The schematic front view of the 1st rotor member and 2nd rotor member which are shown in FIG. 1, and a transmission is shown. FIG. 3 is a schematic plan view of a first rotor member and a second rotor member and their movement relative to each other. FIG. 3 is a schematic plan view of a first rotor member and a second rotor member and their movement relative to each other. FIG. 3 is a schematic plan view of a first rotor member and a second rotor member and their movement relative to each other. FIG. 3 is a schematic plan view of a first rotor member and a second rotor member and their movement relative to each other. FIG. 3 is a schematic plan view of a first rotor member and a second rotor member and their movement relative to each other. FIG. 3 is a schematic plan view of a first rotor member and a second rotor member and their movement relative to each other. It is a schematic plan view of the gear of the transmission that causes the movement of the rotor member. It is a schematic plan view of the gear of the transmission that causes the movement of the rotor member. It is a schematic plan view of the gear of the transmission that causes the movement of the rotor member. It is a schematic plan view of the gear of the transmission that causes the movement of the rotor member. It is a graph of the angular position of the first rotor and the second rotor with respect to the angular position of the drive shaft during one rotation of the transmission. It is the schematic of the inlet port and outlet port in the side plate which forms a part of housing of the motor of this invention. FIG. 4 is a schematic plan view of a first rotor member and a second rotor member, each including a front end portion that can be extended by radially outward blades of the rotor. FIG. 5 is a schematic plan view of opposing chambers that extend outwardly to change the compression and expansion characteristics of the motor and in which the first and second rotor members rotate internally. It is a schematic perspective view of the timing mechanism which reproduces the motion of the blades of the first rotor member and the second rotor member.

Claims (11)

A first rotor member rotatable about a first axis;
A second rotor member rotatable about a second axis;
A rotary motor configured to rotate the first rotor member and the second rotor member, wherein the first rotor member and the second rotor member rotate at a variable angular velocity. Because
In the 360 degree period of the rotor, from the start position, the first rotor rotates at a first average rotation speed and the second rotor rotates at a different average rotation speed for a part of one rotation, and then one rotation During the subsequent portion of rotation, the average rotational speed of the first rotor and the average rotational speed of the second rotor are changed so that after the rotor rotates 360 degrees, the rotor returns to the start position. Rotating motor characterized by lighting.   Each of the first rotor member and the second rotor member includes blades extending radially outward, and has a receiving structure portion between the blades, and the receiving structure of the first rotor member The portion is sized and configured to receive the vanes from the second rotor member, and the receiving structure portion of the second rotor member is to receive the vanes from the first rotor member. The rotary motor according to claim 1, which has dimensions and configuration, and a compression chamber is formed in the receiving structure when the rotor rotates.   The first rotor member and the second rotor member each include a plurality of radially extending vanes, the rotor re-entering the start position at a plurality of rotational positions during a 360 degree rotation cycle. The rotary motor according to 1 or 2.   The housing includes an interior chamber in which the first rotor member and the second rotor member rotate, the interior chamber extending outwardly so as to form a substantially elliptical structure. The rotary motor according to any one of claims 1 to 3.   5. A rotary motor according to claim 4, wherein the free ends of all or selected vanes terminate in a radially extendable portion configured to follow the contour of the internal chamber in the housing.   The rotary motor according to any one of claims 1 to 5, wherein the first rotor member and the second rotor member are coupled to each other so as to rotate by a transmission device.   The transmission device drives the first rotor member at a first angular velocity and the second rotor member at a second angular velocity during at least a portion of one rotation, and then complements the one rotation. The rotary motor according to claim 6, wherein the first rotor member is driven at the second angular velocity and the second rotor member is driven at the first angular velocity.   The rotary motor according to claim 6 or 7, wherein the transmission device includes a plurality of gears partially having a first radius and partially having a second radius.   The rotary motor according to claim 6, wherein the gear has a variable radius.   The housing includes an inlet passage for introducing air into the compression chamber, an outlet passage for discharging gas from the compression chamber, means for introducing fuel into the compression chamber in a predetermined area, and fuel introduced into the compression chamber. The rotary motor according to claim 2, comprising ignition means for igniting.   A rotary motor substantially as described and illustrated herein with reference to the accompanying drawings.

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