JP2011241974A - Speed reduction device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a speed reduction device reducing and transmitting the rotation to an output shaft when an input shaft rotates in one direction, and transmitting the rotation to the output shaft at the same speed when the input shaft rotates in the other direction.SOLUTION: An input member of a speed reduction mechanism is fitted into the input shaft 7. A first one-way clutch 11 is assembled between the fitting surfaces. A reverse input cutoff clutch 40 is assembled between an output member of the speed reduction mechanism and the output shaft 20. A second one-way clutch 22 with the engaging direction opposite to the first one-way clutch 11 is assembled between the input shaft 7 and a cylinder portion 21 of the output shaft 20. When the input shaft 7 rotates in one direction, the first one-way clutch 11 is engaged so that the rotation from the input shaft 7 to the input member of the speed reduction device is reduced and transmitted to the output member. The rotation of the output member locks the reverse input cutoff clutch 40 to rotate the output shaft 20 at the reduced speed. Meanwhile, when the input shaft 7 rotates in the other direction, the second one-way clutch 22 is engaged so that the rotation from the input shaft 7 is transmitted to the output member 20. The output shaft 20 is rotated at the same speed as the input shaft 7.

Description

  The present invention relates to a speed reducer that decelerates rotation of an input shaft and transmits it to an output shaft.

  As this kind of reduction gear, what was described in patent document 1 is conventionally known. FIG. 24 shows a roller-type speed reducer described in Patent Document 1. In this roller type speed reducer, the input shaft 170 and the output shaft 171 are arranged coaxially so that the shaft end portions are opposed to each other, and a plurality of internal teeth 173a are internally formed by a housing 172 that covers the shaft end portions of both shafts 170 and 171. An outer peripheral gear 173 is supported, an eccentric disc 174 that is rotatable in the internal gear 173 is provided at the shaft end of the input shaft 170, and an internal tooth is provided at the shaft end of the output shaft 171. A cage 176 disposed between the gear 173 and the bearing 175 press-fitted into the outer diameter surface 174a of the eccentric disk 174 is provided, and a plurality of pockets 177 having a smaller number than the inner teeth 173a are formed in the cage 176, and the pockets A roller 178 that can roll along the outer diameter surface of the bearing 175 is accommodated in each of the 177.

  In the reduction gear configured as described above, when the input shaft 170 rotates, the roller 178 sequentially meshes with the internal teeth 173a of the internal gear 173 due to the rotation of the eccentric disk 174, and per one rotation of the input shaft 170. The roller 178 moves in the circumferential direction by one tooth of the inner teeth 173a, and the output shaft 171 rotates at a reduced speed with respect to the input shaft 170.

  Here, in order to obtain a smooth rotation transmission, in the reduction gear described in Patent Document 1, the tooth profile of the internal teeth 173a is set so that the rotation angle of the output shaft 171 corresponds to one pitch of the internal gear 173. In this range, the output shaft 171 is rotated by the rotation of the eccentric disk 174, and at this time, a curve that is parallel to the trajectory drawn by the center of the roller 178 has a tooth profile with one tooth as a curve outside the roller 178.

JP 62-93565 A

  By the way, in the conventional roller-type speed reducer, the speed reduction ratio output to the output shaft 171 is the same regardless of whether the input shaft 170 is rotated in the forward or reverse direction. There were still points to be improved in expanding

  The problem of the present invention is that when the input shaft rotates in one direction, the rotation of the input shaft is decelerated and transmitted to the output shaft, and when rotated in the other direction, the rotation of the input shaft is the same speed as the output shaft. It is an object of the present invention to provide a reduction gear that can be transmitted and used for a wide range of applications.

  In order to solve the above problems, in the present invention, an input shaft, an output shaft that is arranged coaxially with the input shaft, and that is provided with a cylindrical portion covering the shaft end portion of the input shaft at the shaft end portion, An input member fitted to the input shaft and a cylindrical output member fitted to the output shaft. When rotation is transmitted from the input shaft to the input member, the rotation is decelerated and output. A speed reduction mechanism that outputs from the member, a first one-way clutch that is incorporated between the input shaft and the input member of the speed reduction mechanism, and transmits the rotation of the input shaft in one direction to the input member, and is engaged with the first one-way clutch A second one-way clutch that is installed between the input shaft and the output shaft with the direction reversed, and transmits the rotation of the input shaft in the other direction to the output shaft; the inner diameter surface of the output member of the speed reduction mechanism; and the output Incorporated between the outer diameter surfaces of the cylindrical part of the shaft Transmits the rotation force member to the output shaft, it was adopted a structure consisting of a reverse input blocking clutch for interrupting the transmission of rotation to the output member from the output shaft.

  In the reduction gear configured as described above, when the input shaft rotates in one direction, the first one-way clutch is engaged, the rotation of the input shaft is transmitted to the input member of the reduction mechanism, and the output member of the reduction mechanism rotates at a reduced speed. .

  When the output member rotates, the reverse input cutoff clutch locks, the rotation of the output member is transmitted to the output shaft, and the output shaft rotates at a reduced speed. At this time, since the first one-way clutch and the second one-way clutch are built with the engagement directions reversed, the second one-way clutch is not engaged and the output shaft rotates smoothly. Thus, when the input shaft rotates in one direction, the rotation is decelerated and transmitted to the output shaft.

  On the contrary, when the input shaft rotates in the other direction, the second one-way clutch is engaged, the rotation of the input shaft is transmitted to the output shaft, and the output shaft rotates at the same speed as the input shaft. At this time, since the first one-way clutch and the second one-way clutch are built with the engagement direction reversed, the rotation of the input shaft is not transmitted to the input member of the speed reducer, and the speed reduction mechanism does not act. The output shaft rotates smoothly.

  In the speed reducer according to the present invention, the speed reduction mechanism may be any of a roller speed reduction mechanism, a wave gear speed reduction mechanism, a planetary gear mechanism, a traction drive device, a cycloid speed reduction mechanism, and a ball speed reduction device. These speed reduction mechanisms have the following configuration.

  In the roller type speed reduction mechanism, an eccentric disk that can rotate around an input shaft is used as an input member, and a cylindrical torque transmission shaft that can rotate around an output shaft is used as an output member. A cage is provided at the shaft end, a roller is accommodated inside each of a plurality of pockets formed in the cage, and a fixedly arranged internal gear is provided outside the cage, and an inner periphery of the internal gear is provided. The number of the inner teeth is larger than the number of rollers, and the rotation of the eccentric disc causes the rollers to sequentially mesh with the inner teeth of the internal gear to rotate the torque transmission shaft at a reduced speed.

  The wave gear type reduction mechanism has an elliptical wave generator that can rotate around an input shaft as an input member, and a cylindrical torque transmission shaft that can rotate around an output shaft as an output member. An external gear that is elastically deformed elliptically by the rotation of the wave generator is provided at the shaft end of the transmission shaft, and an external gear that is elastically deformed elliptically by the rotation of the wave generator is positioned outside in the major axis direction. The teeth are sequentially meshed with the inner teeth on the inner circumference of the fixedly arranged internal gear provided on the outer side, and the rotation direction of the wave generator is reversed by the difference in the number of teeth between the inner teeth and the outer teeth per rotation of the wave generator. The torque transmission shaft is decelerated and rotated in the direction.

  In the planetary gear mechanism, a sun gear rotatable around an input shaft is used as an input member, and a cylindrical torque transmission shaft rotatable around the output shaft is used as an output member. An internal gear having a plurality of internal teeth on the inner periphery is provided at the end, a plurality of planetary gears are incorporated between the internal gear and the sun gear, and the planetary gear is rotated by rotation of the sun gear. While rotating, the torque transmission shaft is rotated at a reduced speed.

  In the traction drive device, a solar wheel rotatable around an input shaft is used as an input member, and a cylindrical torque transmission shaft rotatable around an output shaft is used as an output member. An inscribed vehicle is provided at the part, and a plurality of planetary vehicles are incorporated between the inscribed vehicle and the solar vehicle, and the planetary vehicle is rotated by the rotation of the solar vehicle and revolves to reduce the torque transmission shaft. I try to let them.

  In the cycloid reduction mechanism, an eccentric inner ring that can rotate around an input shaft serves as an input member, and a cylindrical torque transmission shaft that can rotate about the output shaft serves as an output member. A plurality of inner pins are supported by a disk portion provided at the shaft end, each of the inner pins has a circular hole, and a plurality of curves including trochoidal curves such as epitrochoid curves are provided on the outer periphery. The curved curve plate is rotatably provided outside the eccentric inner ring, the curve is engaged with a plurality of freely rotatable outer pins provided at equal intervals in the circumferential direction, and the eccentric rotation of the eccentric inner ring causes the curve plate The torque transmission shaft is decelerated and rotated by taking out the rotational motion of the torque by the inner pin.

  In the ball speed reducer, an eccentric disk that is rotatable about an input shaft is used as an input member, and a speed reduction plate is rotatably supported on the outer periphery of the eccentric disk, and the cylinder is rotatable about the output shaft. The torque transmission shaft is an output member, an output plate is provided at the shaft end of the torque transmission shaft, and a plurality of ball grooves made up of hypocycloidal curves are formed on the surface of the reduction plate facing the output plate. The output plate is formed with an epicycloid curve on the surface facing the speed reduction plate, and a plurality of ball grooves having a number of grooves smaller than that of the hypocycloid curve are formed, and a ball is incorporated at the intersection of the ball grooves, The eccentric transmission of the eccentric disk causes the torque transmission shaft to rotate at a reduced speed by rolling the ball in the ball groove.

  In the present invention, as described above, when the input shaft rotates in one direction, the rotation of the input shaft is decelerated and transmitted to the output shaft, and when rotated in the other direction, the rotation of the input shaft is transmitted to the output shaft. Therefore, it is possible to obtain a reduction gear that can be used in a wide range of applications.

1 is a longitudinal sectional view showing a first embodiment of a reduction gear according to the present invention. Sectional view along the line II-II in FIG. Sectional drawing which expands and shows the incorporating part of the 1st one-way clutch of FIG. Sectional view along line IV-IV in FIG. Sectional view along line V-V in FIG. Sectional view along line VI-VI in FIG. Sectional view showing another example of centering spring Sectional drawing which shows the other example of a reverse input interruption | blocking clutch A longitudinal sectional view showing a second embodiment of a reduction gear according to the present invention Sectional view along line XX in FIG. A longitudinal sectional view showing a third embodiment of a reduction gear according to the present invention Sectional drawing along the XII-XII line of FIG. A longitudinal sectional view showing another example of the speed reduction mechanism of the speed reduction device according to the present invention Sectional drawing which expands and shows a part of meshing part of the internal gear and external gear of the deceleration mechanism part of FIG. Sectional view along line XV-XV in FIG. A longitudinal sectional view showing another example of the speed reduction mechanism of the speed reduction device according to the present invention Sectional drawing along the XVII-XVII line of FIG. A longitudinal sectional view showing another example of the speed reduction mechanism of the speed reduction device according to the present invention Sectional view along line XIX-XIX in FIG. A longitudinal sectional view showing another example of the speed reduction mechanism of the speed reduction device according to the present invention Sectional view along line XXI-XXI in FIG. A longitudinal sectional view showing another example of the speed reduction mechanism of the speed reduction device according to the present invention Sectional view along the line XXIII-XXIII in FIG. A longitudinal sectional view showing a conventional speed reducer

  Embodiments of the present invention will be described below with reference to the drawings. 1 to 6 show a first embodiment of a reduction gear device according to the present invention. As shown in FIG. 1, the housing 1 has a cylindrical shape. The housing 1 is divided into two in the axial direction, and a first divided housing 1a and a second divided housing 1b are provided.

  The first divided housing 1a and the second divided housing 1b are coupled and integrated by tightening bolts (not shown). The first divided housing 1a has a large-diameter recess 2 on the inner periphery of the end facing the second divided housing 1b. Is formed.

  As shown in FIGS. 1 and 2, an internal gear 3 is press-fitted into the large-diameter recess 2, and a plurality of internal teeth 4 are provided on the inner periphery of the internal gear 3.

  As shown in FIG. 1, an end plate 5 is provided at the open end of the first divided housing 1 a, and an input shaft 7 is inserted into a shaft insertion hole 6 formed in the center of the end plate 5. The input shaft 7 is rotatably supported by a bearing 8 incorporated in the shaft insertion hole 6, is arranged coaxially with the internal gear 3, and has an internal tooth at the end of the shaft located in the housing 1a. An eccentric disk 9 is provided as an input member that can rotate within the gear 3.

In FIG. 1, the two eccentric discs 9 integrated with the input shaft 7 at the inner periphery are formed at an interval in the axial direction. However, the number of the eccentric discs 9 is arbitrary, and one eccentric disc 9 is formed. The disc 9 may be used. As shown in the figure, when two eccentric discs 9 are provided, the center of the cylindrical outer diameter surface 10 is attached so that its position is shifted by 180 ° in the circumferential direction. Δ 3 shows the eccentric amount of the center O ₁ of the cylindrical radially outer surface 10 of the center O ₀ with eccentric disc 9 of the input shaft 7.

  As shown in FIGS. 1 and 3, a first one-way clutch 11 is assembled between the outer diameter surface of the input shaft 7 and the inner diameter surface of the eccentric disk 9. The first one-way clutch 11 is provided with a cylindrical clutch surface 12 on the outer periphery of the input shaft 7, and the inner circumferential surface of the clutch outer ring 13 press-fitted into the inner diameter surface of the eccentric disk 9 is circumferentially connected to the clutch surface 12. A plurality of inclined cam surfaces 14 forming a narrow wedge-shaped space from one end to the other end are provided at intervals in the circumferential direction, and a retainer 15 incorporated between the clutch outer ring 13 and the input shaft 7 is provided. The pocket 16 is formed at a position facing each cam surface 14, and a clutch roller 17 and an elastic member 18 that presses the clutch roller 17 toward the narrow portion of the wedge-shaped space are assembled in each pocket 16. It is made of a roller type.

  In the first one-way clutch 11, when the input shaft 7 rotates in the direction indicated by the arrow in FIG. 3 (counterclockwise direction), the clutch roller 17 engages with the clutch surface 12 and the cam surface 14. The rotation is transmitted to the eccentric disk 9.

  As shown in FIG. 1, a bearing 19 is press-fitted into each of the outer diameter surfaces 10 of the two eccentric disks 9.

  An output shaft 20 is inserted inside the second divided housing 1b. The output shaft 20 is arranged coaxially with the input shaft 7.

  A cylindrical portion 21 that covers the shaft end portion of the input shaft 7 is integrally provided at the shaft end portion of the output shaft 20 that faces the input shaft 7, and the inner diameter surface of the cylindrical portion 21 and the shaft end portion of the input shaft 7 are outside. A second one-way clutch 22 is incorporated between the radial surfaces.

  As shown in FIG. 4, the second one-way clutch 22 is provided with a cylindrical clutch surface 23 on the outer periphery of the shaft end portion of the input shaft 7, and the clutch outer ring 24 press-fitted into the inner diameter surface of the cylinder portion 21 is provided with the clutch. A plurality of inclined cam surfaces 25 forming a wedge-shaped space with the surface 23 are provided at intervals in the circumferential direction, and the cage 26 incorporated between the clutch surface 23 and the clutch outer ring 24 is provided with each inclined surface. A roller type in which a pocket 27 is formed at a position facing the cam surface 25, and a clutch roller 28 and an elastic member 29 for pressing the clutch roller 28 toward a narrow portion of the wedge-shaped space are incorporated in each pocket 27. It consists of things.

  In the second one-way clutch 22, when the input shaft 7 rotates in the direction indicated by the arrow in FIG. 4 (clockwise direction), the clutch roller 28 engages with the clutch surface 23 and the inclined cam surface 25. The rotation is transmitted to the cylinder portion 21, and the first one-way clutch 11 is incorporated so that the engagement direction is reversed.

  As shown in FIG. 1, a torque transmission shaft 30 as a cylindrical output member is provided outside the shaft end portion of the output shaft 20. The torque transmission shaft 30 is rotatably supported by a bearing 31 incorporated in the inner diameter surface of the second divided housing 1b and a bearing 32 incorporated in the shaft end portion of the input shaft 7, and is disposed coaxially with the input shaft 7. ing.

  The torque transmission shaft 30 is provided with a cage 33 at the shaft end facing the eccentric disc 9, and the cage 33 is rotatable between the bearing 19 on the eccentric disc 9 and the facing portion of the internal gear 3. ing.

  A plurality of pockets 34 arranged in the circumferential direction at equal intervals are formed in a double row in the cage 33, and the pockets 34 in each row are provided on the outer diameter surface 10 of the two eccentric disks 9. The pockets 34 in one row and the pockets 34 in the other row are offset by a half pitch in the circumferential direction.

  The number of pockets 34 in each row is smaller than the number of internal teeth 4 of the internal gear 3, and one torque transmission roller 35 is accommodated in each pocket 34 so as to be movable in the radial direction.

  The torque transmission roller 35 can mesh with the internal teeth 4 of the internal gear 3, while the internal teeth 4 have a tooth profile that allows all the torque transmission rollers 35 to be in contact with each other at the same time. In order to allow all the torque transmission rollers 35 to be in contact with each other, as described in Patent Document 1, the rotation angle of the output shaft 20 is within a range corresponding to one pitch of the internal teeth 4 of the internal gear 3. The output shaft 20 is rotated by the rotation of the eccentric disk 9, and at this time, the tooth profile having one tooth corresponding to the curve outside the torque transmission roller 35 among the curves parallel to the locus drawn by the center of the torque transmission roller 35 is obtained. Yes.

  As shown in FIGS. 1 and 4, a reverse input cutoff clutch 40 is incorporated between the inner diameter surface of the torque transmission shaft 30 and the outer diameter surface of the cylindrical portion 21 of the output shaft 20.

  The reverse input cut-off clutch 40 forms a cylindrical surface 41 on the outer periphery of the cylindrical portion 21, and a narrow wedge-shaped space is formed on the inner periphery of the torque transmission shaft 30 so as to reach both ends in the circumferential direction with the cylindrical surface 41. A plurality of V-shaped cam surfaces 42 are formed at intervals in the circumferential direction, and a roller 43 assembled between each cam surface 42 and the cylindrical surface 41 is held by a cage 44, and an end of the cage 44 The retainer 44 is elastically held in a neutral position where the roller 43 is disengaged from the cylindrical surface 41 and the cam surface 42 by the centering spring 45 incorporated inside the part, and the circular shape formed on the inner surface of the end plate of the second divided housing 1b. A rotation resistance is applied to the cage 44 by a sliding spring 47 in the recess 46.

  Here, as shown in FIG. 5, the centering spring 45 has a configuration in which a pair of pressing pieces 45b are formed outwardly at the cut end of the ring portion 45a from which a part in the circumferential direction is cut, and the pressing piece 45b Is incorporated into a notch 49 formed at the end of the torque transmission shaft 30 from a notch 48 formed at the end of the retainer 44, and the end surfaces of the notch 48 and the notch 49 facing each other in the circumferential direction are arranged. The rollers 43 are held in a neutral position by pressing in opposite directions.

  On the other hand, as shown in FIG. 6, the sliding spring 47 has a configuration in which a pair of pressing pieces 47 b are formed inwardly at a separation end of a ring portion 47 a from which a part in the circumferential direction is separated. 47a is elastically brought into contact with the inner diameter surface of the circular recess 46, and the pair of pressing pieces 47b is engaged to be engaged with the circumferentially opposed end surfaces of the cutout portion 48 formed at the end portion of the retainer 44. When the container 44 is rotated, the sliding spring 47 is slid along the inner diameter surface of the circular recess 46 so as to impart rotational resistance to the cage 44.

  The speed reduction device shown in the first embodiment has the above-described structure. When the input shaft 7 rotates in the direction indicated by the arrow in FIG. 3, the clutch roller 17 of the first one-way clutch 11 is moved to the clutch surface 12 and the inclined cam surface 14. , The rotation of the input shaft 7 is transmitted to the eccentric disk 9, and the eccentric disk 9 rotates in the same direction as the input shaft 7. Due to the rotation of the eccentric disk 9, the torque transmission roller 35 sequentially meshes with the internal teeth 4 of the internal gear 3, and the torque transmission roller 35 corresponds to one tooth of the internal teeth 4 per one rotation of the input shaft 7. Only in the circumferential direction, the torque transmission shaft 30 rotates at a reduced speed.

  Further, when the torque transmission shaft 30 rotates, the torque transmission shaft 30 and the cage 44 rotate relative to each other because the cage 44 of the reverse input cutoff clutch 40 is provided with a rotational resistance by the sliding spring 47. By the relative rotation, the roller 43 engages and locks with the cylindrical surface 41 and the cam surface 42, the rotation of the torque transmission shaft 30 is transmitted to the output shaft 20, and the output shaft 20 rotates at a reduced speed. At this time, since the first one-way clutch 11 and the second one-way clutch 22 are incorporated so that the engagement directions are reversed, the second one-way clutch 22 is not engaged, and the output shaft 20 rotates smoothly.

  Thus, when the input shaft 7 rotates in one direction, the rotation is decelerated and transmitted to the output shaft 20.

  Here, when the torque transmission shaft 30 and the cage 44 rotate relative to each other, the centering spring 45 shown in FIG. 5 is elastically deformed. For this reason, when the input shaft 7 stops, the retainer 44 of the reverse input cutoff clutch 40 is returned and rotated by the restoring elasticity of the centering spring 45, and the roller 43 is returned to the neutral position.

  On the contrary, when the input shaft 7 rotates in the direction opposite to the direction indicated by the arrow in FIG. 3 (the direction indicated by the arrow in FIG. 4), the clutch roller 28 of the second one-way clutch 22 moves to the clutch surface 23 and the inclined cam surface 25. The rotation of the input shaft 7 is transmitted to the output shaft 20, and the output shaft 20 rotates at the same speed as the input shaft 7. At this time, since the first one-way clutch 11 and the second one-way clutch 22 are assembled so that the engaging directions are reversed, the rotation of the input shaft 7 is not transmitted to the eccentric disk 9, but the torque transmitting roller 35 and the internal teeth Since the speed reduction mechanism portion composed of the gear 3 does not act, the output shaft 20 rotates smoothly.

  Thus, in the speed reduction device shown in the first embodiment, the rotation of the input shaft 7 can be decelerated and transmitted to the output shaft 20 by rotation in one direction of the input shaft 7, By rotating the input shaft 7 in the other direction, the rotation of the input shaft 7 can be transmitted to the output shaft 20 at the same speed, so that a speed reducer that can be used in a wide range of applications can be obtained.

  In the reduction gear shown in the first embodiment, since the rotational direction of the torque transmission shaft 30 of the roller type reduction gear is a predetermined design matter, the reverse input cut-off clutch 40 is connected to the torque rotation shaft 30. It may be of a one-way lock type that locks by rotation in one direction.

  As shown in FIG. 7, one of the pair of pressing pieces 45b provided on the centering spring 45 is bent toward the end surface 49a facing the notch 49, and the tip of the bent piece 45c is brought into contact with the end surface 49a. By making contact, it is possible to allow relative rotation in one direction in the cage 44 of the reverse input cutoff clutch 40 and the torque transmission shaft 30 and prevent relative rotation in the other direction. The clutch 40 can be used as a one-way lock type.

  FIG. 8 shows an example in which a one-way lock type reverse input cutoff clutch 40 is incorporated between the outer periphery of the cylindrical portion 21 of the output shaft 20 and the torque transmission shaft 30. The one-way lock type reverse input shut-off clutch 40 has a narrow wedge from one end to the other end in the circumferential direction between the inner periphery of the torque transmission shaft 30 and the cylindrical surface 41 formed on the outer periphery of the cylindrical portion 21. An inclined cam surface 50 forming a shape space is formed, and a roller 43 is incorporated between the inclined cam surface 50 and the cylindrical surface 41.

  In the reverse input cutoff clutch 40 having the above-described configuration, the roller 43 engages with and locks the cylindrical surface 41 and the inclined cam surface 50 only when the torque transmission shaft 30 rotates in the direction indicated by the arrow in FIG. The rotation of the torque transmission shaft 30 is transmitted from the cylindrical portion 21 to the output shaft 20.

  9 and 10 show a second embodiment of the reduction gear according to the present invention. Here, in the reduction gear shown in the first embodiment, the output shaft 20 rotates at a reduced speed in the direction opposite to the rotation direction of the input shaft 7. Therefore, in the second embodiment, the first embodiment is the same as the first embodiment. A third one-way clutch 60 is used instead of the reverse input cutoff clutch 40 shown in the embodiment. Since other configurations are the same as those of the first embodiment shown in FIG. 1, the same components are denoted by the same reference numerals, and description thereof is omitted.

  Here, the third one-way clutch 60 forms a cylindrical clutch surface 61 on the outer periphery of the cylindrical portion 21, and the inner periphery of the torque transmission shaft 30 is connected to the clutch surface 61 from one end to the other end in the circumferential direction. A plurality of inclined cam surfaces 62 forming a narrow wedge-shaped space are provided at intervals in the circumferential direction, and a cage 63 incorporated between the outer periphery of the cylindrical portion 21 and the inner periphery of the torque transmission shaft 30 is provided. Has a pocket 64 at a position facing each inclined cam surface 62, and a clutch roller 65 and an elastic member 66 for pressing the clutch roller 65 toward the narrow portion of the wedge-shaped space are incorporated in the pocket 64. It is configured.

  In the reduction gear shown in the second embodiment, when the input shaft 7 rotates in the direction indicated by the arrow in FIG. 10, the first one-way clutch 11 is engaged, and the internal gear 3 and the torque transmission roller 35 are formed. The torque transmission shaft 30 rotates in the direction opposite to the rotation direction of the input shaft 7 as shown by the arrow in FIG. Due to the rotation of the torque transmission shaft 30, the clutch roller 65 is engaged with the clutch surface 61 and the inclined cam surface 62, the rotation of the torque transmission shaft 30 is transmitted to the output shaft 20, and the output shaft 20 rotates at a reduced speed.

  On the other hand, when the input shaft 7 rotates in the direction opposite to the direction indicated by the arrow in FIG. 10, the second one-way clutch 22 shown in FIG. 10 is engaged, and the output shaft 20 moves in the same direction as the input shaft 7 at the same speed. Rotate.

  Similarly to the first embodiment, the second embodiment can reduce the rotation of the input shaft 7 and transmit it to the output shaft 20 by rotating the input shaft 7 in one direction. By rotating the input shaft 7 in the other direction, the rotation of the input shaft 7 can be transmitted to the output shaft 20 at the same speed.

  11 and 12 show a third embodiment of the reduction gear according to the present invention. In this embodiment, a cylindrical housing 70 that is fixedly arranged is divided into a first divided housing 70a and a second divided housing 70b, and the first divided portion is formed on the inner diameter surface of the opposite end of the divided surface. A recess 71 having a large diameter is formed across the housing 70a and the second divided housing 70b, and an internal gear 72 having a plurality of internal teeth 73 and a clutch engagement surface 74 on the inner periphery thereof is rotatably assembled in the recess 71. It is crowded.

  In addition, the input shaft 75 and the output shaft 76 whose shaft ends are covered by the housing 70 are arranged coaxially with the housing 70, and are rotatably supported by bearings 77 incorporated in the housing 70. The two eccentric discs 78 rotatable within the inner teeth 73 and the clutch wheel 79 rotatable within the clutch fitting surface 74 are integrally provided, and bearings are provided on the outer diameter surfaces of the eccentric discs 78. 80 is provided.

  On the other hand, a cage 81 that can rotate between the bearing 80 and the internal gear 72 is provided at the shaft end of the output shaft 76, and the cage 81 has a plurality of smaller numbers than the internal teeth 73 at positions facing each bearing 80. Pockets 82 are formed at intervals in the circumferential direction, and a torque transmission roller 83 is incorporated in the pocket 82.

  Furthermore, the input shaft 75 is rotated by being engaged between the clutch engagement surface 74 of the internal gear 72 and the outer diameter surface of the clutch ring 79 provided on the input shaft 75 when the input shaft 75 rotates in one direction. A torque transmission one-way clutch 84 for transmitting to the internal gear 72 is incorporated, and the torque transmission one-way clutch 84 is engaged between the inner diameter surface of the recess 71 of the first divided housing 70 a and the outer diameter surface of the internal gear 72. A locking one-way clutch 85 with the opposite direction is incorporated.

  Here, as shown in FIG. 12, the torque transmission one-way clutch 84 is formed with a cylindrical clutch surface 86 on the outer periphery of the clutch wheel 79, and on the inner periphery of the clutch outer ring 87 press-fitted into the clutch fitting surface 74. An inclined cam surface 88 that forms a wedge-shaped space with the clutch surface 86 is provided, and the cage 89 assembled between the clutch outer ring 87 and the clutch surface 86 has a pocket at a position facing the inclined cam surface 88. 90 is formed, and a clutch roller 91 and an elastic member 92 that presses the clutch roller 91 toward a narrow portion of the wedge-shaped space are incorporated in the pocket 90.

  On the other hand, the one-way clutch 85 for locking is provided with a clutch surface 93 on the outer periphery of the internal gear 72, and the clutch surface 93 is connected to the inner periphery of the clutch outer ring 94 press-fitted into the inner diameter surface of the recess 71 of the first divided housing 70a. An inclined cam surface 95 that forms a wedge-shaped space is provided, and a retainer 96 assembled between the clutch outer ring 94 and the clutch surface 93 is provided with a pocket 97 at a position facing the inclined cam surface 95. The clutch roller 98 and an elastic member 99 that presses the clutch roller 98 toward the narrow portion of the wedge-shaped space are incorporated.

  In the torque transmission one-way clutch 84 and the locking one-way 85 configured as described above, the direction of the wedge-shaped space is reversed, and the engagement direction of the clutch rollers 91 and 98 is reversed.

  The reduction gear shown in the third embodiment has the above-described configuration. When the input shaft 75 rotates in the direction indicated by the arrow in FIGS. 11 and 12, the clutch roller 91 of the torque transmission one-way clutch 84 is moved to the clutch surface 86 and The rotation of the input shaft 75 is transmitted to the internal gear 72 by engaging with the inclined cam surface 88, and the internal gear 72 rotates in the same direction as the input shaft 75.

  At this time, the torque transmitting one-way clutch 84 and the locking one-way clutch 85 are built with the engagement directions reversed, so that the internal gear 72 rotates smoothly and the internal gear 73 of the internal gear 72 is connected to the internal gear 73. The meshing torque transmission roller 83 also rotates in the same direction as the internal gear 72, and the cage 81 that holds the torque transmission roller 83 also rotates integrally, so that the output shaft 76 rotates in the same direction as the input shaft 75. Rotates at the same speed.

  Contrary to the above, when the input shaft 75 rotates in the direction opposite to the direction indicated by the arrow, the torque transmitting roller 83 sequentially meshes with the internal teeth 73 of the internal gear 72 by the rotation of the eccentric disk 78. At this time, the torque transmission one-way clutch 84 is free, and the clutch roller 98 of the locking one-way clutch 85 is engaged with the clutch surface 93 and the inclined cam surface 95, so that the internal gear 72 is fixed to the first divided housing 70a. The torque transmission roller 83 smoothly meshes with the inner teeth and moves in the circumferential direction by one tooth of the inner teeth 73 per one rotation of the input shaft 75, and the output shaft 76 rotates at a reduced speed.

  Thus, also in the reduction gear shown in the third embodiment, the rotation of the input shaft 75 is caused by the rotation of the input shaft 75 in one direction, as in the first and second embodiments. The rotation can be decelerated and transmitted to the output shaft 76, and the rotation of the input shaft 75 can be transmitted to the output shaft 76 at the same speed by rotating the input shaft 75 in the other direction. A speed reducer that can be used in a wide range of applications can be obtained.

  In the embodiment shown in FIG. 1, the roller type reduction mechanism is shown as a reduction mechanism that reduces the rotation of the input shaft 7 and transmits it to the output shaft 20, but the reduction mechanism is not limited to this. 12 to 23 show other examples of the speed reduction mechanism.

  The speed reduction mechanism shown in FIGS. 13 to 15 includes a wave gear type speed reduction mechanism 100. The wave gear type speed reduction mechanism 100 includes an internal gear 101 fixed to the inner surface of the first divided housing 1a of the housing 1, a wave generator 111 as an input member rotatably supported by the input shaft 7, and a wave thereof. An externally deformable external gear 121 is provided outside the generator 111.

  The internal gear 101 has a plurality of internal teeth 102 having an involute tooth profile on the inner periphery. The wave generator 111 includes an elliptical cam 112 and a bearing 113 fitted to the elliptical outer peripheral surface of the cam 112, and the cam 112 is rotatable about the input shaft 7. A first one-way clutch 11 shown in FIG. 3 is assembled between the inner diameter surface of the input shaft 7 and the outer diameter surface of the input shaft 7.

  Each of the inner ring 114 and the outer ring 115 of the bearing 113 is formed of an elastic body, and the inner ring 114 is fixed to the outer periphery of the cam 112 and has an elliptical shape. On the other hand, the outer ring 115 is elastically deformed into an elliptical shape via the rolling elements 116.

  The external gear 121 has a cup shape with an end plate portion 122 integrated at the shaft end portion of the torque transmission shaft 30 as an output member. The external gear 121 is thin and elastically deformable, and the number of external teeth 123 formed on the outer periphery thereof is smaller than the internal teeth 102 of the internal gear 101. The external gear 121 is fitted to the outer periphery of the bearing 113 of the wave generator 111 and elastically deforms into an elliptical shape, and external teeth 123 positioned in the major axis direction mesh with the internal teeth 102 of the internal gear 101. .

  In the wave gear type speed reduction mechanism 100 having the above structure, when the input shaft 7 rotates in the direction indicated by the arrow in FIG. 15, the clutch roller 17 of the first one-way clutch 11 is engaged with the clutch surface 12 and the inclined cam surface 14. The rotation of the input shaft 7 is transmitted to the wave generator 111, and the wave generator 111 rotates in the same direction as the input shaft 7. Due to the rotation of the wave generator 111, the external gear 121 is bent into an elliptical shape, and the external teeth 123 sequentially mesh with the internal teeth 102 of the internal gear 101, and the external teeth 123 are rotated per one rotation of the input shaft 7. The torque transmission shaft 30 decelerates and rotates in the direction opposite to the rotation direction of the input shaft 7 by shifting in the circumferential direction by a number difference from the internal teeth 102.

  Further, when the torque transmission shaft 30 rotates, the reverse input cutoff clutch 40 shown in FIG. 4 is locked, the rotation of the torque transmission shaft 30 is transmitted to the output shaft 20, and the output shaft 20 rotates at a reduced speed. At this time, since the first one-way clutch 11 and the second one-way clutch 22 are incorporated so that the engagement directions are reversed, the second one-way clutch 22 is not engaged, and the output shaft 20 rotates smoothly. Thus, when the input shaft 7 rotates in one direction, the rotation is decelerated and transmitted to the output shaft 20.

  Conversely, when the input shaft 7 rotates in the direction opposite to the direction indicated by the arrow in FIG. 15, the second one-way clutch 22 shown in FIG. 4 is engaged, and the rotation of the input shaft 7 is transmitted to the output shaft 20. The output shaft 20 rotates at the same speed as the input shaft 7. At this time, since the first one-way clutch 11 and the second one-way clutch 22 are incorporated so that the engaging directions are reversed, the rotation of the input shaft 7 is not transmitted to the wave generator 111, and the external gear 121 and the internal gear 101. Therefore, the output shaft 20 rotates smoothly.

  As described above, even in the reduction gear employing the wave gear type reduction mechanism 100, the rotation of the input shaft 7 can be decelerated and transmitted to the output shaft 20 by the rotation of the input shaft 7 in one direction. Since the rotation of the input shaft 7 in the other direction can transmit the rotation of the input shaft 7 to the output shaft 20 at the same speed, a reduction gear that can be used in a wide range of applications can be obtained.

  The speed reduction mechanism shown in FIGS. 16 and 17 includes a planetary gear mechanism 130. In this planetary gear mechanism 130, a sun gear 131 as an input member is provided outside the input shaft 7, and an internal gear 132 is integrally provided at the shaft end portion of the torque transmission shaft 30 as an output member. Each of the plurality of planetary gears 133 is meshed with the inner teeth 132a formed on the inner periphery of 132 and the outer teeth 131a formed on the outer periphery of the sun gear 131, and the plurality of planetary gears 133 are supported by the carrier 134. The rotation of the sun gear 131 causes the planetary gear 133 to rotate and revolve to rotate the torque transmission shaft 30 at a reduced speed.

  In the reduction gear employing the planetary gear mechanism 130, the first one-way clutch 11 is incorporated between the input shaft 7 and the sun gear 131 as the input member, and the torque transmission shaft 30 as the output member and the cylinder of the output shaft 20 are combined. As the reverse input cutoff clutch 40 is incorporated between the parts 21, the rotation of the input shaft 7 is decelerated and transmitted to the output shaft 20 by the rotation of the input shaft 7 in one direction. The rotation in the direction causes the rotation of the input shaft 7 to be transmitted to the output shaft 20 through the second one-way clutch 22 at the same speed.

  The speed reduction mechanism shown in FIGS. 18 and 19 includes a traction drive device. In this traction drive device, a sun wheel 141 as an input member is provided outside the input shaft 7, and a cylindrical inscribed wheel 142 is integrally provided at the shaft end portion of the torque transmission shaft 30 as an output member. A plurality of planetary wheels 143 are incorporated between the inner diameter surface of the contact wheel 142 and the outer diameter surface of the sun wheel 141, each planet wheel 143 is supported by the carrier 144, and the planet wheel 133 is rotated by the rotation of the sun wheel 141. The torque transmission shaft 30 is rotated at a reduced speed by revolving.

  In the speed reducer employing the traction drive device 140, the first one-way clutch 11 is incorporated between the input shaft 7 and the sun wheel 141 as the input member, and the torque transmission shaft 30 as the output member and the cylinder of the output shaft 20 are assembled. As the reverse input cutoff clutch 40 is incorporated between the parts 21, the rotation of the input shaft 7 is decelerated and transmitted to the output shaft 20 by the rotation of the input shaft 7 in one direction. The rotation in the direction causes the rotation of the input shaft 7 to be transmitted to the output shaft 20 through the one-way clutch 22 at the same speed.

  The speed reduction mechanism shown in FIGS. 20 and 21 includes a cycloid speed reduction mechanism 150. The cycloid speed reduction mechanism 150 rotatably supports a curved plate 153 via a plurality of rolling elements 152 on the outer side of an eccentric inner ring 151 as an input member rotatable about the input shaft 7, and the curved plate 153. A plurality of curves 153a made of a trochoid curve such as an epitrochoid curve are formed on the outer periphery of the housing, and a plurality of outer pins 154a are provided on the end 154 of the housing 1 so as to be able to rotate. Are engaged with each other.

  Further, a plurality of inner pins 156 are provided at equal intervals in the circumferential direction on a disk portion 155 provided at the shaft end portion of the torque transmission shaft 30, and each of the inner pins 156 is the same number as the inner pins formed on the curved plate 153. Inserted into each of the circular holes 157, the curved plate 153 is eccentrically oscillated by the eccentric rotation of the eccentric inner ring 151, and the rotational movement is taken out by the inner pin 156 to rotate the torque transmission shaft 30 at a reduced speed.

  In the reduction gear employing the cycloid reduction mechanism 150, the first one-way clutch 11 is incorporated between the input shaft 7 and the eccentric inner ring 151 as the input member, and the torque transmission shaft 30 and the output shaft 20 as the output members are connected. By incorporating the reverse input cutoff clutch 40 between the cylindrical portions 21, the rotation of the input shaft 7 is decelerated and transmitted to the output shaft 20 by the rotation of the input shaft 7 in one direction. By rotating in the other direction, the rotation of the input shaft 7 is transmitted to the output shaft 20 through the second one-way clutch 22 at the same speed.

  The speed reduction mechanism shown in FIGS. 22 and 23 includes a ball speed reduction device 160. This ball speed reducer 160 rotatably supports a speed reduction plate 163 via a rolling bearing on an outer side of an eccentric disc 161 as an input member that can rotate about an input shaft 7, and centering on an output shaft 20. An output plate 164 that is axially opposed to the speed reduction plate 163 is integrally provided at the shaft end portion of the torque transmission shaft 30 as a rotatable output member, and the speed reduction plate 163 is axially provided on the inner surface of the end plate of the housing 1. The opposing Oldham plate 165 is fixed, a plurality of ball grooves 166 each having a hypocycloidal curve are provided on both side surfaces of the speed reducing plate 163, and the output plate 164 and Oldham plate 165 are epicycloidal on the surface facing the speed reducing plate 163. A plurality of ball grooves 167 having a number of grooves smaller than the number of the ball grooves 166 of the hypocycloid curve are formed, and the ball grooves 166, 1 opposed in the axial direction are formed. Built the ball 168 at the intersection of 7, so as to decelerate rotation of the torque transmission shaft 30 by the rolling of the balls 168 in the ball grooves 166 and 167 by the eccentric rotation of the eccentric disc 161.

  In the speed reduction device employing the ball speed reduction device 160, the first one-way clutch 11 is incorporated between the input shaft 7 and the eccentric disk 161 as the input member, and the torque transmission shaft 30 and the output shaft 20 as the output members are assembled. By incorporating the reverse input cutoff clutch 40 between the cylindrical portions 21, the rotation of the input shaft 7 is decelerated and transmitted to the output shaft 20 by the rotation of the input shaft 7 in one direction. By rotating in the other direction, the rotation of the input shaft 7 is transmitted to the output shaft 20 through the second one-way clutch 22 at the same speed.

3 Internal gear 4 Internal tooth 7 Input shaft 9 Eccentric disc (input member)
11 First one-way clutch 20 Output shaft 21 Tube portion 22 Second one-way clutch 30 Torque transmission shaft (output member)
33 Cage 40 Reverse input shut-off clutch 100 Wave gear type reduction mechanism 101 Internal gear 102 Internal tooth 111 Wave generator (input member)
121 external gear 123 external gear 130 planetary gear mechanism 131 sun gear (input member)
131a External tooth 132 Internal gear 132a Internal tooth 133 Planetary gear 140 Traction drive device 141 Solar wheel (input member)
142 inscribed vehicle 143 planetary vehicle 150 cycloid reduction mechanism 151 eccentric inner ring (input member)
153 Curved plate 153a Curve 154a Outer pin 155 Disk portion 156 Inner pin 157 Circular hole 160 Ball reducer 161 Eccentric disc (input member)
163 Deceleration plate 164 Output plate 166 Ball groove 167 Ball groove 168 Ball

Claims (7)

  An input shaft, an output shaft that is arranged coaxially with the input shaft, and that is provided with a cylindrical portion covering the shaft end of the input shaft at the shaft end, an input member fitted to the input shaft, and the output shaft A reduction mechanism that decelerates the rotation and outputs the output from the output member when rotation is transmitted from the input shaft to the input member; and the input shaft and the deceleration A first one-way clutch that is incorporated between the input members of the mechanism and transmits the rotation of the input shaft in one direction to the input member; and the cylinders of the input shaft and the output shaft with the first one-way clutch and the engagement direction being reversed. And a second one-way clutch that transmits rotation in the other direction of the input shaft to the output shaft, and is incorporated between the inner diameter surface of the output member of the speed reduction mechanism and the outer diameter surface of the cylindrical portion of the output shaft. The rotation of the output member is transmitted to the output shaft and output from the output shaft Reduction gear consisting of a reverse input blocking clutch for interrupting the transmission of rotation to the wood.   In the speed reduction mechanism, an eccentric disc rotatable about the input shaft is used as an input member, and a cylindrical torque transmission shaft rotatable about the output shaft is used as an output member. A cage is provided at the shaft end of each of the two, a roller is accommodated in each of a plurality of pockets formed in the cage, and a fixedly arranged internal gear is provided outside the cage. It has a roller-type speed reduction mechanism in which inner teeth larger than the number of rollers are provided on the circumference, and the torque transmission shaft is decelerated and rotated by sequentially engaging the rollers with the internal teeth of the internal gear by the rotation of the eccentric disk. The speed reducer according to claim 1.   The speed reduction mechanism has an elliptical wave generator that can rotate around the input shaft as an input member, and a cylindrical torque transmission shaft that can rotate around the output shaft as an output member. An external gear that is elastically deformed elliptically by the rotation of the wave generator is provided at the shaft end of the transmission shaft, and an external gear that is elastically deformed elliptically by the rotation of the wave generator is positioned outside in the major axis direction. The teeth are sequentially meshed with the inner teeth on the inner circumference of the fixedly arranged internal gear provided on the outer side, and the rotation direction of the wave generator is reversed by the difference in the number of teeth between the inner teeth and the outer teeth per rotation of the wave generator. The speed reducer according to claim 1, comprising a wave gear type speed reduction mechanism configured to decelerate and rotate the torque transmission shaft in a direction.   In the speed reduction mechanism, a sun gear rotatable around the input shaft is used as an input member, and a cylindrical torque transmission shaft rotatable around the output shaft is used as an output member. An internal gear having a plurality of internal teeth on the inner periphery is provided at the shaft end, a plurality of planetary gears are incorporated between the internal gear and the sun gear, and the planetary gear rotates by rotation of the sun gear. The speed reducer according to claim 1, comprising a planetary gear mechanism configured to revolve while rotating the torque transmission shaft at a reduced speed.   The deceleration mechanism is configured such that a solar wheel that can rotate about the input shaft serves as an input member, and a cylindrical torque transmission shaft that can rotate about the output shaft serves as an output member. An inscribed vehicle is provided at the shaft end, and a plurality of planetary vehicles are incorporated between the inscribed vehicle and the solar vehicle, and the planetary vehicle is revolved by rotating the solar vehicle to revolve the torque transmission shaft. The speed reducer according to claim 1, comprising a traction drive device that rotates at a reduced speed. In the speed reduction mechanism, an eccentric inner ring that can rotate about the input shaft serves as an input member, and a cylindrical torque transmission shaft that can rotate about the output shaft serves as an output member. A curved plate in which a plurality of inner pins are supported by a disk portion provided at an end of the shaft, a circular hole into which each of the inner pins is inserted, and a plurality of curves composed of trochoidal curves are provided on the outer periphery. Engage with a plurality of rotatable outer pins provided on the outer side of the eccentric inner ring so that the curved line is provided at equal intervals in the circumferential direction;
2. The reduction gear according to claim 1, comprising a cycloid reduction mechanism in which a curved plate is eccentrically oscillated by eccentric rotation of the eccentric inner ring, and the rotational movement is taken out by the inner pin to decelerate and rotate the torque transmission shaft. .   An eccentric disk that can rotate about the input shaft serves as an input member, and a speed reducing plate is rotatably supported on the outer periphery of the eccentric disk, and a cylindrical torque transmission that can rotate about the output shaft The shaft is an output member, an output plate is provided at the shaft end of the torque transmission shaft, and a plurality of ball grooves made of hypocycloidal curves are formed on the surface of the reduction plate facing the output plate. Is formed with an epicycloid curve on the surface facing the speed reduction plate, and a plurality of ball grooves having a number of grooves smaller than that of the hypocycloid curve are formed, and balls are incorporated at intersections of the ball grooves, and the eccentric disk The speed reducer according to claim 1, further comprising a ball speed reducer configured to decelerate and rotate the torque transmission shaft by rolling the ball in the ball groove by eccentric rotation of the ball.

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