JPWO2011125969A1 - Gearbox and power generator equipped with the gearbox - Google Patents

Abstract

An object of the present invention is to provide a gearbox having a simple structure, a compact configuration and good rotational torque transmission efficiency, and a power generator equipped with the gearbox, and an input shaft that rotates by an external force; A frame; an output shaft rotatably supported by the base frame; a fixed external gear concentric with the axis of the output shaft and fixed to the base frame; An eccentric wheel that is coupled to the output shaft and rotates integrally with the output shaft about the shaft of the output shaft; a bearing portion that supports the eccentric wheel so as to be slidably rotatable therein; By providing a speed increasing device having a rotor having an internal gear that meshes with an external gear; a rotation transmission mechanism that transmits the rotation of the input shaft to the rotor, and a power generation device including the speed increasing device. Solve .

Description

  The present invention relates to a speed increaser that speeds up rotation of an input shaft and transmits it to an output shaft, and a power generation device including the speed increaser.

  2. Description of the Related Art Conventionally, power generation apparatuses that generate power using natural energy such as wind power or hydraulic power are known. In these power generators, when transmitting the rotation of the windmill or water turbine to the rotor of the generator, a speed increaser is interposed between the main shaft and the rotor, and the rotational speed of the main shaft is increased and transmitted to the rotor. Things have been done.

  For example, Patent Document 1 discloses a waterway hydroelectric power generator that rotates a water wheel with the energy of water, and transmits the rotation to a generator by increasing the rotation speed using a speed increaser. That is, a wind power generator with a speed increaser that rotates a windmill with the energy of the atmosphere and transmits the rotation to a power generator by a planetary gear type speed increaser is disclosed in Patent Document 3. In the same way, the windmill is rotated by the energy of the atmosphere, and the rotation is increased by a gearbox that combines a star-type planetary roller traction drive and a planetary planetary roller-type traction drive, and is transmitted to the generator. A wind power generator is disclosed.

However, the conventional speed increaser has the disadvantages that it has a complicated structure, a large number of parts, and is expensive. That is, for example, the planetary gear type speed increaser as used in Patent Document 2 has a drawback in that the number of gears used is large due to its structure, the structure is complicated, bulky, and expensive to manufacture. Further, for example, the traction drive type speed increaser used in Patent Document 3 has little noise and vibration, but still has a large number of parts, a complicated structure, and is bulky, and also has a stable rotational torque transmission efficiency. In addition, there is a problem that it is difficult to obtain a large speed increase ratio by itself.
JP 2003-269315 A JP 2001-304094 A JP-A-5-0779450

  The present invention has been made in view of the above-described circumstances, and includes a speed increaser that has a simple structure, can be configured compactly, and has high rotational torque transmission efficiency, and a power generation apparatus including the same. The purpose is to provide.

  As a result of repeating various trials and errors to solve the above problems, the present inventor paid attention to the phase gear employed in the rotary engine, and rotated the member corresponding to the rotor in the rotary engine by rotating the input shaft. The idea was that if the rotation was transmitted to the output shaft via an eccentric ring, the structure would be simple and efficient acceleration could be achieved. As a result of further research based on this concept, a rotor with a built-in internal gear that meshes with the fixed external gear is rotated around the fixed external gear, and an eccentric ring is slidably rotated inside the rotor. By connecting the rotor to the input shaft and connecting the eccentric wheel to the output shaft, the input shaft can be rotated from a low speed to a high speed with a simple structure, enabling efficient speed increase. As a result, the present invention was completed.

  That is, the present invention includes an input shaft that is rotated by an external force; a base frame; an output shaft that is rotatably supported by the base frame; and a shaft that is concentrically fixed to the base frame. A fixed external gear; an eccentric wheel that is eccentric with respect to the axis of the output shaft, is coupled to the output shaft, and rotates integrally with the output shaft around the axis of the output shaft; Provided is a speed increaser comprising: a rotor having a bearing portion that is slidably supported inside; a rotor having an internal gear meshing with the fixed external gear; and a rotation transmission mechanism that transmits the rotation of the input shaft to the rotor. This solves the above problem.

  In the speed increaser of the present invention, it is not necessary to use a complicated planetary gear mechanism, and an extremely simple structure of a fixed external gear, a rotor having an internal gear, and an eccentric wheel that is slidably and rotatably supported inside the rotor. By the component, the rotation of the input shaft can be accelerated and transmitted to the output shaft. The speed increasing rate is determined by the ratio of the number of teeth of the fixed external gear and the number of teeth of the internal gear in the rotor, that is, the gear ratio. For example, the gear ratio of the fixed external gear and the internal gear in the rotor is 2: If it is 3, the eccentric wheel built in the rotor is rotated three times by one rotation of the rotor, and a threefold speed increase rate is obtained. In addition, if the number of teeth of the fixed external gear and the gear ratio of the internal gear in the rotor are 1: 2, the eccentric wheel built in the rotor is rotated four times by one rotation of the rotor, and the speed increase rate is four times. Is obtained. As for the relationship between the gear ratio and the rotational speed in the phase gear mechanism, for example, GP Planning Center, “History of Mazda Rotary Engine”, Grand Prix Publishing Co., Ltd., published on February 10, 2003, 28-36. Page 44.

  Further, in the speed increaser of the present invention, the eccentric wheel is rotated by rotating the rotor by the rotation of the input shaft. Therefore, when the eccentric wheel is rotated, the operating point of the rotational force from the rotor from the rotation center of the eccentric wheel is rotated. The moment with the distance up to the arm length can be used. Therefore, the rotational torque is increased as compared with the case where the input shaft and the output shaft are rotated concentrically without using an eccentric ring, and an efficient speed increase is possible.

  In a preferred embodiment, the speed increaser of the present invention preferably transmits the rotation of the input shaft to the rotor by an Oldham coupling mechanism. That is, the rotor revolves while rotating around the fixed external gear while meshing the built-in internal gear with the fixed external gear, so the center of the rotor moves without being stationary at one point, but as a rotation transmission mechanism When using the Oldham coupling mechanism, the movement of the center of the rotor is absorbed by the Oldham coupling mechanism, and the rotation of the input shaft that rotates with the rotation center stationary at one point is efficiently transmitted to the rotor to rotate the rotor. Can do.

  In the preferred embodiment, the Oldham coupling mechanism described above has a drive plate connected to the input shaft, and an intermediate node interposed between the drive plate and the rotor, the intermediate node being a drive plate. Having a first convex portion or a concave portion on the surface facing the rotor, and having a second convex portion or a concave portion on the surface facing the rotor, the first convex portion or the concave portion and the second convex portion or the concave portion. Are perpendicular to each other, the drive plate has a third convex portion or concave portion that is slidably fitted to the first convex portion or concave portion, and the rotor is a second convex portion or concave portion. And a fourth convex portion or a concave portion that is slidably fitted. In order to smooth the sliding movement of the convex portions or concave portions that are slidably fitted to each other, at least one convex portion or concave portion of the first to fourth convex portions or concave portions Is preferably provided with a bearing mechanism. Examples of the bearing mechanism include a flat roller bearing, a dry bearing, and an oil impregnated bearing.

  According to a preferred aspect of the speed increaser of the present invention, as a rotation transmission mechanism for transmitting the rotation of the input shaft to the rotor, an external gear provided on the rotor and an internal gear meshing with the external gear are provided. And a rotation transmission mechanism having a rotation wheel coupled to the input shaft and rotating around the axis of the output shaft as the input shaft rotates. When the speed increaser of the present invention is provided with such a rotation transmission mechanism, the rotation of the input shaft rotating with the rotation center stationary at one point is transmitted to the rotor via the internal gear and the external gear. Therefore, the rotation of the input shaft can be transmitted to the rotor more efficiently. The internal gear provided on the rotating wheel and the external gear provided on the rotor may be spur gears. However, from the viewpoint of smooth meshing and reduced vibration and noise. It is preferable to use a gear.

  In a preferred embodiment of the speed increaser according to the present invention, the fixed external gear, the eccentric wheel, the rotor, and the rotation transmission mechanism are provided on both sides along the axial direction of the output shaft. The phases of the eccentric rotations of the rotors and the eccentric rings on both sides are different by 180 degrees. As described above, when the speed increaser of the present invention has the rotation mechanisms including the eccentric wheel on both sides of the output shaft with the rotation phases different from each other by 180 degrees, The vibration accompanying the rotation of the rotor is canceled out, and a quieter and less vibration operation can be realized.

  Further, the speed increaser of the present invention can obtain a high speed increase rate by using it connected in two or more stages so that the output of the front speed increaser becomes the input of the subsequent speed increaser. Is possible. For example, if the speed increaser of the present invention having a gear ratio of 1: 2 is connected in two stages, the speed increase rate per stage is 4 times, so the rotation of the input shaft is increased 4 × 4 = 16 times. In the case of connecting in three stages, the speed can be increased 4 × 4 × 4 = 64 times. Since the speed increaser of the present invention has a simple structure and can be configured in a compact manner, even when two or more stages are connected, the overall speed is not so bulky, and the speed increaser is relatively small and has a high speed increase rate. Can do.

  When the speed increaser of the present invention is connected in multiple stages, the rotation of the output shaft of the front speed increaser is increased between the front speed increaser and the rear speed increaser to increase the rotation speed of the rear speed increaser. An appropriate speed increasing mechanism for transmitting to the input shaft of the speed increaser may be interposed. With this speed increasing mechanism, when the rotation of the output shaft of the front speed increaser is increased by, for example, about 1.5 times and transmitted to the input shaft of the rear speed increaser, the speed increasing rate is further increased. Is possible.

  The present invention also includes a main shaft that is rotated by the energy of the fluid, a generator, and a power transmission unit that transmits the rotation of the main shaft to the generator. The power transmission unit is the speed increaser of the present invention. The above-mentioned problem is solved by providing a power generator provided with the above. Typical examples of the fluid include water, air (atmosphere), water vapor, and the like, and the power generation devices that use the energy possessed by them are produced by various hydroelectric power generation devices, various wind power generation devices, thermal power, or nuclear power. Examples thereof include a thermal power generation apparatus and a nuclear power generation apparatus that convert thermal energy into steam energy to rotate a turbine. The speed increaser of the present invention can be used as a speed increaser in any of these power generators.

  According to the speed increaser of the present invention, since the structure of the speed increaser can be simplified, there are advantages that the speed increaser can be made compact and the manufacturing cost can be reduced. In addition, when rotating the eccentric wheel connected to the output shaft, it is possible to use the moment whose arm length is the distance from the center of rotation of the eccentric wheel to the point of application of the rotational force of the rotor. Speedup with high efficiency is possible, and stable speedup is possible from when the input rotational force is relatively small to large. Furthermore, according to the power generation device of the present invention having the speed increaser of the present invention in the power transmission unit, it is possible to efficiently use the energy of the fluid, and to achieve efficient power generation with a more compact configuration. Is obtained.

It is a cross-sectional side view which shows an example of the gearbox of this invention. It is the elements on larger scale of FIG. FIG. 3 is a cross-sectional view taken along the line X-X ′ of FIG. 2. FIG. 3 is a Y-Y ′ sectional view of FIG. 2. It is an exploded view of an Oldham coupling mechanism. It is explanatory drawing of the operation | movement which an output shaft rotates via an eccentric ring | wheel by rotation of a rotor. It is explanatory drawing of the operation | movement which an output shaft rotates via an eccentric ring | wheel by rotation of a rotor. It is explanatory drawing of the operation | movement which an output shaft rotates via an eccentric ring | wheel by rotation of a rotor. It is explanatory drawing of the operation | movement which an output shaft rotates via an eccentric ring | wheel by rotation of a rotor. It is a cross-sectional side view which shows another example of the speed up gears of this invention. It is the elements on larger scale of FIG. It is X-X 'sectional drawing of FIG. It is sectional drawing which shows the state which the internal gear of a rotor and a fixed external gear mesh in the right end part of a fixed external gear. FIG. 14 is a cross-sectional view showing both the rotating wheel and the internal gear in FIG. 13. It is explanatory drawing of the operation | movement which an output shaft rotates via a rotor and an eccentric ring | wheel by rotation of a rotating wheel. It is explanatory drawing of the operation | movement which an output shaft rotates via a rotor and an eccentric ring | wheel by rotation of a rotating wheel. It is explanatory drawing of the operation | movement which an output shaft rotates via a rotor and an eccentric ring | wheel by rotation of a rotating wheel. It is a cross-sectional side view which shows another example of the speed up gears of this invention. It is a cross-sectional side view showing an example of a two-stage type speed increaser in which the speed increaser of the present invention is connected in two stages. It is a top view which shows an example of the 3 step | paragraph type | formula gear box which connected the gear box of this invention to 3 steps | paragraphs. It is a conceptual diagram which shows an example of the electric power generating apparatus of this invention which has the gearbox of this invention in a power transmission part. It is a conceptual diagram which shows another example of the electric power generating apparatus of this invention which has the gearbox of this invention in a power transmission part.

  Hereinafter, the present invention will be described in detail with reference to the drawings, but the present invention is not limited to the illustrated one.

  FIG. 1 is a cross-sectional side view showing an example of a speed increaser according to the present invention. In FIG. 1, 1 is a speed increaser of the present invention, 2 is an input shaft, 3 is an output shaft, 4 is a base frame, 5 is a bearing, 6 is a fixed external gear, 7 is a rotor, 8 is an eccentric wheel, 9 Is an internal gear, G is an installation surface, and the speed increaser 1 is installed on an appropriate installation surface G via a base frame 4.

  As shown in the figure, the input shaft 2 and the output shaft 3 are rotatably supported by the base frame 4 by bearings 5, 5, 5,. On the other hand, the fixed external gear 6 is fixed to the base frame 4. A through-hole 6h that passes through the fixed external gear 6 in the axial direction is provided at the center of the fixed external gear 6, and the output shaft 3 passes through the inside of the through-hole 6h. The center position of the fixed external gear 6 is concentric with the axis of the output shaft 3.

  An eccentric ring 8 is supported inside the rotor 7 via a bearing 5 so as to be slidably rotatable. The bearing 5 inside the rotor 7 constitutes a bearing portion that supports the eccentric ring 8 so as to be slidably rotatable. doing. The eccentric ring 8 is coupled to the output shaft 3 and rotates integrally with the output shaft 3 around the axis of the output shaft 3, but the center thereof is eccentric with respect to the axis of the output shaft 3. An internal gear 9 is provided inside the rotor 7, and a part of the internal gear 9 meshes with a part of the fixed external gear 6. The rotor 7 revolves while rotating around the fixed external gear 6 by rotating while meshing a part of the internal gear 9 with the fixed external gear 6.

  Reference numeral 10 denotes an intermediate node, 11 denotes a drive plate, and 12 denotes a fixing member that couples the drive plate 11 and the input shaft 2. The convex portion 7a, the intermediate joint 8, and the drive plate 9 provided on the side surface of the rotor 7 on the input shaft 2 side constitute an Oldham coupling mechanism as a rotation transmission mechanism, as will be described later. Is transmitted to the rotor 7 through this rotation transmission mechanism.

  FIG. 2 is a partially enlarged view of FIG. In FIG. 2, 6g shows the teeth of the fixed external gear 6, and 9g shows the teeth of the internal gear 9, respectively. As shown in the figure, the teeth 9g of the internal gear 9 and the teeth 6g of the fixed external gear 6 are in mesh with each other (upper part in FIG. 2), and the rotor 7 has a part of the teeth 9g of the internal gear 9. It rotates around the fixed external gear 6 while meshing with a part of the teeth 6g of the fixed external gear 6, and revolves while rotating around the fixed external gear 6. Reference numeral 10b denotes a concave portion provided on the side surface of the intermediate joint 10 on the rotor 7 side, and the convex portion 7a of the rotor 7 is slidably fitted into the concave portion 10b, which will be described later.

  The speed increaser 1 of the present invention is configured as described above, and the rotor 7 is a bearing portion that supports the eccentric wheel 8 so as to slide and rotate along the axial direction of the output shaft 3. A bearing 5 and an internal gear 9 that meshes with the fixed external gear 6 are provided. Further, since the rotor 7 is coupled to the input shaft 2 via the intermediate joint 10, the drive plate 11, and the fixed member 12, the rotor 7 rotates when the input shaft 2 rotates, and the rotor 7 has its internal gear. By rotating around the fixed external gear 6 while rotating a part of 9 with the fixed external gear 6, the eccentric wheel 8 slidably supported by the bearing 5 in the rotor 7 rotates. As a result, the output shaft 3 connected to the eccentric ring 8 rotates. At this time, as described above, the rotation of the input shaft 2 is accelerated and transmitted to the output shaft 3 according to the gear ratio which is the ratio of the number of teeth of the fixed external gear 6 and the number of teeth of the internal gear 9. become. Incidentally, if the gear ratio of the fixed external gear 6 and the internal gear 9 is 2: 3, the rotation of the input shaft 2 is tripled, and if it is 1: 2, the rotation of the input shaft 2 is quadrupled. Thus, it is transmitted to the output shaft 3.

  3 is a cross-sectional view taken along line X-X ′ in FIG. 2. As shown in FIG. 3, an internal gear 9 is provided inside the rotor 7. In the state shown in the figure, the internal gear 9 meshes with the fixed external gear 6 at the upper portion thereof. 6g is a tooth of the fixed internal gear 6, and 9g is a tooth of the internal gear 9, but it is omitted and only the outline of the tooth tip is shown. 6h is a through-hole penetrating the fixed external gear 6 as described above. Reference numeral 3 c denotes an axis of the output shaft 3, which coincides with the center of the fixed external gear 6.

  4 is a cross-sectional view taken along the line Y-Y 'in FIG. 2, and the output shaft 3 and its axis 3c are also shown for convenience. As shown in FIG. 4, the eccentric ring 8 is supported inside the rotor 7 through a bearing 5 so as to be slidably rotatable. 8 c is the center of the eccentric ring 8, and the center 8 c of the eccentric ring 8 is eccentric from the axis 3 c of the output shaft 3 by a distance e. As a result, when the rotor 7 rotates around the shaft center 3c, the rotational force passes through the center 8c of the eccentric wheel 8 from the shaft center 3c and the moment having the length of the arm as the length of the arm. Thus, it is efficiently transmitted to the output shaft 3. As a result, the rotation of the input shaft 2 is increased and efficiently transmitted to the output shaft 3.

  FIG. 5 is an exploded view of the Oldham coupling mechanism including the convex portion 7 a of the rotor 7, the intermediate joint 10, and the drive plate 11. As shown in the figure, convex portions 7a and 7a are provided at the end of the rotor 7 with an interval of 180 degrees from each other. On the side surface of the intermediate joint 10 on the rotor 7 side, the convex portions 7a and 7a Concave portions 10b and 10b are provided at opposite positions at an interval of 180 degrees. Concave portions 10a and 10a are also provided on the side surface of the intermediate joint 10 on the drive plate 11 side with an interval of 180 degrees, but their positions are shifted by 90 degrees from the grooves 10b and 10b. 10a and the recesses 10b and 10b are in a positional relationship orthogonal to each other. Further, the drive plate 11 is provided with convex portions 11a and 11a at a position facing the concave portions 10a and 10a with an interval of 180 degrees therebetween.

  In the Oldham coupling mechanism, the convex portions 7a and 7a of the rotor 7 are fitted to the concave portions 10b and 10b of the intermediate node 10, and the convex portions 11a and 11a of the drive plate 11 are fitted to the concave portions 10a and 10a of the intermediate node 10. Assembled by. Since the convex portions 7a and 7a and the convex portions 11a and 11a are slidably movable in the concave portions 10b and 10b and the concave portions 10a and 10a, respectively, the input shaft 2 is rotated and the rotor 7 is rotated. When the rotor 7 drive plate 11 is moved in any direction of the direction connecting the recesses 10a and 10a and the direction connecting the recesses 10b and 10b shifted by 90 degrees from the rotor 7 drive plate 11, the movement of the projection 7a 7a and the convex portions 11a and 11a are absorbed by sliding movement in the concave portions 10b and 10b and the concave portions 10a and 10a, respectively, and the center of the drive plate 11, that is, the input shaft 2 does not move. By using the Oldham coupling mechanism as described above, there is an advantage that the rotation of the input shaft 2 whose axis does not move can be efficiently transmitted to the rotor 7 whose center moves with the rotation.

  In the illustrated example, the convex portions 7a and 7a, the concave portions 10a, 10a, and 10b and 10b, and the convex portions 11a and 11a are two pairs of convex portions or linearly arranged with an interval of 180 degrees. Although these are formed as recesses, it is of course possible to extend a pair of projections or recesses to form one continuous projection or recess. In addition, since the convex portions and the concave portions may be fitted to each other and slidable, it goes without saying that the relationship between the concave portions of the convex portions may be opposite to that shown in the drawing. That is, the intermediate joint 10 has a first convex portion or concave portion on the surface facing the drive plate 11, and a second convex portion or concave portion on the surface facing the rotor 7, and the first convex portion or concave portion and the first convex portion The two convex portions or concave portions are in a positional relationship orthogonal to each other, and the drive plate 11 has a third convex portion or concave portion that is slidably fitted to the first convex portion or concave portion of the intermediate node, The rotor 7 only needs to have a fourth protrusion or recess that is slidably fitted to the second protrusion or recess of the intermediate node.

  Note that it is desirable to provide an appropriate bearing mechanism on the contact surface where the convex portion and the concave portion are fitted, so that the convex portion and the concave portion which are fitted to each other can slide smoothly. Examples of the bearing mechanism that can be used include a linear flat roller bearing, a dry bearing, and an oil-impregnated bearing. These bearing mechanisms are at least one of the first to fourth protrusions or recesses described above. By providing the two, the sliding movement between the rotor 7, the intermediate joint 10, and the drive plate 11 can be performed more smoothly, and the rotational force of the input shaft 2 can be transmitted to the rotor 7 more efficiently.

  The rotation transmission mechanism that transmits the rotation of the input shaft 2 to the rotor 7 is not limited to the Oldham coupling mechanism described above, and the rotation of the input shaft 2 is allowed to rotate even if the rotation shaft of the rotor 7 is eccentric with respect to the input shaft 2. Any mechanism may be employed as long as the mechanism can transmit to the sensor. For example, it is possible to use a flexible shaft coupling mechanism such as a rubber shaft coupling mechanism or a diaphragm shaft coupling, but it is preferable to use an Oldham coupling mechanism from the viewpoint of reducing the loss of transmitted rotational force.

  Next, operation | movement of the gearbox 1 of this example is demonstrated using FIGS. 6 to 9, (a) in each figure shows the rotation of the input shaft 2 while the rotor 7 meshes the teeth 9 g of the internal gear 9 with the teeth 6 g of the fixed external gear 6. (B) in each figure shows the movement of the eccentric ring 8 together with the movement of the rotor 7, and (c) in each figure shows the output shaft 3 at that time. Shows exercise. For convenience, the tooth 9g of the internal gear 9 and the tooth 6g of the fixed external gear 6 are shown only by the outline of the tooth tip, and the output shaft 3 is also shown in FIG.

  As shown in FIG. 6A to FIG. 9A, when the rotor 7 rotates around the fixed external gear 6 while meshing a part of the internal gear 9 with the fixed external gear 6, As shown in (b), the eccentric ring 8 supported so as to be slidably rotatable inside the rotor 7 rotates around the axis 3c of the output shaft 3 in the direction of the arrow in the figure, and as a result, each figure (C), the output shaft 3 coupled to the eccentric ring 8 also rotates in the direction of the arrow in the figure. At this time, as shown in (b) of each figure, the center 8c of the eccentric ring 8 is eccentric by the distance e described above from the center of rotation of the eccentric ring 8, that is, the axis 3c of the output shaft 3. The rotational force applied to the eccentric wheel 8 by the shaft 7 is efficiently transmitted to the output shaft 3 as a moment having the distance from the shaft center 3c to the outer periphery of the eccentric wheel 8 through the center 8c of the eccentric wheel 8 as the arm length. Will be. Thereby, in the speed increaser 1 of this invention, efficient speed increase is possible from a low speed area to a high speed area.

  FIG. 10 is a cross-sectional side view showing another example of the speed increaser 1 of the present invention, and the same reference numerals are given to the same members as before. The speed increaser 1 of the present example uses a rotating wheel 13, an internal gear 14, and an external gear 15 as a rotation transmission mechanism that transmits the rotation of the input shaft 2 to the rotor 7, instead of the Oldham coupling mechanism. This is different from the gearbox 1 shown in FIG. That is, the input shaft 2 is coupled with a rotating wheel 13 that rotates around the axis of the output shaft 3 as the input shaft 2 rotates, and a cylindrical portion that protrudes toward the output shaft 3 of the rotating wheel 13. Is provided with an internal gear 14, and an outer gear 15 is provided on the outer peripheral surface of the rotor 7. The external gear 15 is partially engaged with the internal gear 14. , And transmitted to the rotor 7 via the internal gear 14 and the external gear 15. In the speed increaser 1 of this example, since the axis of the input shaft 2 coincides with the axis of the output shaft 3, the rotating wheel 13 is concentrically coupled to the input shaft 2 via the fixing member 12. As a result, the input shaft 2 rotates around the axis of the output shaft 3, but the input shaft 2 and the output shaft 3 do not coincide with each other. The rotating wheel 13 may be supported so as to be rotatable about the axis of the output shaft 3 and the rotation of the input shaft 2 may be transmitted to the rotating wheel 13 through an appropriate shaft coupling.

  FIG. 11 is a partially enlarged view of FIG. In FIG. 11, 14 g indicates the teeth of the internal gear 14, and 15 g indicates the teeth of the external gear 15. As shown in the figure, the teeth 14g of the internal gear 14 of the rotating wheel 13 and the teeth 15g of the external gear 15 of the rotor 7 are partially engaged (lower part in FIG. 11), and as the input shaft 2 rotates. When the rotating wheel 13 rotates, the rotation is transmitted to the rotor 7 via the internal gear 14 and the external gear 15, and the rotor 7 revolves while rotating around the fixed external gear 6. At this time, the external gear 15 of the rotor 7 revolves while rotating around the fixed external gear 6, but the locus of the point farthest from the axis 3 c of the output shaft 3 of the external gear 15 is the axis of the output shaft 3. Since a circle centered on the center 3c is drawn, the rotor 7 is rotated by providing the internal gear 14 having a radius corresponding to the radius of the circle on the rotating wheel 13 concentrically with the axis 3c of the output shaft 3. Even if the gear 15 revolves while rotating around the fixed external gear 6, the internal gear 14 of the rotating wheel 13 and the external gear 15 of the rotor 7 always mesh with each other while changing the meshing position. The rotation of the rotating wheel 13 accompanying the rotation of the shaft 2 can be continuously transmitted to the rotor 7 via the internal gear 14 and the external gear 15.

  This point will be described in detail with reference to the drawings as follows. 12 is a cross-sectional view taken along the line X-X ′ of FIG. 11. In FIG. 12, 3 c is the axis of the output shaft 3, and 7 c is the center of the rotor 7. The center 7c of the rotor 7 coincides with the center 8c of the eccentric wheel 8 described above, and is eccentric from the axis 3c of the output shaft 3 by a distance e. In the state shown in FIG. 12, the internal gear 9 of the rotor 7 meshes with the fixed external gear 6 at the top of the fixed external gear 6 in the figure, and the point P at the lowest end of the external gear 15 provided on the rotor 7 in the figure. Is the point farthest from the axis 3c of the output shaft 3 of the external gear 15. When the distance from the center 7c of the rotor 7 to the tip of the tooth 15g of the external gear 15 provided on the outer peripheral surface of the rotor 7, that is, the radius of the external gear 15, is r, the distance from the axis 3c to the point P is e + r. When the rotor 7 revolves while rotating around the fixed external gear 6 while meshing the internal gear 9 with the fixed external gear 6, the positional relationship between the rotor 7 and the fixed external gear 6 changes and the axis of the output shaft 3 changes. The point P farthest from 3c also moves, but the distance from the axis 3c of the output shaft 3 to the point P is always e + r and does not change.

  That is, for example, as shown in FIG. 13, the rotor 7 revolves from the state shown in FIG. 12 while rotating around the fixed external gear 6, and the internal gear 9 of the rotor 7 When the stationary external gear 6 is in meshing state, the leftmost point P of the external gear 15 of the rotor 7 in the figure is the point farthest from the axis 3c of the output shaft 3. The axis of this point P The distance from 3c is also e + r. Thus, the distance to the point P that is farthest from the axis 3c of the output shaft 3 is such that the rotor 7 rotates around the fixed external gear 6 and the positional relationship between the rotor 7 and the fixed external gear 6 is the same. Even if it changes, it is e + r. That is, assuming a circle C having a radius e + r around the axis 3c of the output shaft 3, even if the rotor 7 revolves while rotating around the fixed external gear 6, the axis of the external gear 15 of the rotor 7 The point P farthest from the center 3c is always inscribed in the circle C. Therefore, as shown in FIG. 14, the internal gear 14 having a radius corresponding to the distance e + r is connected to the shaft center 3 c of the output shaft 3 such that the teeth 14 g partially mesh with the teeth 15 g of the external gear 15 of the rotor 7. By providing the rotating wheel 13 concentrically, even if the rotor 7 rotates and the external gear 15 revolves while rotating around the fixed external gear 6, the internal gear 14 and the external gear 15 always mesh with each other, The rotation of the rotating wheel 13 accompanying the rotation of the input shaft 2 can be continuously transmitted to the rotor 7.

  Next, operation | movement of the gearbox 1 of this example is demonstrated using FIGS. 15-17. 15 to 17, (a) in each figure corresponds to a cross-sectional view taken along the line XX ′ in FIG. 11, and the rotor 7 is rotated by the rotation of the rotating wheel 13 accompanying the rotation of the input shaft 2. The movement of rotating around the fixed external gear 6 while meshing the teeth 9g of the 9 with the teeth 6g of the fixed external gear 6 is shown. Moreover, (b) of each figure is equivalent to YY 'sectional drawing in FIG. 11, and has shown the motion of the eccentric ring | wheel 8 accompanying rotation of the rotating wheel 13 with the motion of the rotor 7, (c) of each figure. ) Shows the movement of the output shaft 3 at that time.

  As shown in (a) of each figure, when the rotating wheel 13 rotates in the direction of the arrow in the drawing as the input shaft 2 rotates, the rotation causes the internal gear 14 of the rotating wheel 13 and the external gear 15 of the rotor 7 to rotate. The rotor 7 rotates around the fixed external gear 6 while meshing a part of the internal gear 9 with the fixed external gear 6. With the rotation of the rotor 7, as shown in each figure (b), the eccentric wheel 8 supported so as to be slidably rotatable inside the rotor 7 is an arrow in the figure centering on the axis 3 c of the output shaft 3. As a result, as shown in (c) of each figure, the output shaft 3 coupled to the eccentric ring 8 also rotates in the direction of the arrow in the figure. At this time, as shown in (b) of each figure, since the center 8c of the eccentric ring 8 is eccentric from the axis 3c of the output shaft 3 by the distance e described above, the rotational force applied to the eccentric ring 8 by the rotor 7 is Thus, the distance from the shaft center 3c to the outer periphery of the eccentric wheel 8 through the center 8c of the eccentric wheel 8 becomes a moment having the length of the arm and is efficiently transmitted to the output shaft 3. Further, since the rotation of the input shaft 2 is transmitted to the rotor 7 through the gear mechanism of the internal gear 14 of the rotating wheel 13 and the external gear 15 of the rotor 7, energy due to sliding friction as in the case of using the Oldham coupling mechanism. There is little loss, and more efficient speed increase is possible from low speed to high speed.

  Since the speed increaser 1 of this example is configured as described above, when the input shaft 2 rotates, the rotation is transmitted to the rotor 7 via the rotating wheel 13, and the rotor 7 is connected to the internal gear 9. By rotating around the fixed external gear 6 while revolving around a portion of the fixed external gear 6, the eccentric wheel 8 supported by the bearing 5 so as to be slidably rotatable is rotated. As a result, the output shaft 3 coupled to the eccentric ring 8 rotates. At this time, the rotation of the input shaft 2 is accelerated and transmitted to the output shaft 3 according to the gear ratio which is the ratio of the number of teeth of the fixed external gear 6 and the number of teeth of the internal gear 9. The same as in the example shown above. Further, in the speed increaser 1 of this example, the rotation of the input shaft 2 is increased according to the ratio of the number of teeth of the internal gear 14 of the rotating wheel 13 and the number of teeth of the external gear 15 of the rotor 7. Since it is transmitted to the rotor 7, a further speed increase rate can be expected.

  FIG. 18 is a cross-sectional side view showing still another example of the speed up gear 1 of the present invention. The speed increaser 1 of this example has speed increasing mechanisms such as a fixed external gear 6, a rotor 7, an eccentric wheel 8, and a rotating wheel 13 on both sides along the axial direction of the output shaft 3. The members located on both sides of the output shaft 3 are the same on the left and right, but for convenience, the reference numerals of the members located on the right side along the axial direction of the output shaft 3 are marked with “′” and located on the left side. These are shown separately from corresponding members. However, the rotor 7 and the eccentric wheel 8 positioned on the left side along the axial direction of the output shaft 3 and the rotor 7 'and the eccentric wheel 8' positioned on the right side along the axial direction of the output shaft 3 Are 180 degrees different. Further, in this example, the output shaft 3 is a hollow cylinder, and the left and right rotors 7 and 7 'and the portions corresponding to the hollow portions of the hollow cylinders of the eccentric wheels 8 and 8' are also provided with holes 7h, 7'h, 8h and 8′h are provided. A connecting shaft 16 is inserted inside the hollow cylinder and the holes 7h, 7'h, 8h, 8'h which are output shafts, and the left rotating wheel 13 and the right rotating wheel 13 'are mutually connected by the connecting shaft 16. It is connected to. Reference numeral 17 denotes a gear for taking out the rotation of the output shaft 3 to the outside.

  In such a speed increaser 1, when the input shaft 2 and / or the input shaft 2 ′ is rotated, the rotating wheels 13 and 13 ′ are rotated around the axis 3 c of the output shaft 3 along with the rotation. Is transmitted to the rotors 7 and 7 'via the internal gears 14 and 14' and the external gears 15 and 15 ', respectively. Thereby, the rotors 7 and 7 ′ revolve while rotating around the fixed external gears 6 and 6 ′ while meshing the internal gears 9 and 9 ′ with the fixed external gears 6 and 6 ′, respectively. 8 'is eccentrically rotated around the axis 3c of the output shaft 3, and the output shaft 3 is rotated. At this time, the rotor 7 and the eccentric wheel 8 located on the left side along the axial direction of the output shaft 3 and the rotor 7 ′ and the eccentric wheel 8 ′ located on the right side have different rotational phases by 180 degrees. The eccentric force generated with the eccentric rotation is canceled out, and the advantage that the generation of vibration and noise can be suppressed is obtained.

  Both the input shaft 2 and the input shaft 2 'may be rotated by an external force, or only one of them may be rotated by an external force. Since the rotating wheel 13 and the rotating wheel 13 ′ are connected by the connecting shaft 16 as described above, when either the input shaft 2 or the input shaft 2 ′ is rotated, the rotating wheel 13 is rotated along with the rotation. And both of the rotating wheels 13 'rotate.

  FIG. 18 shows the case where the rotating wheel 13 is used as the rotation transmitting mechanism. However, the same applies to the case where the rotation transmitting mechanism is an Oldham coupling mechanism, and instead of the rotating wheels 13, 13 ′, the driving plate 11 is used. , 11 ′ and intermediate nodes 10, 10 ′ are arranged on both sides in the axial direction of the output shaft 3, and the drive plates 11 and 11 ′ are connected to the hollow portion of the hollow cylinder which is the output shaft 3, What is necessary is just to connect with the connecting shaft which penetrates the hole provided in each of the rotors 7 and 7 'and the eccentric rings 8 and 8'. Even if the rotation transmission mechanism is an Oldham coupling mechanism, the rotors 7 and 7 ′ and the rotor 7 and the eccentric wheel 8 on the left side and the rotor 7 ′ and the eccentric wheel 8 ′ on the right side are different from each other by 180 degrees. Of course, the eccentric rings 8 and 8 'are arranged.

FIG. 19 is a cross-sectional side view showing an example of a two-stage gearbox in which the gearbox 1 of the present invention shown in FIG. 1 is connected in two stages. That is, as shown in FIG, front output shaft 3 ₁ speed increaser 1 ₁ (left side in the figure) is, via an appropriate fitting 18, subsequent input shaft 2 of the speed increaser 1 ₂ (right side in the figure) ₂ is combined. Any gear ratio between the fixed external gear 6 and the internal gear 9 in the speed increasing device 1 ₁ and the rear stage speed increaser 1 ₂ of the preceding stage is 1: 2, respectively 4 times the rotational speed at each stage Since the speed increase can be obtained, the speed increase of 4 × 4 = 16 times can be obtained in the entire speed increaser of this example connected in two stages. Thus, the speed increaser 1 of the present invention can realize a large speed increase rate by being connected in multiple stages. Moreover, since the speed increaser 1 of this invention is simple in structure, it can be comprised compactly without being bulky and is suitable for connecting in multiple stages. Note that the number of connecting stages is not limited to two, but may be three or more and any number of stages. Further, different gear ratios of the present invention may be connected to the front stage and the rear stage by changing the gear ratio between the internal gear 9 and the fixed external gear 6 or changing the structure.

FIG. 20 is a plan view showing an example of a three-stage gearbox in which the gearbox 1 of the present invention shown in FIG. 18 is connected in three stages. That is, as shown in FIG., The gear 17 ₁ which is attached to the output shaft 3 ₁ speed increaser 1 ₁ of the first stage is the second stage of the speed increaser 1 ₂ of the input shaft 2 _second gear 19 attached to coupled with _2, similarly, the second stage of the speed increaser 1 _second output shaft 3 _second gear 17 ₂ which is attached to is attached to the input shaft 2 ₃ speed increaser 1 ₃ of the third stage gear 19 ₃ . Also the gear ratio of the fixed external gear 6 and the internal gear 9 is one in speed increaser 1 ₁ to 1 ₃ of each stage 1: 2, is accelerated in the rotational speed of each of the four times in each stage to give Therefore, the speed increaser of the present example connected in three stages can obtain a speed increase of 4 × 4 × 4 = 64 times. Further, the number of gear 17 ₁ and 17 _2, respectively, by more than the number of teeth of the gear 19 ₂ and 19 _3, subsequent increase of further accelerating the rotation of the output shaft of the preceding speed increaser It is possible to transmit to the speed machine, and it is possible to further increase the speed increase rate of the entire speed increaser of the present invention connected in multiple stages.

  Note that the mechanism for transmitting the rotation of the output shaft 3 in the upstream gearbox 1 to the input shaft 2 of the downstream gearbox 1 is not limited to that shown in FIG. 20, for example, the output shaft in the upstream gearbox 1. The rotation of the gear 17 attached to 3 may be transmitted to the gear 19 attached to the input shaft 2 of the speed-up gear 1 at the subsequent stage via a chain or the like.

FIG. 21 is a conceptual diagram showing an example of the power generator of the present invention having the speed increaser 1 of the present invention in the power transmission unit. In FIG. 21, 20 is water, that is, a water wheel that rotates by the energy of the water flow, 21 is a power transmission unit, 22 is a generator, 23 is a coupling unit, and 24 is a clutch. The rotation of the water turbine 20 is transmitted to the power transmission unit 21 via the coupling unit 23 and is increased by the speed increasers 1 ₁ and 1 _{2 of} the present invention connected to the two stages provided in the power transmission unit 21. Then, it is transmitted to the rotor of the generator 22 to generate power.

FIG. 22 is a conceptual diagram showing another example of the power generator of the present invention having the speed increaser 1 of the present invention in the power transmission unit. In FIG. 22, 25 is a windmill that rotates by the energy of the atmosphere, that is, wind, 21 is a power transmission unit, 22 is a generator, 23 is a coupling unit, and 24 is a clutch. The rotation of the windmill 25 is transmitted to the power transmission unit 21 via the coupling unit 23, and the speed increasers 1 ₁ , 1 ₂ , 1 _{3 of} the present invention connected to the three stages provided in the power transmission unit 21. Is transmitted to the rotor of the generator 22 to generate power.

  The energy that can be used by the power generation device of the present invention is not limited to the energy that water or air has. It may be the energy of water vapor obtained by converting heat generated by thermal power or nuclear power, or the energy of other fluids. Further, the speed increaser of the present invention can efficiently increase the speed even if the force for rotating the input shaft 2 is small. Therefore, the use of flowing water with a low energy such as a water channel or a water channel with a small head is used. It is suitable for use in hydroelectric power generators and wind power generators installed in areas where strong winds cannot be expected. In addition, used water flow and steam in normal hydroelectric power generation facilities, thermal power plants, and nuclear power generation facilities are used for turbines and turbines. It is a very good useful speed increaser that can be reused as an energy source for rotating the motor, and can use the energy of various fluids without waste.

  According to the speed increaser of the present invention, since the rotation of the input shaft can be efficiently increased and transmitted to the output shaft with a simple and compact structure, it is extremely useful in all fields that require speed increase. . In addition, according to the power generation device provided with the gearbox of the present invention in the power transmission unit, not only large energy of the fluid but also relatively small energy can be used for power generation without waste. Is highly useful and has excellent industrial applicability.

DESCRIPTION OF SYMBOLS 1 Speed increaser 2 Input shaft 3 Output shaft 3c Output shaft axis 4 Base frame 5 Bearing 6 Fixed external gear 7 Rotor 8 Eccentric ring 9 Internal gear 10 Intermediate node 11 Drive plate 12 Fixing member 13 Rotating ring 14 Internal gear 15 Out Gear 16 Connection shaft 17 Gear 18 Joint 19 Gear 20 Water wheel 21 Power transmission part 22 Generator 23 Coupling part 24 Clutch 25 Windmill G Installation surface e Eccentric distance r Radius of external gear provided in rotor

Claims (11)

  An input shaft rotated by an external force; a base frame; an output shaft rotatably supported by the base frame; a fixed external gear fixed to the base frame concentrically with the axis of the output shaft; An eccentric that is eccentric with respect to the axis of the output shaft, is coupled to the output shaft, and rotates integrally with the output shaft around the axis of the output shaft; A speed increasing device comprising: a rotor having a bearing portion to be supported on; and a rotor having an internal gear meshing with the fixed external gear; and a rotation transmission mechanism for transmitting rotation of the input shaft to the rotor.   The speed increaser according to claim 1, wherein the rotation transmission mechanism is an Oldham coupling mechanism.   The Oldham coupling mechanism has a drive plate coupled to the input shaft, and an intermediate node interposed between the drive plate and the rotor, and the intermediate node is a surface facing the drive plate The first convex portion or the concave portion, and the second convex portion or the concave portion on the surface facing the rotor. The first convex portion or the concave portion and the second convex portion or the concave portion are The drive plate has a third protrusion or recess that is slidably fitted to the first protrusion or recess, and the rotor has the second protrusion. The speed increaser according to claim 2, further comprising a fourth convex portion or a concave portion that is slidably fitted to the portion or the concave portion.   The speed increaser according to claim 3, wherein a bearing mechanism is provided in at least one of the first to fourth convex portions or the concave portions.   The rotation transmission mechanism is a rotating wheel having an external gear provided on the rotor and an internal gear meshing with the external gear, and is connected to the input shaft, and the rotation of the input shaft is caused by the rotation of the input shaft. The speed increaser according to claim 1, further comprising a rotating wheel that rotates about an axis.   The fixed external gear, the eccentric wheel, the rotor, and the rotation transmission mechanism are provided on both sides along the axial direction of the output shaft, and the phase of the eccentric rotation of the rotor and the eccentric wheel on both sides is 180. The speed increaser in any one of Claims 1-5 which differ in degree.   The speed increaser according to any one of claims 1 to 6, wherein a gear ratio of the fixed external gear and the internal gear of the rotor is 1: 2 or 2: 3.   It is a multi-stage type gearbox that consists of two or more gearboxes, and the output of the first gearbox is the input to the second gearbox. As described above, the output shaft of the speed-up gear in the preceding stage and the input shaft of the speed-up gear in the subsequent stage are connected, and each speed-up gear is a speed-up gear according to any one of claims 1 to 7. A multi-stage gearbox characterized by   A speed increasing mechanism for increasing the rotation of the output shaft of the front speed increaser and transmitting it to the input shaft of the rear speed increaser is provided between the front speed increaser and the rear speed increaser. Item 9. The multistage speed increaser according to Item 8.   It has a main axis | shaft rotated with the energy which a fluid has, a generator, and the power transmission part which transmits rotation of the said main axis | shaft to the said generator, The said power transmission part is any one of Claims 1-9. A power generator characterized by comprising a step-up gear.   The power generation device according to claim 10, wherein the fluid is water, air, or water vapor.

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