JP2009092080A - Variable tooth-number geared continuously variable speed transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a device which reduces a power transmission loss, and can continuously perform the acceleration/deceleration control of an input/output ratio having a simple structure and lower manufacturing cost in a variable power transmission device, and to solve the problems that the variable power transmission device of a conical type or a disk type is required to convert from a friction transmission method into a gear transmission method which is a reliable power transmission means, an amount corresponding to a surplus is absorbed when it is not an intejer, and also the gear engaged with the opposite gear is continuously smoothly moved when gear-changed. <P>SOLUTION: A method solved by a stepless topological pattern structure having a V-shaped continuous tooth groove on a conical and a disk surface, and a round tooth groove for rounding the tooth number surplus is invented in order to take measures to cope with the situation. Thus, one embodiment contemplates application for the continuously variable gear device having the lower transmission loss, the simple structure, and easy manufacturing by combining the gears of this device. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

The present invention relates to a mechanism for realizing a change from a friction transmission system to a gear transmission system with reliable power transmission in a conventional conical or disk type variable speed power transmission device.

In the prior art related to the conical type continuously variable transmission, there is a continuously variable transmission mechanism using a conical roller, and in order to solve the power transmission loss due to such a friction transmission system, as a means of aiming for power transmission by changing the number of teeth, There is a gear type stepless (continuous) power transmission structure (see Patent Document 1).

Patent Publication 2000-240738 Variable Gear Number Gear Transmission

As described in Patent Document 1, in the “SURIBACHI pattern” (upper right of FIG. 9), “one tooth missing occurs, or there is a tooth in which the tooth arrangement and the traveling direction are deviated from each other at right angles in each sector. In addition to the problem that “change occurs”, the tooth shape is not continuously cut with respect to the surface of the disk, and therefore, the gears of the mating gears cannot move smoothly and get caught, and the gears may be damaged. In addition, in order to eliminate the remainder of the number of teeth with an intermediate diameter that does not become an integer, some tooth crests are deleted to ensure play, but this further enlarges the remainder and newly increases the possibility of uneven rotation. . Furthermore, there are many problems such as speed deviation being not corrected because the direction of the tooth profile that approximates the mesh cut on the surface of the disk is one direction.

Since the number of teeth of the gear must be an integer value, it has been difficult to realize such a continuous continuously variable transmission. However, since the change in diameter and size of the cone / disk is continuous, this feature is used to absorb the remainder corresponding to the number of teeth that do not become an integer, and to smoothly control the shifting by moving the gears of the mating counterpart smoothly. If possible, it is possible to realize a simple and reliable gear transmission type continuously variable transmission, and this is the subject of the present invention.

First, the gear wheel pitch width (tooth gap width + tooth thickness) is fixed, the phase of the tooth profile (Fig. 6) corresponding to the change in diameter and size of the cone (including the disk) is aligned, and the gear shift (gear change) ) Realizes the meshing function of the gear by the easy-to-operate V-shaped continuous tooth groove pattern (Figs. 6-611 to 617 based on Fig. 6-604).

Furthermore, this structure allows the remaining number of teeth at the time of shifting to be gathered on a continuous tooth gap connecting folded corner (FIG. 6-603), which is formed into a plurality of inverted V-shaped continuous tooth groove patterns (FIG. 6-605 is a basic shape). ) And a triangular buffer tooth groove (FIGS. 4-411 to 419), the remainder of the number of teeth is 0.5 pitch or less (if it exceeds, the remainder is divided: FIG. 4 421-a / b to 429-a / b) A round tooth gap structure (FIG. 4) having a function of absorbing and rounding and always maintaining the meshing with the counter gear is realized as a continuously variable gear type continuously variable transmission function called a “continuous topological tooth pattern”. .

It is easy to change gears even during rotation because the tooth profile positions and phases of all teeth (corresponding to all 37 steps in the example) corresponding to the change in diameter of the cone (disk) are aligned. In addition, there is a power transmission device that can control the speed of input / output ratio steplessly with a large transmission force by the gear mechanism because the pitch change rate is maintained at a diameter size that leaves a remainder in the number of teeth (integer). Is possible.

Furthermore, the structure is simple and the number of parts is remarkably small (in the example of FIGS. 1 and 2, the conventional 37 steps and 37 gears are equivalent to one piece). This is a variable power transmission gear that is energy-saving and environmentally friendly in terms of product lifetime energy costs.

FIGS. 1 and 2 are completed views of a V-shaped continuous tooth gap of a conical (hereinafter also including a disk) gear according to the first and second embodiments of the present invention, and FIGS. FIG. For this reason, the order of appearance of components and the like is reversely shown in FIGS. In these drawings, the same reference numerals may be used for the same components.

The completed drawing of the V-shaped continuous tooth gap of claim 1 is FIG. 1 and FIG. 2, but from FIG. 6, first, the circle pitch width is fixed and the maximum: minimum tooth ratio is 4: 1, the number of teeth. In the range of 12 to 48 (in this open, it becomes a continuously variable gear, but all models of 37 stages are assumed in the simulation: FIGS. 6-601 and 602), so the number of reference teeth that perfectly match every 90 degrees (Equivalent to 10 steps: 12, 16, 20, 24, 28, 32, 36, 40, 44, 48) and position (FIG. 6-601) are set, and the basic shape of the V-shaped continuous tooth space structure (FIG. 6-) 604).

Further, the phase of the middle 27 gears is 90 ° as the starting point, and a meshing diagram in the lower right (1/4) in which the tooth profile position obtained by adding the number of teeth to the left and right 45 degrees is calculated by computer simulation. FIG. 6 is an overlapping view of a letter-shaped continuous tooth groove (FIGS. 6-611 to 617, which are developed from the basic shape of FIG. 6-604). The whole is four times this (Fig. 2), but the principle is the same.

FIG. 3 is a view of the conical continuous topological tooth profile pattern gear of FIG. 2 with the same V-shaped continuous tooth profile cut out from the lower right broken line (FIG. 2-203) and the tooth tip positions of the 10 reference gears. FIGS. 4 and 6 are mapped views, and the tooth number variable switching operation (gear change) is facilitated by a V-shaped continuous tooth profile structure close to vertical as shown in FIGS.

The variable round tooth gap structure of claim 2 will be described with reference to FIGS. 5 and 4. An example of the number of teeth that does not become an integer in a V-shaped continuous tooth profile divided into four (FIG. 5, 5-r37, r38, r39: right) When the tooth tip position during rotation is a small rhombus and the tooth tip position when the counterclockwise rotation is a small square position) exceeds the 4-fold folding line (Fig. 5-501), the number of teeth is left, and the inverted V-shaped continuous Tooth profile position pattern (basic shape: thick dotted line display in FIG. 6-605). If these tooth number surplus values are calculated, from (40-39) ÷ 4 = 0.25 (FIG. 5-i39) from (the nearest reference tooth value to be rounded−the remainder calculating tooth value) ÷ number of divisions (40−38) ÷ 4 = 0.5 (FIG. 5-i 38). When the pitch is 0.5 pitch or less, absorption by rounding is easy, so the excess pitch interval provided near the folding line (FIG. 5-501). The remainder of the number of teeth is absorbed by a part of the corresponding triangular adjustment round tooth gap structure (FIG. 5-417), and the phase is adjusted.

However, when the number of teeth becomes 37, the remainder becomes 0.75 pitch (5-r37 in FIG. 5) and the play angle is large (FIG. 5-503), so the synchronization with the mating counterpart teeth is delayed, and there is a possibility of collision between the tooth tips. is there. Therefore, the tooth profile on the folding line (Fig. 5-505: Fig. 4-402 to 406) is left as the synchronous adjustment separator toothpaste, and there are two play positions (Fig. 5-427-a / b: 9 in total). Dividing into rows (Fig. 4, 421-a / b to 429-a / b), the pitch is reduced to 0.5 pitch or less, the remainder is rounded to facilitate absorption, and the meshing is adjusted. By arranging and processing in FIGS. 2-204, 205, 206, and 207), the meshing of all the gears is established, and the gear number variable gear function is realized.

Strictly speaking, there is no excess or deficiency in the circumference of each diameter, but when the number of teeth becomes excessive, fluctuations occur in the speed change when rounding up to a maximum of 0.5 pitch or less at each of four locations. Therefore, when strict accuracy is required for the gear ratio and rotation angle change during such a shift, or when using at ultra-high speed rotation, care must be taken, but the position during gear change also changes under normal shift operation conditions. Fluctuations are even smaller and the speed ratio itself is changed, so there is no problem.

In addition, as shown in the continuous topological tooth profile pattern (FIG. 3) even when the number of teeth is excessive, the angle θ (FIG. 3-301) of the mating teeth is on a vertical line from the center of the circle (FIG. 3-301). 3-306) The V-shaped continuous tooth profile is inverted. For this reason, the rotation unevenness due to the excessive number of teeth is offset within a quarter turn (90 degrees), and the speed does not change.

The width of the continuous tooth gap (FIG. 3-302) will be described in detail. Since the position of the tooth gap (FIG. 3-303) is inclined (θ degrees: FIG. 3-301) with respect to the vertical of the central axis, the tooth gap width ( FIG. 3-302) = circle pitch of the mating gear (FIG. 3-305) × cos θ + tooth width of the gear (FIG. 3-304) × sin θ. As the distance from the starting points (201-a, b, c, d in FIG. 2) increases, the tooth gap width becomes wider.

Therefore, it is possible to suppress the increase in the tooth gap width by rounding the corners of the four edges of the mating gear, thereby increasing the power transmission force by increasing the meshing area and making the gear change smoother. In order to further increase the power transmission force, the engagement area can be increased by creating a concave curved pocket at the standard number of teeth of the V-shaped continuous tooth gap, and a state maintaining function is also provided. Conversely, the width of the continuous tooth gap is reduced by reducing the tooth width of the mating transmission gear meshing with the conical gear (Fig. 3-304: tooth length measured in the axial direction) within a range in which a reduction in transmission force is allowed. It is also possible to hold down.

Next, FIG. 7 shows an embodiment of a conical gear type parallel shaft continuously variable transmission type power transmission device.
In order to achieve this, the conical gears of claims 1 and 2 are arranged along the rotation axis (FIGS. 7-701 and 703) so that the diameters are opposite to each other (FIGS. 7-702, 704), and gears for transmission and transmission (FIG. 7-705) that can always mesh and move with respect to the tooth tips of which diameter changes in the meantime.

Then, the rotational ratio of the two conical gears (input shaft to output shaft) is continuously variably controlled by automatically or manually changing the position of the transmission / transmission gear from the outside (arrow 708 in FIG. 7). A conical gear type continuously variable transmission type parallel shaft power transmission device having a function can be configured.

In addition, variable speeds equivalent to 37 steps or more are possible between the gear ratios 1 to 4: 4 to 1 of the conical gears of the first and second claims. Conventionally, with a transmission of this scale, 74 (37 × 2) and a complicated meshing mechanism is required, but as shown in FIG.

FIG. 8 shows an embodiment of a conical planetary gear type coaxial continuously variable transmission power transmission device according to an embodiment of claim 4 of the present invention. In order to realize the fourth aspect, the sun gear 1 (FIG. 8-802) is first connected to the original shaft (FIG. 8-801), and the ends of the conical gears described in the first and second aspects are engaged with each other. A plurality of (FIGS. 8-803, 804) are arranged in a planetary gear structure. Next, the sun gear 2 (FIGS. 8-806) is arranged so as to be always meshed with the tooth tip of the conical planetary gear whose diameter changes, and is movable, and is connected so as to be able to transmit rotational force. A planetary gear type coaxial continuously variable transmission type power transmission device that rotates the driven shaft (FIG. 8-807) is constructed. The original shaft and the slave shaft are independent of rotation operation by a coaxial independent rotary bearing (FIG. 8-808).

If the sun gear 1 described above is used as an input shaft for rotational power, the position where the sun gear 2 (FIG. 8-806) meshes with the conical gear (FIG. 8-805-806) is automatically or manually applied from the outside. Thus, it is possible to configure a planetary gear continuously variable transmission type power transmission device having a function of continuously changing the rotational speed on the sun gear 2 side meshing with one of the conical gears. In this explanatory diagram, there are two conical planetary gears, but four or more conical planetary gears are possible to increase the power transmission force.

Industrial applicability

As a field of use of the continuously variable transmission of the present invention, it is used in a power transmission unit between a rotating wind turbine unit and a generator of a lift type wind power generator, thereby reducing the rotational load of the generator in a low wind region. While accelerating natural lift acceleration against unstable wind, it is possible to compensate for the lack of torque and rotate the generator for a longer time to improve power generation efficiency. Also, if it is used as a continuously variable transmission for motors that do not have a speed shift control function or a transmission for an internal combustion engine that continuously controls the rotational output of the prime mover, it will respond to torque increase during initial drive and fluctuations in load. It can be operated with high efficiency.

A side view of a conical gear Continuous stepless topological tooth profile diagram of conical gears as seen from above Interlocking gear angle explanatory diagram superimposed on the portion corresponding to the lower right broken line in FIG. Bottom right (1/4) panoramic view of round tooth gap structure for adjusting the number of teeth Rounded tooth gap structure for enlarged adjustment of the number of teeth (Expanded display with the round tooth gap structure of FIG. 4 superimposed on FIG. 6) V-shaped continuous tooth gap structure diagram (shown in the lower right ¼ calculated by computer simulation of assumed tooth profile positions with 12 to 48 teeth with the same circular pitch width) Conical gear type parallel shaft continuously variable transmission type power transmission device configuration diagram Conical planetary gear type coaxial continuously variable transmission Patent Document 1: Variable Teeth Gear Transmission Diagram

Explanation of symbols

DESCRIPTION OF SYMBOLS 101 Conical gear rotating shaft 102 Conical gear continuous tooth groove bottom 103 Conical gear continuous tooth tip crest 201-a, b, c, d Starting position 203 of conical gear four-part inner continuous tooth groove Cutout range portions 204 to 207 corresponding to FIG. 3 4-fold folding line (round tooth gap position where the number of teeth is rounded off)
2-E001 to E048 Corresponds to outer diameter teeth number 1 to 48 2-I001 to I012 Corresponds to inner teeth number 1 to 301 301 Inclination angle θ of the counter gear meshing with the continuous tooth groove of the conical gear
302 Continuous tooth groove width 303 Continuous tooth groove cut line 304 Tooth gear width (tooth length measured in the axial direction) of the mating gear meshing with the continuous tooth groove
305 Circular pitch width of gear mating with continuous tooth gap (width of tooth gap + tooth thickness)
306 Four-fold folding line 401 of conical gear Four-fold folding lines 402 to 406 Phase adjustment separator teeth 411 to 419 at the time of the remaining number of teeth absorption process Variable round tooth groove (0.1 to 0.5 for number of teeth remaining correction) (Pitch correspondence)
421-a / b to 429-a / b Variable round tooth gap for correction of division of excess number of teeth
(0.5-0.9 pitch compatible)
501 Quadrant folding line 502 Tooth shape surplus assumed tooth profile locus arc (5-r37, 5-r38, 5-r39)
503 Assuming that the number of teeth exceeds 0.5 pitch 504 Assuming that the number of teeth is less than 0.5 pitch 505 Phase adjustment separator tooth gap (corresponding to 0.5 to 0.9 pitch)
601 Gear meshing position with 10 reference teeth (circle indication: number of teeth 12, 16, 20, 24, 28, 32, 36, 40, 44, 48, equivalent to 10 steps)
602 Engagement positions with more than 27 teeth (◇: Displayed when rotating right, □: Displayed when rotating left, Number of teeth 13, 14, 15, 17, 18, 19, 21, 22, 23, 25, 26, 27, (29, 30, 31, 33, 34, 35, 37, 38, 39, 41, 42, 43, 45, 46, 47, equivalent to 27 steps)
603 Continuous tooth gap connection fold line 604 V-shaped connection tooth gap basic pattern structure (basic shape of standard 10 tooth positions)
605 Inverted V-shaped idle tooth groove basic pattern structure (basic form of the assumed tooth profile position of the gear with the remaining number of teeth)
611 to 617 V-shaped continuous tooth groove 701 Input rotation shaft 702 of conical gear type parallel shaft continuously variable transmission type power transmission device Input side conical gear 703 of the present invention Output rotation shaft 704 Output side conical gear 705 of the present invention Movable speed Control and transmission gear (input / output constant speed position)
706 Speed control and transmission gear output shaft deceleration position (assumed position)
707 Speed control and transmission gear output shaft acceleration position (assumed position)
801 Conical planetary gear type coaxial continuously variable transmission power transmission shaft 802 Sun gear 1 (fixed position)
803 Conical planetary gear 1 of the present invention
804 Conical planetary gear 2 of the present invention
805 Position movable sun gear 2 (slave driven deceleration position: assumed position)
806 Position movable sun gear 2 (slave maximum deceleration position)
807 Conical planetary gear type coaxial continuously variable transmission power transmission slave shaft 808 Coaxial independent (original shaft / slave shaft) rotation bearing 809 Rotation bearing

Claims (4)

V-shaped continuous teeth with a constant circular pitch width (tooth gap width + tooth thickness), which is the standard for gears, and the number of teeth continuously changing in proportion to the diameter of the cone (including the disk) A "continuous topological tooth pattern" structure having a groove and a conical (disk) type tooth number variable gear having the structure. In claim 1, when the number of teeth continuously changes in proportion to the size of the diameter, an inverted V-shaped continuous tooth gap and a variable round for dividing and absorbing the remainder of the number of teeth that cannot be divided by an integer. Tooth gap structure and conical (disk) type tooth number variable gear having the same. The conical gears of the first and second aspects are arranged along the rotation axis so that the diameters are opposite to each other, and the conical gears can always mesh with each other and move with respect to the tooth tip. A conical gear type parallel shaft continuously variable transmission type power transmission structure having a function of continuously changing the rotation ratio between two conical gears by arranging a transmission gear and changing the position of the transmission gear. A planetary gear mechanism in which a sun gear 1 is arranged in connection with a rotation center shaft, and a plurality of planetary gear mechanisms are arranged so that the tips of the ends of the conical gears configured in claim 1 and 2 are engaged with each other. The sun gear 2 that can move along the same central axis and can rotate independently is arranged so that it always meshes with the tooth tip of the conical planetary gear, and the position of the sun gear 2 changes along the central axis. A conical planetary gear type coaxial continuously variable transmission power transmission structure having a function of continuously and variably controlling the rotation ratio of the sun gear 1 and the sun gear 2 by making them.

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