JP2012141025A - Rotation power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a new rotation power transmission technology that reduces the number of components, significantly improves endurance strength, and reduces the size and weight, while achieving excellent assembling efficiency.SOLUTION: The rotation power transmission apparatus includes: a tubular input shaft 3; an output shaft 4 disposed in the input shaft 3; arc-shaped grooves 40 formed in the output shaft 4; and cylindrical planetary gears 5. The arc-shaped groove 40 is disposed at each of positions evenly on the peripheral surface of the output shaft 4 around the axis thereof, and has a cross section on a plane perpendicular to the axis of the output shaft 4, the cross section having such an arc shape that a space between the groove and the inner wall surface of the tubular input shaft 3 is smaller than a predetermined diameter at both ends in a direction around the axis of the output shaft 4, of the groove and has a size exceeding the predetermined diameter near the center in the direction around the axis of the output shaft 4, of the groove, and also has a cross section on a plane radially passing through the axis of the output shaft 4, the cross section having a rectangular shape between the groove and the inner wall surface of the tubular input shaft 3. Each of the cylindrical planetary gears 5 having the above predetermined diameter is loosely fitted between each groove 40 of the output shaft 4 and the inner wall surface of the tubular input shaft 3 in such a way that the cylindrical planetary gear 5 is parallel to the axis of the output shaft 4.

Description

    The present invention relates to rotational force transmission technology, and in particular, the field of manufacturing and providing a rotational power transmission device capable of efficiently transmitting rotational driving force as a differential gear, a one-way clutch, etc. From the field of providing and selling equipment and equipment necessary for its transportation, storage, assembly and installation, materials necessary for those materials, machinery and parts, such as wood, stone, various fibers, plastics, Fields that provide various metal materials, etc., electronic components incorporated in them, control-related equipment that integrates them, fields of various measuring instruments, fields of power machines that move the equipment and instruments, electric power and energy Fields generally referred to as industrial machinery, such as the source of electricity and oil, as well as testing and researching those facilities and equipment, Fields related to these displays, sales, import / export, generals, fields related to the collection, transportation, etc. of waste generated as a result of their use, equipment for making them, and operation of equipment There is no technical field that is not related to the new field that cannot be envisaged at present, such as the recycling field that efficiently recycles garbage.

(Points of interest)
Open diff or multi-plate clutch type LSD that absorbs the difference between the inner wheels of the left and right wheels and distributes and transmits the torque from the prime mover evenly to the left and right wheels during cornering by a four-wheeled vehicle with wheels on the left and right Various differential devices such as (limited slip differential), helical LSD, viscous LSD, and active LSD have been developed and put into practical use. However, when the inner ring is idle, the rotational force escapes to the inner ring, There is a drawback that it is impossible to transmit the driving force to the outer ring. In the multi-plate clutch type LSD, dedicated oil and overhaul are indispensable, and the torque plate slips during transmission of the driving force, resulting in a large amount of heat generation. Yes, in the case of helical LSD, the gears rub against each other and rotate to generate a large amount of heat. A large force is generated in the thrust direction, and the viscous LSD uses a fluid for viscous coupling, so the transmission loss of the driving force is large, and the active LSD includes various sensors, hydraulic actuators, computers. Etc. are indispensable and very expensive, each has its own problems.

(Conventional technology)
Proposals that reflect this situation and serve as a breakthrough are not unheard of.
For example, as typified by those proposed in Patent Documents 1 (1) and (2) below, a pinion is provided with a pair of side gears connected to the left and right wheels in the differential case, and meshed separately with the side gears. A combination of a plurality of gears, viscous couplings, etc., such as providing gears, to keep the differential limiting force generated in each side gear even when either the left or right wheels idle, (3) to (5), as shown in (5), which incorporates a ball cam, or a combination of a ball cam and a hydraulic mechanism, etc. Some things have been raised.

However, the combination of a plurality of gears as shown in Patent Documents 1 (1) and (2) described above has a large number of parts and requires high precision in processing of individual gears. Since high durability is required so as to prevent chipping and wear, there is a disadvantage that each part becomes vigorous and expensive, which is uneconomical. Also, in Patent Documents 1 (3) to (5) In the case where a ball cam is incorporated like a thing, each ball cam transmits a rotational force by a point contact, so that each ball cam requires high sphericity and durability, and in addition, it does not incorporate a hydraulic circuit. However, it cannot solve the problem that it is not economical because maintenance such as regular oil change is required.
(1) JP-A-8-61464 (2) JP-A-8-28655 (3) JP-A-11-108154 (4) JP-A-2001-12507 (5) JP-A-2003-42188

(Awareness of problems)
As described above, the various differential gears that have been proposed so far have a large number of parts, have a complicated structure, increase the cause of failure of the differential, and have been able to eliminate these disadvantages. Even in such a case, maintenance such as oil change becomes indispensable, leaving problems in terms of economic efficiency. For many years, it has been possible to respond flexibly to various users and efficiently distribute rotational driving force. In addition, while being engaged in the development and provision of differential gears with excellent durability, based on various knowledge obtained from them and information from users, the number of parts has been further reduced. It is possible to make further improvements to the configuration to achieve the rotational power distribution function accurately and efficiently from the manufacturing process as well as achieving simplification and excellent durability. Which has led to the keenly aware.

(Object of invention)
Therefore, the present invention can reduce the number of parts and can significantly increase the durability, and can be developed with a new torque transmission technology that is excellent in manufacturing and assembly efficiency by reducing the size and weight. Judging from the judgment, the development and research were started quickly, and as a result of repeating trial and error over many years and many trial manufactures and experiments, this time, we finally succeeded in realizing a rotary power transmission device with a new structure. In the following, the configuration thereof will be described in detail together with an embodiment representative of the present invention shown in the drawings.

(Structure of the invention)
As will be clearly understood from the embodiments representing the present invention shown in the drawings, the rotational power transmission device of the present invention basically comprises the following configuration.
That is, the output shaft and a cylindrical input shaft whose outer periphery of the output shaft is concentrically arranged, and a plurality of locations that are balanced around the axis of the peripheral wall of the output shaft that is disposed in the cylindrical input shaft The cross-sectional shape on the plane perpendicular to the output shaft axis is less than the predetermined diameter between both ends of the cylindrical input shaft between the inner wall surface of the cylindrical input shaft and the direction around the output shaft axis. An arc-shaped groove that has an arc shape exceeding a predetermined diameter in the vicinity of the center of the tube and a rectangular cross-sectional shape between the cylindrical input shaft inner wall surface and a cross-sectional shape on a plane passing through the output shaft axis in the diametrical direction. A cylindrical planetary gear having a predetermined diameter is mounted in a loose fit between the arc grooves of the output shaft and the inner wall surface of the cylindrical input shaft so as to be in a posture parallel to the output shaft axis. This is a rotational power transmission device having the configuration as a gist.

    More specifically, the rotational power transmission device having this basic configuration has an output shaft and a cylindrical input shaft in which the outer periphery of the output shaft is concentrically arranged, and the cylindrical input shaft The cross-sectional shape on the plane perpendicular to the output shaft axis is between the inner wall surface of the cylindrical input shaft and the output shaft shaft center at a plurality of locations that are balanced around the axis of the output shaft peripheral wall. A circular cross-section on the plane passing through the output shaft axis in the diametrical direction with both ends in the rotation direction having an arc shape that is less than a predetermined diameter at the edge and exceeding the predetermined diameter in the vicinity of the center in the rotation direction around the output shaft axis. A rectangular arc groove is formed between the inner wall surface of the input shaft and a cylindrical planetary gear having the predetermined diameter is output between each arc groove of the output shaft and the inner wall surface of the cylindrical input shaft. Mount in a loose fit so that it is parallel to the axis of the shaft, and face the opposite ends of each planetary gear in the direction parallel to the axis of the output shaft Each position is formed with a plurality of gear guides that can guide and regulate each planetary gear position around the axis of the output shaft within a range corresponding to the space between each arc groove and the inner wall surface of the cylindrical input shaft. The guide board can be rotated together with the output shaft, and each gear guide portion is incorporated so that each planetary gear position can be rotated and adjusted around the axis of the output shaft within each arc groove range. The rotational power transmission device having the configuration as described above is obtained.

    In other words, it has an output shaft and a cylindrical input shaft in which the outer periphery of the output shaft is concentrically arranged, and is balanced around the axis of the output shaft peripheral wall disposed in the cylindrical input shaft. The cross-sectional shape on a plane perpendicular to the output shaft axis is less than a predetermined diameter between the cylindrical input shaft inner wall surface and the both ends in the direction around the output shaft center. An arc shape exceeding a predetermined diameter in the vicinity of the center in the direction around the center, and a cross-sectional shape on a plane passing through the output shaft axis in the diameter direction forms a rectangular shape with the inner wall surface of the cylindrical input shaft. A cylindrical planetary gear longer than the predetermined diameter and the arc groove axial length is parallel to the output shaft axis between each arc groove of the output shaft and the inner wall surface of the cylindrical input shaft. Each arcuate groove is mounted in a loosely fitted shape so as to be in a posture, and is in a direction parallel to the axis of the output shaft and opposed to both ends of each planetary gear. A pair of guide panels formed with a plurality of gear guide portions capable of guiding and regulating the planetary gear positions in the direction around the axis of the output shaft within a range corresponding to the space between the inner wall surface of the cylindrical input shaft and the output shaft Each planetary gear position can be rotated and adjusted around the axis of the output shaft within the range of each arc groove, and the output shaft can be adjusted for each planetary gear surplus shaft length. Incorporated so as to be slidable in the direction parallel to the shaft center, and in each of a plurality of appropriate locations balanced around the shaft center between the arc grooves on the output shaft peripheral wall, slide grooves parallel to the output shaft axis are engraved. In each slide groove, a slide cam longer than each slide groove length is loosely fitted, and both ends of each slide cam are fitted in slide guide portions formed in the corresponding positions on the guide panel, respectively. Forward rotation locking part at one of the appropriate locations on the opposite wall of the output groove around the output shaft In addition to forming a reverse latching part at each appropriate wall, each face wall facing each forward / reverse latching part of each slide cam is either one of the opposing walls in the circumferential direction of the output shaft center of each sliding groove For forward rotation that can be fitted to one of the forward rotation engagement portions that can be fitted to one of the forward rotation engagement portions, and the other reverse rotation engagement portion of the sliding groove around the output shaft axis. When a fitting part is formed and each slide cam is moved to one side in the direction parallel to the output shaft axis, the forward rotation fitting part of each slide cam is fitted to one forward locking part of each sliding groove. The rotational force can be transmitted to the output shaft in one direction around the axis, and when each slide cam is moved to the other in the direction parallel to the output shaft axis, Rotational power transmission device having a configuration in which a reverse rotation fitting portion of each slide cam is fitted to be able to transmit a rotational force to the output shaft in the other direction around the axis. It becomes.

    As described above, according to the rotational power transmission device of the present invention, unlike the conventional ones, the open differential mechanism for a conventional four-wheel vehicle or the like has a characteristic configuration as described above. The traction is lost to the slipped tire of either the left or right wheel, and the vehicle stops moving at all. Also, the vehicle equipped with LSD operates to eliminate the rotation difference between the left and right wheels even when it is not slipping. However, the rotational power transmission device cuts the driving force to the wheels that are over-rotated from the rotational power transmission device, and the rotational power is reduced. A rotational driving force can be transmitted to a wheel that rotates slower than the transmission device at the same rotational speed as the rotational power transmission device, which is impossible with a conventional differential gear mechanism. It can be used as a one-way clutch mechanism or differential gear mechanism in various fields including four-wheel vehicles, and the number of parts can be reduced. Compared with the conventional differential gear mechanism, it is greatly reduced, and the excellent effect that it can be simplified and the durability can be remarkably increased is exhibited.

    In addition, a plurality of planetary gears mounted loosely between each arcuate groove of the output shaft and the inner wall surface of the cylindrical input shaft, a gear guide portion is formed at each of the locations facing the planetary gear ends, Each planetary gear is shifted in the direction around the center of the output shaft with each gear guide board arranged on both sides of the planetary gear, and the rotational drive force in the desired rotational direction during forward / reverse rotation of the cylindrical input shaft Can be selectively and efficiently transmitted to the output shaft, and each slide cam is mounted loosely in each slide groove formed around the output shaft. In this configuration, each slide cam can select the forward / reverse rotation of each gear guide panel with respect to the output shaft in the direction around the center of the output shaft, and perform the shifting operation more accurately. .

    And each of the forward rotation latching portion and the reverse rotation latching portion of each sliding groove of the output shaft and the forward rotation fitting portion and the reverse rotation fitting portion of each slide cam are each formed with a guide inclined surface. The guide inclined surface can guide and maintain the positional relationship between the rotating output shaft and each slide cam in the direction parallel to the center axis of the output shaft to a certain fitting position. This makes it possible to achieve an excellent effect of making the control smoother and more reliable and enabling the transmission of the rotational driving force to be remarkably efficient.

    Furthermore, a cylindrical input shaft with a normal rotation guide groove and a reverse rotation guide groove formed at a suitable location on the cylindrical outer peripheral wall is incorporated so as to be concentrically accommodated within an outer cylinder having a guide pin projecting at a suitable location on the cylindrical inner peripheral wall. Each slide cam, each gear guide panel, and the cylindrical input shaft can be slidably moved in the direction parallel to the output shaft axis with respect to the output shaft. When force is input, each guide pin moves along each forward guide groove or each reverse guide groove that is slidably fitted according to the forward / reverse direction of the input rotation. Since each slide guide gear guide panel and cylindrical input shaft are automatically moved in either direction parallel to the output shaft axis, each gear guide panel in the rotating cylindrical input shaft and each Simple control for moving the planetary gears in the forward / reverse direction more accurately. In it shall be realized, it the number of parts required to significantly reduce, can be reduced in size and weight.

    A plurality of output shafts are incorporated in a cylindrical input shaft so as to be concentrically arranged in a tandem arrangement, and cylindrical connecting pipes are provided between the ends of the output shaft shafts concentrically facing each other. If the output shaft and the cylindrical input shaft are maintained on the same axis, the vibration and noise are reduced and quiet. In addition, it is possible to provide a rotational power transmission device that is excellent and has much higher wear resistance and durability.

In implementing the present invention having the above-described configuration, the best or desirable mode will be described.
The cylindrical input shaft rotates by receiving a rotational driving force from the outside, transmits the rotational driving force to the output shaft through a plurality of planetary gears, and the one-way clutch mechanism and / or differential throughout the rotational power transmission device. It is responsible for the function that enables the formation of a gear mechanism, has sufficient durability to transmit rotational input, and so that multiple planetary gears arranged around the output shaft and the output shaft peripheral wall operate normally. The inner peripheral wall must be finished in a precise circular shape, and as shown in the examples described later, in the case of being incorporated in the outer cylinder, the shaft of the cylindrical input shaft outer peripheral wall It is possible to engrave a normal rotation guide groove at one of the ends in the center direction, and a reverse guide groove at either end opposite to the opposite direction. Accommodates shafts in columns and concentricity Yo can be obtained by setting the embeddable dimensions.

    The forward rotation guide groove moves the cylindrical input shaft to one of the directions parallel to the output shaft axis with respect to the outer cylinder when the forward rotation is input to the cylindrical input shaft via the outer cylinder. The forward rotation fitting part of the slide cam is fitted to each forward rotation latching part of the output shaft, and shares the function that enables the output shaft to be controlled to output the forward rotation. It is engraved at either one of the appropriate locations on both ends in the axial direction of the wall so as to incline in the forward rotation direction around the cylindrical input shaft axis, with the other end opposite to the one end facing the side. The guide pin of the outer cylinder should be slidable as shown in the embodiments described later.

    When the reverse rotation guide groove is reversely input to the cylindrical input shaft via the outer cylinder, the other side of the cylindrical input shaft parallel to the output shaft axis is opposite to the other cylinder (the other is opposite to the other). And the function of enabling the control unit so that the reverse rotation fitting part of each slide cam is fitted to each reverse rotation latching part of the output shaft and the output shaft outputs the reverse rotation. The cylindrical input shaft outer peripheral wall is inclined in the direction of reversal around the cylindrical input shaft axis around one end of the cylindrical input shaft outer peripheral wall, with one end opposite to the other end facing toward the side. The guide pins of the outer cylinder should be capable of being slidably guided as shown in the embodiments described later.

    The output shaft receives the driving force from the cylindrical input shaft via a plurality of planetary gears, outputs the rotational driving force to the outside, and forms the one-way clutch mechanism and / or differential gear mechanism with the entire rotational power transmission device It has a function that enables it, has sufficient durability to transmit rotational input, and the peripheral wall surface of the cylindrical input shaft and the planetary gears are finished with high precision so that each planetary gear operates normally. The cross-sectional shape on a plane perpendicular to the output shaft axis is in the direction around the output shaft axis between the cylindrical input shaft inner wall surface at each of a plurality of locations balanced around the axis of the output shaft peripheral wall. The cylindrical input shaft has a cross-sectional shape on a plane that passes through the output shaft axis in the diametrical direction and has an arc shape that exceeds the predetermined diameter near the center in the direction around the output shaft axis. A rectangular arc groove is formed between the inner wall and the inner wall. As shown in the embodiments described later, sliding grooves parallel to the output shaft axis are inscribed at a plurality of appropriate positions that are balanced around the axis between the arc grooves on the output shaft peripheral wall. And a slide cam can be freely fitted in each sliding groove.

    The rotational power transmission device of the present invention has only one output shaft, but also has a plurality of output shafts, and the plurality of output shafts are arranged in a concentric and tandem arrangement as shown in the embodiments described later. In addition, the output shaft shaft ends concentrically facing each other are regulated so as to be supported so as to be arranged on the same shaft center by a cylindrical connecting tube, and are accommodated and incorporated in the cylindrical input shaft. The cylindrical connecting pipe has a function of concentrically holding the output shaft shaft ends concentrically facing each other among a plurality of concentric and tandem output shafts. In addition to being able to reliably hold each output shaft so that each output shaft can rotate independently, each output shaft is firmly connected to each other so that it can be driven to rotate integrally, etc. For example, bearing function or connecting franc There is no harm be incorporated as which also serves as one of the such.

    The arcuate groove of the output shaft can accommodate the planetary gear at each of a plurality of locations that are balanced between the inner peripheral wall of the cylindrical input shaft and around the axis, and the cylindrical input shaft is interposed via each planetary gear. The rotary drive force from the output shaft can be output as the rotary drive force of the same output shaft, and the cross-sectional shape on the plane perpendicular to the output shaft axis is in each of a plurality of locations balanced around the axis of the output shaft peripheral wall. , Both ends in the direction around the output shaft axis are less than a predetermined diameter between the inner wall surface of the cylindrical input shaft and an arc shape exceeding the predetermined diameter near the center in the direction around the output shaft axis, and the output shaft The cross-sectional shape on the plane passing through the axis in the diametrical direction must be formed in a rectangular shape between the inner wall surface of the cylindrical input shaft.

    The slide groove on the output shaft allows the slide cam to be housed and assembled in an appropriate position on the peripheral wall of the output shaft, and when the slide cam is moved in either direction parallel to the output shaft axis, a guide for the output shaft is provided. When the position of the panel is slightly shifted to one around the output shaft axis, each planetary gear can transmit only forward rotation to the output shaft, and the slide cam moves in either direction parallel to the output shaft axis. The function of allowing the planetary gears to be controlled so that only the reverse movement can be transmitted to the output shaft by slightly shifting the position of the guide panel with respect to the output shaft around the output shaft center. As shown in the embodiment, the output shaft peripheral wall is engraved in a shape parallel to the output shaft axis at a plurality of appropriate positions balanced around the axis between the arc grooves. A slide cam longer than the groove length can be loosely fitted, A forward rotation latching portion is formed at one of the appropriate locations on the wall facing the output shaft center circumference of the sliding groove, and a reverse rotation latching portion is formed at either location on the other wall. The stopping portion and the reverse rotation engaging portion are arranged at a sufficient interval in the direction parallel to the output shaft axis center, and the forward rotation fitting portion has a normal rotation fitting portion at the forward rotation locking portion of each sliding groove. When fitted to the latching part, it forms a guide inclined surface that can guide the slide cam in a direction parallel to the output shaft axis until the fitting part for reverse rotation deviates from the reverse latching part, and reverse rotation In the latching part, when the reverse rotation fitting part is fitted to the reverse rotation latching part, slide the slide cam in a direction parallel to the output shaft axis until the forward rotation fitting part deviates from the normal rotation latching part. It is desirable to form a guiding inclined surface that can be guided to the surface.

    The forward rotation latching part of the sliding groove can be latched so that the slide cam does not move inadvertently in a direction parallel to the output shaft axis direction when fitted to the forward rotation fitting part of the slide cam. It shall have a sufficient strength, and shall be formed so as to be fitted to the forward rotation fitting portion of the slide cam when the cylindrical input shaft transmits the forward driving force. The sliding groove should be formed into a fitting shape such as a convex shape or a concave shape on either one of the opposing walls in the circumferential direction of the output axis of each sliding groove. Thus, when the forward rotation fitting part of the slide cam is fitted to the forward rotation latching part, the direction in which the slide cam is parallel to the output shaft axis to the position where the reverse rotation fitting part deviates from the reverse rotation latching part It is desirable to form a guiding inclined surface that can be guided to the surface.

    The reverse rotation latching part of the sliding groove allows the slide cam to be latched so that it does not move inadvertently in the direction parallel to the output shaft axis when fitted to the reverse rotation fitting part of the slide cam. It shall be responsible for the function, shall have sufficient strength, and shall be formed so as to be fitted to the reverse fitting portion of the slide cam when the cylindrical input shaft transmits the reverse driving force. First, it should be formed in a fitting shape such as a convex shape or a concave shape on either one of the opposing walls in the circumferential direction of the output shaft center of each sliding groove, as shown in the examples described later. When the slide cam reverse fitting part is fitted to the reverse latching part, the slide cam is guided in the direction parallel to the output shaft axis until the forward cam fitting part deviates from the normal latching part. It is desirable to form a possible guiding inclined surface.

    The planetary gear makes it possible to transmit the rotational driving force of the cylindrical input shaft to the output shaft, transmit either the forward or reverse driving force of the cylindrical input shaft to the output shaft, and disable either of the other. It also has a function of transmitting either the forward or reverse driving force of the cylindrical input shaft to the output shaft and disabling or switching either of them. It must have a cylindrical shape with a predetermined diameter and strength, and can be assembled loosely between each output shaft arcuate groove and the inner wall surface of the cylindrical input shaft so as to be parallel to the output shaft axis. As shown in the embodiments described later, the positions of the planetary gears are set at the ends of the planetary gears at the ends corresponding to the spaces between the arc grooves and the inner wall surface of the cylindrical input shaft. A guide board formed with multiple gear guides that can be guided and regulated in the direction of rotation is used as the output shaft. And each gear guide portion should be capable of being installed so that each planetary gear position can be rotated and adjusted around the axis of the output shaft within each arc groove range, Furthermore, the planetary gear is set longer than the axis length of the arc groove groove, the pair of guide panels can be moved in the direction of the output shaft axis, and the slide cam can be controlled to switch between forward and reverse rotation by the guide panel. Is desirable.

    The slide cam can be loosely fitted and installed at a suitable place on the peripheral wall of the output shaft, and when the slide cam is moved in either direction parallel to the output shaft axis, the position of the guide panel relative to the output shaft is adjusted. Slightly shifted to one side around the shaft center, each planetary gear can transmit only forward rotation to the output shaft, and when the slide cam is moved in either direction parallel to the output shaft center, the guide board for the output shaft Is slightly shifted to the other around the output shaft axis so that each planetary gear can be controlled so that only reverse movement can be transmitted to the output shaft. As shown in the figure, the surface wall of each slide cam that faces the forward / reverse latching portion of each sliding groove is forwardly locked to either one of the opposing walls in the circumferential direction of the output shaft center of each sliding groove. Fitting part for forward rotation that can be fitted to the stop part, and each sliding The reverse rotation fitting portion that can be fitted to one of the other reverse rotation latching portions of the opposing wall in the circumferential direction of the output shaft center should be formed, and the forward rotation fitting portion of the slide cam When the forward rotation fitting part is fitted to the forward rotation latching part, the slide cam can be guided in the direction parallel to the output shaft axis to the position where the reverse rotation fitting part deviates from the reverse rotation latching part. An inclined surface is formed, and the reverse rotation fitting portion of the slide cam is engaged with the reverse rotation fitting portion when the reverse rotation fitting portion is fitted to the reverse rotation engagement portion. It may be desirable to form a guide inclined surface that can be guided in a direction parallel to the output shaft axis to a position deviating from the portion.

    The guide panel guides and regulates the position of each planetary gear in the direction around the axis of the output shaft within the range corresponding to the space between each arc groove and the inner wall surface of the cylindrical input shaft. It has the function of enabling reverse switching, and a gear guide is formed at each position facing each end of each planetary gear within a range corresponding to the space between each arc groove and the inner wall surface of the cylindrical input shaft. It should be able to be assembled as a pair so that each pair of planetary gears forms a pair at each end of the planetary gear. It is possible to form a guide portion, and as shown in the embodiment described later, it is composed of an annular flat plate that can be mounted through so that the shaft end of the output shaft is concentrically arranged. Is desirable.

    The gear guide portion of the guide board is loosely fitted to both ends of each planetary gear, and when the guide board is moved in the direction around the axis of the output shaft, it is located in the space between each arc groove and the inner wall surface of the cylindrical input shaft. In the corresponding range, each planetary gear position can be guided and regulated in the direction around the axis of the output shaft. As shown in the embodiments described later, grooves formed at appropriate positions on the guide board In addition to a through hole or the like, a convex portion that can be fitted into a concave portion formed at both ends of each planetary gear may protrude from each appropriate position of the guide board.

    The slide guide portion of the guide board is loosely fitted to both ends of each slide cam, and each slide cam moves in a direction parallel to the axis of the output shaft and a direction around the axis of the output shaft. In addition, it can maintain the loose fit state with the guide board and bears the function of accurately and smoothly transmitting the amount of angular movement of each slide cam in the direction around the axis to the guide board (and each planetary gear). As shown in the examples to be described later, there can be grooves, through holes, etc. formed at appropriate positions on the guide board, and projections that can be fitted into recesses formed at both ends of each slide cam. It can be made to protrude from each appropriate position of the guide board.

    The outer cylinder bears a function that enables the operation force to move each guide panel in a direction parallel to the axis of the output shaft to be derived from the rotational force of the cylindrical input shaft. The outer peripheral wall should be composed of a lid-cylinder-type covered cylindrical body that can be slidably mounted in the direction around the axis center and in a direction parallel to the axis center. As shown in the figure, the cylindrical input shaft rotates around the cylindrical input shaft axis so that one end of the outer circumferential wall in the axial direction is at one end and the other end opposite to the one end is facing the The cylindrical input shaft has a forward rotation guide groove inclined in the forward rotation direction, and one end opposite to the other end of the outer peripheral wall at an appropriate position on both ends in the axial center direction. A reverse guide groove that inclines in the reverse direction around the shaft center is engraved, and can be externally concentrically mounted on the cylindrical input shaft. Body, the inner circumferential wall of either the lid or the cylinder corresponding to either the forward rotation guiding groove or the reverse rotation guiding groove of the covered cylindrical body, A guide pin that can be freely slidably fitted on either one of the lids and cylinders corresponding to either one of the forward rotation guide grooves or the reverse rotation guide grooves of the covered cylindrical body is provided. An outer cylinder in which a guide pin that can be freely slidably fitted to either the forward rotation guide groove or the reverse rotation guide groove is projected on the inner peripheral wall portion, and is combined with the cylindrical input shaft concentrically. It is desirable to be.

    The outer cylinder lid and cylinder can be combined concentrically with the cylindrical input shaft, and each guide pin can be slidably fitted to each forward or reverse guide groove of the cylindrical input shaft. In the outer cylinder lid and cylinder, the cylindrical input shaft has the function of being integrally rotatable while being slidable in a direction parallel to the rotation axis. Yes, as shown in the embodiments described later, when a forward rotation is input to the cylindrical input shaft via the outer cylinder, each guide pin slides along each forward rotation guide groove, and the cylindrical input The shaft moves in a direction parallel to the output shaft axis, and the forward rotation fitting part of each slide cam is fitted to each forward rotation latching part of the output shaft. Each guide pin slides along each reverse guide groove when reverse rotation is input to the cylindrical input shaft through the cylinder. The cylindrical input shaft moves in a direction parallel to the output shaft axis, the reverse rotation fitting portion of each slide cam is fitted to each reverse rotation latching portion of the output shaft, and the output shaft outputs reverse rotation. It is convenient to make it. .

Each guide pin of the outer cylinder is slidably fitted in the forward and reverse guide grooves of the cylindrical input shaft, and the cylindrical input shaft can be guided in the direction parallel to the axis in the outer cylinder. In this embodiment, the forward rotation guide groove and the reverse rotation guide groove of the cylindrical input shaft have sufficient durability and can be slidably fitted. As shown in FIG. 3, the cylindrical input shaft protrudes in the centripetal direction from the lid and the inner peripheral wall of the cylindrical input shaft toward the center of the cylindrical input shaft. Should be.
In the following, the structure will be described in detail together with some examples representing the present invention shown in the drawings.

    The example shown in the perspective view of the rotary power transmission device 1 disassembled in FIG. 1 and the front view of the rotary power transmission device 1 in FIG. 2 has the outer periphery of the output shaft 4 and the tubular input shaft 3. Arc grooves 40, 40 are formed between the inner peripheral wall surface of the cylindrical input shaft 3 around the axis of the peripheral wall of the output shaft 4, and the arc grooves 40, 40 of the output shaft 4 and the cylindrical input shaft 3 1 shows a typical embodiment of the rotational power transmission device according to the present invention in which planetary gears 5 and 5 are mounted in a loose fit between wall surfaces.

    As can be clearly understood from these drawings, the rotational power transmission device 1 of the present invention has an output shaft 4 and a cylindrical input shaft 3 in which the outer periphery of the output shaft 4 is concentrically arranged. The cross-sectional shape on the plane orthogonal to the output shaft 4 axis center is formed at two locations that are balanced with an opening angle of 180 ° around the axis of the peripheral wall of the output shaft 4 that is disposed in the cylindrical input shaft 3. Between the inner wall surface of the cylindrical input shaft 3, both ends in the direction around the output shaft 4 axis are set to be smaller than a predetermined diameter, and one end in the direction around the output shaft 4 axis is set to have a small curvature. The inner surface of the cylindrical input shaft 3 has a streamlined arc shape exceeding a predetermined diameter in the vicinity of the center of the output shaft 4 axis center, and a cross-sectional shape on a plane passing through the output shaft 4 axis center in the diameter direction. A rectangular arc groove 40 is formed between the output shaft 4 and the inner wall surface of the cylindrical input shaft 3. It is made by mounting the loosely fitted so as to be parallel posture planetary gears 5,5 of cylindrical shape with a predetermined diameter on the output shaft 4 axis.

    3 is a front view of the main part of the rotary power transmission device 1 in FIG. 4, a side view of the planetary gear 5 in FIG. 5, a front view of the guide panel 7 in FIG. 6, and a guide in FIG. The example shown in the front view of the rotational power transmission device 1 incorporating the panel 7 and the front view of the main part of the rotational power transmission device 1 incorporating the guide panel 7 of FIG. , 7 is incorporated, and a representative embodiment 2 of the rotational power transmission device of the present invention is shown.

    As shown in FIGS. 3 to 8, the rotational power transmission device 1 balances with an opening angle of 90 ° around the axis of the peripheral wall of the output shaft 4 arranged in the cylindrical input shaft 3. The cross-sectional shape on the plane orthogonal to the output shaft 4 axis center at each of the four locations is less than a predetermined diameter at both ends in the direction around the output shaft 4 axis between the inner wall surface of the cylindrical input shaft 3 and The inner surface of the cylindrical input shaft 3 has a streamlined arc shape exceeding a predetermined diameter in the vicinity of the center of the output shaft 4 axis center, and a cross-sectional shape on a plane passing through the output shaft 4 axis center in the diameter direction. Are formed into a rectangular shape, and a cylindrical shape having the predetermined diameter is formed between each of the output groove 4 and the inner wall surface of the cylindrical input shaft 3. Of the planetary gears 5, 5... Are mounted in a loose fit so as to be parallel to the output shaft 4 axis, and as shown in FIG. 5 to FIG. Concentric diameter-reduced shafts 50, 50,... Protrude from both ends of a, 5, 5,..., And are parallel to the axis of the output shaft 4 at the ends of each planetary gear 5, 5,. In opposite positions, each of the reduced diameter shafts 50, 50,... Can be slidably fitted, and in the space between each arc groove 40, 40,. Within the corresponding range, the planetary gears 5, 5,... Have gear guide portions 70, 70,... Formed of a plurality of arc holes whose positions can be guided and regulated around the axis of the output shaft 4. The formed annular disk-shaped gear guide board 7 can be rotated together with the output shaft 4, and each of the gear guide portions 70, 70,. , 40,... Are incorporated so that they can be rotated and adjusted around the axis of the output shaft 4 within the range.

    9 is a front view of the improved output shaft 4, FIG. 10 is a side view of the improved output shaft 4, FIG. 11 is a side view of the slide cam 6, and FIG. 14 is a side view of the slide cam 6 that performs the reverse rotation operation, FIG. 14 is a front view of the improved guide board 7, FIG. 15 is a side view and a front view of the rotational power transmission device 1 that performs the normal rotation operation, and FIG. Side view and front view of the transmission device 1, a perspective view of the rotary power transmission device 1 incorporating the output shafts 4 and 4 of FIG. 17 in a column, a perspective view of the output shaft 4 of FIG. 18, a cylindrical body of the outer cylinder 2 of FIG. 20, a perspective view of the outer cylinder 2 lid 21 in FIG. 20, a perspective view of the cylindrical input shaft 3 in FIG. 21, and a side surface of the cylindrical input shaft 3 that rotates forward in the outer cylinder 2 in FIG. FIG. 24 is a side view of the cylindrical input shaft 3 that rotates in reverse in the outer cylinder 2 of FIG. The side view of the output shafts 4 and 4 accommodated in the cylindrical input shaft 3, the side view of the cylindrical input shaft 3 and the output shaft 4 incorporated in the outer cylinder 2 of FIG. 25, and the slide cams 6 and 6 of FIG. In the example shown in the side view of the rotary power transmission device 1 and the front view of the improved rotary power transmission device 1 in FIG. 27, two output shafts 4 and 4 are mounted in a columnar arrangement in the cylindrical input shaft 3. The slide cams 6, 6,... Are incorporated in a plurality of appropriate positions that are balanced around the axis between the output shafts 4, the peripheral walls 40, 40,. The typical Example in the rotary power transmission device of invention is shown.

    As shown in each drawing of FIGS. 9 to 27, the rotary power transmission device 1 has arcuate grooves 40, 40, 40, 40, 40, 40, 40, 40, 40 formed on each output shaft 4, 4 circumferential wall in a balanced manner with an opening angle of 90 °. In the meantime, an opening angle of 45 ° is separated from each arcuate groove 40, 40,..., And an output shaft 4 is provided at each of four locations that are balanced about the axis with an opening angle of 90 ° between each other. .. Are formed in the slide grooves 41, 41,... Parallel to the shaft center, and slide cams 6, 6 longer than the length of the slide grooves 41, 41,. ,... Are loosely fitted, and slide guides 71, 71,. A total of four guide panels, two for each of the two output shafts 4 and 4 that are concentrically arranged in tandem. , 7, there is the assumption that incorporating ....

    Of the sliding grooves 41, 41,... Around the output shaft 4 axis circumferential direction facing wall, the normal rotation locking portion 42 is positioned at one of the appropriate positions on the wall, and the reverse rotation locking portion 43 is positioned at the appropriate position of the other wall. Are formed on the surface walls of the slide cams 6, 6,... Facing the forward / reverse engaging portions 42, 43, respectively. The forward rotation fitting portion 60 that can be fitted to any one of the forward rotation latching portions 42 of the circumferentially facing wall, and the output shaft 4 axis center circumferential direction opposite side of each of the sliding grooves 41, 41,. A reverse rotation fitting portion 61 that can be fitted to any one of the reverse rotation latching portions 42 of the wall is formed.

    In addition, the forward rotation latching portions 42, 42,... And the reverse rotation latching portions 43, 43,... Of the output shaft 4 sliding grooves 41, 41,. Are arranged at a sufficient distance from each other, and the forward rotation locking portions 42, 42,... Of the sliding grooves 41, 41,... And the forward fitting portions 60, 60 of the slide cams 6, 6,. ,..., When the forward rotation fitting portions 60, 60,... Are engaged with the forward rotation locking portions 42, 42,. .., Forming guide inclined surfaces 44, 44,... That can be guided in a direction parallel to the four axis of the output shaft to a position where the joint portions 61, 61,. .., And the reverse rotation engaging portions 43, 43,... Of the slide grooves 41, 41,... And the reverse rotation fitting portions 61, 61,. When the fitting portions 61, 61,... Are fitted to the reverse rotation latch portions 43, 43,..., The slide cams 6, 6,. It is assumed that guide inclined surfaces 44, 44,... That can be guided in a direction parallel to the output shaft 4 axis to a position deviating from the locking portions 42, 42,.

    Moreover, as shown in FIGS. 17 to 27, the cylindrical input shaft 3 is at one of the appropriate positions on both ends in the axial direction of the outer peripheral wall, and each of the four positions having an opening angle of 90 ° around the axial center. In addition, the forward rotation guide grooves 30, 30,... That are inclined in the forward rotation direction around the cylindrical input shaft 3 axis center and the other end opposite to the one end toward the side The cylindrical input shaft 3 is arranged so that one end opposite to the other end faces toward the four at each of the four ends having an opening angle of 90 ° around the shaft center at either one end at both ends in the axial direction. .. Are formed on the cylindrical input shaft 3 in a concentric manner, and the lid 20 and the cylindrical body 21 are divided. It is possible to mount the outer cylinder 2 composed of the covered cylindrical bodies 20 and 21.

    The outer cylinder 2 has a lid-like body 20 / cylindrical body corresponding to either one of the forward rotation guiding grooves 30, 30,... Or the reverse rotation guiding grooves 31, 31,. 21, or forward guide grooves 30, 30,... Or reverse guide grooves 31, 31,... Or guide pins 22, 22,. ..., and the forward rotation guiding grooves 30, 30,... Or the reverse rotation guiding grooves 31, 31,. 21, each of the forward guide grooves 30, 30,... Or the reverse guide grooves 31, 31,... ... is a projecting project.

    Further, as shown in FIGS. 17 to 20, the rotational power transmission device 1 includes an output shaft on each of the guide boards 7, 7,..., The lid-like body 20 and the cylindrical body 21 of the outer cylinder 2. 4 and 4, through holes are formed through the outer ends, and as shown in FIGS. 15, 16, 22, 23, and 26, the cylindrical input shaft 3 and the outer shaft are connected to the output shafts 4 and 4, respectively. The cylinder 2 is assembled so as to be movable in a direction parallel to the output shaft 4 axis.

    28 is a side view of the output shafts 4 and 4 whose axis is shifted, a side view of the output shaft 4 incorporating the cylindrical connecting tube 8 of FIG. 29, and an output shaft 4 incorporating the cylindrical connecting tube 8 of FIG. , 4 is a side view of the rotary power transmission device of the present invention in which a cylindrical connecting pipe 8 is interposed between opposite shaft ends of a plurality of output shafts 4, 4 arranged in tandem. 28 shows a typical example 4 in FIG. 1. As shown in FIGS. 28 to 30, the rotary power transmission device 1 has two output shafts 4 and 4 arranged in a concentric and tandem arrangement. In the cylindrical input shaft 3, the output shafts 4 and 4 that are concentrically opposed to each other are regulated to be arranged on the same axial center by the cylindrical connecting tube 8, and are accommodated and incorporated in the cylindrical input shaft 3. can do.

(Operation / Effect of Example 1)
When the cylindrical input shaft 3 is rotationally driven in the direction of arrow A in FIG. 2, the rotational power transmission device 1 of the present invention configured as described above receives a frictional force with the inner wall surface of the cylindrical input shaft 3. The planetary gears 5 and 5 gradually move toward the rear of the arcuate grooves 40 and 40 in the direction of rotation of the cylindrical input shaft 3, and the curved surfaces of the arcuate grooves 40 and 40 have a small curvature and the inner wall surface of the cylindrical input shaft 3. And the rotational driving force of the cylindrical input shaft 3 is transmitted to the output shaft 4 via the planetary gears 5 and 5 and the arc grooves 40 and 40, respectively. The output shaft 4 is driven to rotate in a fixed direction, which is the same rotational direction as the input shaft 3.

    When the cylindrical input shaft 3 is rotationally driven in the direction of arrow B in FIG. 2, the planetary gears 5, 5 receiving the frictional force with the inner wall surface of the cylindrical input shaft 3 gradually become the cylinders of the arc grooves 40, 40. The cylindrical input shaft 3 is moved to the rear side in the rotational direction, and is arranged between the curved surface having a large curvature of each arc groove 40, 40 and the inner wall surface of the cylindrical input shaft 3, and the inner wall surface of the cylindrical input shaft 3 Each planetary gear 5, 5 and each arcuate groove 40, 40 slip each other so that the rotational driving force of the cylindrical input shaft 3 is not transmitted to the output shaft 4.

    Accordingly, the rotational power transmission device 1 transmits only the rotational driving force of the cylindrical input shaft 3 in the direction of arrow A in FIG. 2 to the output shaft 4 and rotates in the direction opposite to that in the direction of arrow B in FIG. It has the property of not transmitting the driving force to the output shaft 4 and can form a one-way differential gear. By incorporating it between the left and right wheels of a four-wheeled vehicle, either left or right that is over-rotated from the differential gear. The driving force is not transmitted to one of the wheels, and the wheel that rotates slower than the left or right differential gear can be automatically controlled so that it rotates physically in the same rotation as the differential gear. It becomes possible to do.

    The conventional open diff for four-wheeled vehicles has the drawback that when either the left or right wheels slip, the slipped tire loses traction, causing the vehicle to stop moving. Even when there is not, there is a drawback that it works to eliminate the rotation difference between the left and right wheels, and the engine output is lost accordingly, but by incorporating the rotational power transmission device 1 between the left and right wheels of the vehicle, The drawback can be eliminated.

(Operation / Effect of Example 2)
Although the rotational power transmission device 1 of the first embodiment can form a one-way differential gear, the rotational driving force in the direction of arrow B in FIG. 2 is transmitted from the cylindrical input shaft 3 to the output shaft 4. In addition, when used in a four-wheel vehicle or the like, the function of the engine brake cannot be exhibited, and there remains a drawback that the vehicle rotates idly. However, the rotational power transmission device 1 of the second embodiment is described below. Thus, this problem can be solved.

As shown in FIGS. 3 to 4, each planetary gear 5 accommodated between arcuate grooves 40, 40,... Formed at a total of four locations around the output shaft 4 and the inner peripheral wall of the cylindrical input shaft 3. , 5,... Are inserted between the arc groove 40 and the inner peripheral wall of the cylindrical input shaft 3 at positions C indicated by a solid line and E indicated by a broken line, respectively, as shown in FIG. The rotational driving force of both reverse rotations is reliably transmitted from the cylindrical input shaft 3 to the output shaft 4.
However, since the planetary gear 5 is not bitten at the position D indicated by the two-dot chain line and in the vicinity of the center of the arcuate groove 40 in the direction around the output shaft 4 axis, no rotational force is transmitted. With this configuration alone, it is impossible to switch between forward and reverse rotation as necessary to accurately transmit the desired rotational force.

As shown in FIGS. 5 to 8, the rotational power transmission device 1 incorporating the guide panels 7 and 7 can solve such a problem of forward / reverse control.
As shown in FIGS. 7 and 8, when the guide panels 7, 7 are shifted counterclockwise with respect to the output shaft 4, the planetary gears 5, 5,... 40 between the cylindrical input shaft 3 and the inner peripheral wall of the cylindrical input shaft 3, and only the rotational driving force in the counterclockwise direction is transmitted from the cylindrical input shaft 3 to the output shaft 4, and the cylindrical input shaft 3 is rotated in the clockwise direction. , The planetary gears 5, 5,... May be controlled so as not to transmit the rotational driving force in the clockwise direction by moving to the position G indicated by the two-dot chain line. it can.

    Although not shown, when the guide plates 7 are shifted in the clockwise direction opposite to the above with respect to the output shaft 4, the planetary gears 5, 5,... Is engaged between the arc groove 40 and the inner peripheral wall of the cylindrical input shaft 3 at a position opposite to F shown by the solid line in FIG. 8, and rotates clockwise from the cylindrical input shaft 3 to the output shaft 4. When the cylindrical input shaft 3 rotates counterclockwise, the planetary gears 5, 5,... Move to the position G indicated by a two-dot chain line. Thus, it can be controlled so that the rotational driving force in the counterclockwise direction is not transmitted, and by incorporating the guide boards 7 and 7, the direction of the rotational force output in the clockwise direction and the counterclockwise direction can be selectively selected. It can be made controllable.

(Operation / Effect of Example 3)
The rotational power transmission device 1 according to the third embodiment shown in FIGS. 9 to 27 is a technique for shifting guide boards 7 and 7 rotating together with the output shaft 4 in the direction around the center of the output shaft 4 with respect to the output shaft 4. The slide cams 6, 6,... Are arranged on the outer peripheral wall of the output shaft 4, and the slide cams 6, 6,. 7 can be controlled so as to be shifted in the direction around the output shaft 4 axis.

    As shown in FIGS. 12 and 15, when the slide cams 6, 6,... Are moved with respect to the output shaft 4 in one direction parallel to the output shaft 4 axis, the slide grooves 41, 41 are provided. ,..., One forward rotation latching portion 42, 42,..., The guide inclined surfaces 44, 44,. The guide inclined surfaces 44, 44,... Are brought into contact with each other to be guided and fitted, and the guide boards 7, 7 are shifted in one direction around the output shaft 4 axis so that the planetary gears 5, 5,. One of the direction around the axis between the grooves 40, 40,... And the inner peripheral wall surface of the cylindrical input shaft 3 is caught in the hook, and the output shaft 4 is rotated in one direction (arrow H in FIG. 15). The rotational force is transmitted, and the rotational force is not transmitted in the direction of the arrow J in FIG. 15 opposite to the rotational force. Further, as shown in FIGS. When the cams 6, 6,... Are moved to the other in the direction parallel to the four output shafts, the other reverse latching portions 43, 43,. , The inversion fitting portions 61, 61,... Of the slide cams 6, 6,..., And the guide inclined surfaces 44, 44,. Then, the guide boards 7 and 7 are shifted in the other directions around the output shaft 4 axis, and the planetary gears 5, 5,... And the arcuate grooves 40, 40,. The other direction around the axis between the two is caught in the hook, and the output shaft 4 transmits the rotational force in the other direction around the circumference (arrow K in FIG. 16). The direction of the arrow L in FIG. It is possible not to transmit the rotational force.

    As shown in FIGS. 19 to 26, the rotary power transmission device 1 combines the outer cylinder 2 with the cylindrical input shaft 3 in a concentric outer shape, and each slide cam 6, 6,. A force that automatically moves in a parallel direction is obtained, and when a forward rotation is input to the cylindrical input shaft 3 through the outer cylinder 2 as shown in FIG. .. Slide along the forward rotation guide grooves 30, 30,..., And the cylindrical input shaft 3 moves in a direction parallel to the output shaft 4 axis. 26, the forward rotation fitting portions 60, 60,... Of the respective slide cams 6, 6,... Are engaged with the respective forward rotation locking portions 42, 42,. The output shaft 4 outputs a forward rotation, and enters the cylindrical input shaft 3 through the outer cylinder 2 as shown in FIG. In this case, each guide pin 22, 22,... Slides along each reverse guide groove 31, 31,..., And the cylindrical input shaft 3 moves in a direction parallel to the output shaft 4 axis. As shown in FIGS. 13 and 16, the reverse rotation fitting portions 61, 61,... Of the slide cams 6, 6,... Fit into the reverse rotation latching portions 43, 43,. In this case, the output shaft 4 is configured to output in reverse rotation.

(Operation / Effect of Example 4)
As shown in FIG. 28, the rotational power transmission device 1 in which a plurality of output shafts 4, 4 are arranged in a column in the cylindrical input shaft 3, the opposite shaft ends of the output shafts 4, 4 are opposed to each other. However, as shown in FIGS. 29 and 30, the rotational power transmission device 1 according to the fourth embodiment is opposed to the output shafts 4 and 4. A cylindrical connecting tube 8 is mounted between the shaft ends, and is pivotally supported so as to be concentrically regulated, so that the output shafts 4 and 4 can be stably supported so as to be able to rotate silently.

(Conclusion)
As described above, the rotational power transmission device according to the present invention can achieve the intended purpose evenly by its novel configuration, is easy to manufacture, and greatly compared with the conventional differential gear mechanism technology. In addition to reducing the number of parts, the durability can be significantly increased, and the size and weight can be reduced to produce and assemble with excellent efficiency. The distribution efficiency of the rotational driving force to the left and right wheels of a four-wheel vehicle, etc. will be greatly improved, and the loss of rotational driving force will be greatly reduced to realize more efficient driving. Some output loss due to slipping is unavoidable in the automobile industry and auto parts industry, as well as in the general home and transportation industries that want to reduce vehicle fuel consumption and battery consumption. Been highly valued, including the various machines art other than vehicle technology, use over a wide range, it is expected to be that continue to spread.

The drawings show some typical embodiments embodying the technical idea of the rotational power transmission device of the present invention.
It is a perspective view which shows the rotational power transmission device 1 decomposed | disassembled. It is a front view which shows the rotational power transmission device. It is a front view which shows the rotational power transmission device. FIG. 2 is a front view showing a main part of the rotational power transmission device 1. 3 is a side view showing the planetary gear 5. FIG. It is a front view which shows the guide board. It is a front view which shows the rotational power transmission device 1 incorporating the guide board 7. FIG. It is a front view which shows the principal part of the rotational power transmission device 1 incorporating the guide board 7. FIG. It is a front view which shows the improved output shaft. It is a side view which shows the improved output shaft. It is a side view which shows the slide cam 6. FIG. It is a side view which shows the slide cam 6 which carries out normal rotation operation | movement. It is a side view which shows the slide cam 6 which reversely operates. It is a front view which shows the improved type guide board. It is the side view and front view which show the rotational power transmission device 1 which carries out normal rotation operation | movement. It is the side view and front view which show the rotational power transmission device 1 which carries out reverse rotation operation. It is a perspective view which shows the rotational power transmission device 1 which incorporates the output shafts 4 and 4 in a column. 4 is a perspective view showing an output shaft 4. FIG. FIG. 4 is a perspective view showing an outer cylinder 2 tubular body 20. 3 is a perspective view showing an outer cylinder 2 lid-like body 21. FIG. It is a perspective view which shows the cylindrical input shaft 3. FIG. FIG. 4 is a side view showing a cylindrical input shaft 3 that rotates forward in the outer cylinder 2. FIG. 4 is a side view showing a cylindrical input shaft 3 that rotates in reverse in the outer cylinder 2. 4 is a side view showing output shafts 4 and 4 accommodated in a cylindrical input shaft 3. FIG. FIG. 3 is a side view showing a cylindrical input shaft 3 and an output shaft 4 in the outer cylinder 2. It is a side view which shows the rotational power transmission device 1 incorporating the slide cam 6. FIG. 1 is a front view showing an improved rotational power transmission device 1. FIG. It is a side view which shows the output shafts 4 and 4 from which the shaft center shifted | deviated. It is a side view which shows the output shaft 4 incorporating the cylindrical connection pipe 8. FIG. It is a side view which shows the output shafts 4 and 4 incorporating the cylindrical connection pipe 8. FIG.

1 Rotational power transmission device 2 Outer cylinder
20 Same lid
21 The cylinder
22 Same guide pin 3 Tubular input shaft
30 Forward rotation guide groove
31 Same as above, Reverse guide groove 4 Output shaft
40 Same arc groove
41 Same sliding groove
42 Same forward locking part
43 Same as above
44 Same inclined surface 5 Planetary gear 5
50 Same diameter reduction shaft 6 Slide cam
60 Fitting part for forward rotation
61 Fitting part for reverse rotation 7 Guide board
70 Same gear guide
71 Slide guide part 8 Cylindrical connecting pipe

Claims (6)

    An output shaft and a cylindrical input shaft whose outer periphery of the output shaft is concentrically arranged in the alligator, and each of a plurality of locations balanced around the axis of the peripheral wall of the output shaft that is disposed in the cylindrical input shaft The cross-sectional shape on the plane perpendicular to the output shaft axis is less than the predetermined diameter between the both ends in the direction around the output shaft center between the inner wall surface of the cylindrical input shaft and the center in the direction around the output shaft center An arc shape exceeding a predetermined diameter in the vicinity, and a cross-sectional shape on a plane passing through the output shaft axis in the diameter direction forms a rectangular arc groove between the inner wall surface of the cylindrical input shaft. A cylindrical planetary gear having a predetermined diameter is mounted between each arcuate groove of the output shaft and the inner wall surface of the cylindrical input shaft so as to be loosely fitted in a posture parallel to the output shaft axis. A rotational power transmission device characterized by that.     An output shaft and a cylindrical input shaft whose outer periphery of the output shaft is concentrically arranged in the alligator, and each of a plurality of locations balanced around the axis of the peripheral wall of the output shaft that is disposed in the cylindrical input shaft The cross-sectional shape on the plane perpendicular to the output shaft axis is less than the predetermined diameter between the both ends in the direction around the output shaft center between the inner wall surface of the cylindrical input shaft and the center in the direction around the output shaft center An arc shape exceeding a predetermined diameter in the vicinity, and a cross-sectional shape on a plane passing through the output shaft axis in the diameter direction forms a rectangular arc groove between the inner wall surface of the cylindrical input shaft. The cylindrical planetary gear having the predetermined diameter is mounted between the output shaft arcuate grooves and the inner wall surface of the cylindrical input shaft in a loosely fitting manner so as to be parallel to the output shaft axis, and the output The positions parallel to the axis of the shaft and facing both ends of each planetary gear correspond to the space between each arc groove and the inner wall surface of the cylindrical input shaft. A gear guide board formed with a plurality of gear guide portions capable of guiding and regulating each planetary gear position in the direction around the axis of the output shaft can be rotated together with the output shaft, and each gear guide portion is each planet. A rotational power transmission device, wherein the gear position is incorporated so as to be rotatable and adjustable in the direction around the axis of the output shaft within each arc groove range.     An output shaft and a cylindrical input shaft whose outer periphery of the output shaft is concentrically arranged in the alligator, and each of a plurality of locations balanced around the axis of the peripheral wall of the output shaft that is disposed in the cylindrical input shaft The cross-sectional shape on the plane perpendicular to the output shaft axis is less than the predetermined diameter between the both ends in the direction around the output shaft center between the inner wall surface of the cylindrical input shaft and the center in the direction around the output shaft center An arc shape exceeding a predetermined diameter in the vicinity, and a cross-sectional shape on a plane passing through the output shaft axis in the diameter direction forms a rectangular arc groove between the inner wall surface of the cylindrical input shaft. The cylindrical planetary gear longer than the predetermined diameter and the arc groove axial length is provided between each arc groove of the output shaft and the inner wall surface of the cylindrical input shaft so as to be in a posture parallel to the output shaft axis. Each of the arc grooves and the inner wall surface of the cylindrical input shaft are mounted in a fitting shape and are parallel to the axis of the output shaft and are opposed to both ends of each planetary gear. A pair of guide panels formed with a plurality of gear guide portions capable of guiding and regulating each planetary gear position in the direction around the axis of the output shaft within a range corresponding to the space of The gear guide can rotate and adjust the position of each planetary gear within the arc groove range around the axis of the output shaft, and slides in the direction parallel to the output shaft axis by the length of each planetary gear excess shaft. Incorporated so that it can freely move, and in each of a plurality of appropriate locations that balance around the axis between the arc grooves of the output shaft peripheral wall, a slide groove parallel to the axis of the output shaft is engraved. The slide cam longer than each slide groove length is loosely fitted, and both ends of each slide cam are fitted to the slide guide portions formed at the corresponding positions on the guide panel, and the output shaft axis of each slide groove is fitted. Forward rotation locking part at one of the appropriate locations on the opposite wall in the circumferential direction, and reverse rotation at the appropriate location on the other wall In addition, each of the surface walls facing the forward / reverse latching portions of the slide cams is formed on each of the slide cams, and either one of the positive rotation latching portions of the sliding groove around the output shaft axis circumferential direction Forming a forward rotation fitting portion that can be fitted to any one of the reverse rotation latching portions of the opposing wall in the circumferential direction of the output shaft axis of each sliding groove, When each slide cam is moved in one direction parallel to the output shaft axis, the forward rotation fitting portion of each slide cam is fitted to one of the forward locking latch portions of each slide groove, and the shaft center is connected to the output shaft. Rotational force can be transmitted in one direction, and when each slide cam is moved to the other in the direction parallel to the output shaft axis, the reverse rotation of each slide cam is fitted to the other reverse latching portion of each slide groove. A rotational power transmission device characterized in that a joint portion is fitted to transmit torque to the output shaft in the other direction around the axis.     The forward rotation latching portion and the reverse rotation latching portion of the output shaft sliding groove are arranged at a sufficient interval in a direction parallel to the output shaft axis center, and the forward rotation latching portion of the sliding groove and the slide cam are arranged. When the forward rotation fitting part is fitted to the forward rotation latching part, the slide cam is moved to the position where the reverse rotation fitting part deviates from the reverse rotation latching part. In addition, a reverse inclined fitting portion is formed in the reverse rotation engaging portion of the sliding groove and the reverse rotation fitting portion of the slide cam. The guide cam is formed with a guide inclined surface that can be guided in a direction parallel to the output shaft axis to a position where the forward rotation fitting portion deviates from the normal rotation latching portion when the slide cam is combined. 3. The rotational power transmission device according to 3.     The cylindrical input shaft is rotated in the forward rotation direction around the cylindrical input shaft axis so that the other end opposite to the one end is directed to either end of the outer wall in the axial direction. Inclined forward rotation guide groove, and one end of the outer peripheral wall in the axial direction at both ends in the axial direction. A reverse guide groove that inclines in the reverse direction is engraved, and can be packaged concentrically on the cylindrical input shaft, and is composed of a lid / cylinder split type covered cylindrical body, and each forward rotation of the covered cylindrical body A guide pin that can be freely slidably fitted in either the forward guide groove or the reverse guide groove is provided on the inner peripheral wall portion of either the lid or the cylinder corresponding to either the guide groove or the reverse guide groove. In addition, each forward rotation guide groove or reverse rotation on the inner peripheral wall portion of either the lid or tube corresponding to either the forward rotation guide groove or the reverse rotation guide groove on the other side of the covered cylindrical body An outer cylinder formed by projecting a guide pin that can be freely slidably fitted in either one of the guide grooves is combined with the cylindrical input shaft in a concentric outer shape, and forwardly rotated to the cylindrical input shaft via the outer cylinder. When input, each guide pin slides along each forward rotation guide groove, the cylindrical input shaft moves in a direction parallel to the output shaft axis, and the forward rotation fitting portion of each slide cam outputs When fitted to each forward rotation latching part of the shaft, the output shaft outputs forward rotation, and when the reverse rotation is input to the cylindrical input shaft via the outer cylinder, each guide pin follows each reverse rotation guide groove The cylindrical input shaft moves in a direction parallel to the output shaft axis, the reverse rotation fitting part of each slide cam is fitted to each reverse rotation latching part of the output shaft, and the output shaft is reversed. The rotational power transmission device according to claim 3 or 4, wherein the rotational power transmission device is configured to rotate.     There are a plurality of output shafts, and the plurality of output shafts are concentrically arranged in tandem, and are arranged on the same shaft center with cylindrical connecting pipes between the ends of the output shaft shafts concentrically facing each other. The rotary power transmission device according to any one of claims 1 to 5, wherein the rotational power transmission device is configured so as to be accommodated and incorporated in a cylindrical input shaft.

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