JP2005344885A - Planetary roller type speed reducer and speed reducer series - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a planetary roller type speed reducer more compact than a conventional speed reducer; and speed reducer series having the planetary roller type speed reducer and a planetary gear type speed reducer equal in allowable torque and an allowable radial load and common in tie-in with an external member. <P>SOLUTION: This planetary roller type speed reducer 10 has a casing 12, a planetary roller unit 20 formed by installing a plurality of planetary rollers 16 and a sun roller 18 forming an input part in a ring roller 14 integrally formed in the casing 12 in a tight fit state, and a carrier unit 34. The carrier unit 34 is constituted to be rotatably supported by the casing 12 integral with the ring roller 14 in a state of being supported at its opposite ends by an input side carrier bearing 30 and an output side carrier bearing 32. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a planetary roller type reduction device and a reduction gear series including a planetary roller type reduction device and a planetary gear type reduction device.

  The planetary roller unit is assembled with the sun roller, planetary roller, and ring roller pressed in the radial direction as the speed reduction mechanism. The rotation input to the sun roller is decelerated and output as a revolution component of the planetary roller. A planetary roller type speed reducer configured as described above is known (for example, see Patent Document 1). Such a planetary roller type speed reducer includes a carrier unit that rotatably supports the planetary roller, and outputs the revolution component of the planetary roller as the rotation of the carrier unit.

  The ring roller is integrated with the central casing, and the central casing is connected to the joint casing for coupling to the motor and the front casing for accommodating the carrier with axial bolts. That is, an axial bolt hole for integrating all the casings is formed in the central casing integrated with the ring roller.

  The carrier unit includes a roller shaft inserted into the planetary roller, and a carrier that is disposed on the output side of the planetary roller unit and to which the roller shaft is fixed. An output shaft is formed integrally with the carrier. The carrier unit is rotatably supported by the front casing via a bearing on the carrier and output shaft on the output side of the planetary roller unit.

  By the way, the planetary roller unit is similar in structure to a simple planetary gear unit (hereinafter simply referred to as a planetary gear unit), but both have functions more advantageous than the other. For example, the planetary roller unit has lower noise and vibration than the planetary gear unit because there is no gear meshing like the planetary gear unit. Further, the planetary roller unit is extremely small in rotational fluctuation and is suitable for applications such as precision polishing.

  On the other hand, the planetary gear unit has a constant ratio between the input rotation speed and the output rotation speed, and is therefore suitable for applications that require open-loop control or precise rotation angle transmission.

  As described above, the planetary roller unit and the planetary gear unit each have a more advantageous function than the other. Conventionally, the planetary roller type speed reducer and the planetary gear type speed reducer are appropriately selected and used depending on the application. (For example, refer to Patent Document 2).

  Also, in recent years, in view of the similarities of the structure of planetary roller units and planetary gear units and their functions, there is a need to use planetary gear type reducers for applications where planetary roller type reducers have been used, On the other hand, there is a need to use a planetary roller type speed reducer for an application that conventionally uses a planetary gear type speed reducer.

Japanese Patent Laid-Open No. 2001-108036 JP 58-119746 A

  However, even though the planetary roller unit and the planetary gear unit are similar in structure, the planetary roller unit is a structure in which the sun roller, planetary roller, and ring roller transmit torque by traction force, whereas the planetary gear unit is The sun gear, planetary gear, and ring gear mesh with each other to transmit torque. Therefore, when the design is considered with a constant life (time until damage), and the outer diameter of the ring roller and the outer diameter of the ring gear are set to be equal to each other, as shown in FIG. The permissible torque was larger in the planetary gear unit indicated by B in the drawing than in the planetary roller unit indicated by the line indicated by A. In other words, when the allowable torque is the same, the planetary roller type speed reducer is larger than the planetary gear type speed reducer.

  More specifically, since the planetary gear unit has a large relative curvature radius at the contact portion between the gears, the area of the contact portion increases accordingly. On the other hand, since the planetary roller unit has a small relative radius of curvature at the contact portion between the rollers, the area of the contact portion between the rollers is smaller than the area of the contact portion between the gears in the planetary gear unit.

  When the equivalent torque is input to the planetary gear unit and the planetary roller unit having the same size and reduction ratio, the contact portion between the rollers in the planetary roller unit is the same as that between the gears in the planetary gear unit. The same force is received in an area smaller than the contact portion, and the life is shortened accordingly. In other words, in order to make the life equivalent to the planetary gear unit, it is necessary to reduce the force acting on the contact portion between the rollers by increasing the diameter of the roller. It was larger than the planetary gear type reducer.

  Further, in the above conventional planetary roller type speed reducer, the planetary roller unit is supported by the bearing only by the carrier and output shaft provided on the output side thereof, so that when a radial load acts on the output shaft, it is output as a reaction force. A relatively large radial load acts on the bearing that supports the shaft and the carrier. Therefore, as shown in FIG. 7, the planetary roller unit indicated by the line labeled C in FIG. 7 has a smaller allowable radial load than the planetary gear unit labeled D in FIG. In other words, if the allowable radial load is the same, the planetary roller type reduction gear has to be larger than the planetary gear type reduction gear because the bearing supporting the output shaft and the carrier becomes large. there were.

  Therefore, when selecting either a planetary roller type speed reducer or a planetary gear type speed reducer, even if the required allowable torque or allowable radial load is the same, selecting a planetary roller type speed reducer, When the type reduction gear is selected, there is a difference in the installation space and the connection with the external member, and it is not possible to easily select both from the difference in function.

  The present invention has been made in view of the above problems, and the planetary roller type speed reducer that is more compact than the conventional allowable torque and allowable radial load, and the allowable torque and allowable radial load are equivalent. An object of the present invention is to provide a speed reducer series including a planetary roller type speed reducer and a planetary gear type speed reducer that have a common engagement with an external member.

  The present invention relates to a casing, a planetary roller unit in which a plurality of planetary rollers, a sun roller, and a ring roller integrally formed with the casing are assembled in a tight fit state, and one axial side of the planetary roller unit An output-side carrier disposed on the other side, an input-side carrier disposed on the other-side input side, and a plurality of connecting members that pass through the planetary roller unit and connect the input-side carrier and the output-side carrier. A carrier unit; an input-side carrier bearing disposed between the input-side carrier and the casing; and an output-side carrier bearing disposed between the output-side carrier and the casing, wherein the carrier unit is the ring. A planetary roller type speed reducer characterized in that it is rotatably supported by the casing integral with the roller in a both-side supported state. By is obtained by solving the above problems.

  In the present application, “the ring roller is assembled with a plurality of planetary rollers and the sun roller forming the input portion in a tightly fitted state” means that these members are assembled by a shrink-fit or cold-fit method. Therefore, it is used in the sense that it is pressurized in the radial direction without depending on the pressing force of other members such as bolts.

  In the conventional planetary roller type speed reducer, the casing integrated with the ring roller and the other casing such as the casing for accommodating the carrier bearing are separate bodies. Bolt holes for coupling with the casing are formed, so the size in the radial direction is large, and the rigidity of the casing is low by the amount of the bolt holes, and large radial pressure is applied to the ring roller, planetary roller, and sun roller. It was difficult to give. On the other hand, the planetary roller type speed reducer according to the present invention is formed integrally with a ring roller and a casing that accommodates an input side carrier bearing and an output side carrier bearing, and is coupled with other casings. Therefore, it is not necessary to form a bolt hole for the outer side in the radial direction of the ring roller, so that it is compact in the radial direction, and the casing and the ring roller have high rigidity, so that a large pressing force can be applied to the planetary roller unit. it can. Therefore, if the sizes are the same, a larger torque can be transmitted than the conventional planetary roller type speed reducer.

  Further, the carrier unit is supported on the casing in a both-sided manner by an input-side carrier bearing arranged on the input side of the planetary roller unit and an output-side carrier bearing arranged on the output side in the input-side carrier and the output-side carrier. Therefore, when a radial load is applied to the output shaft, the reaction force acting on the output-side carrier bearing is greater than the conventional planetary roller type speed reducer in which the carrier unit is supported by the bearing on one side of the planetary roller unit and the output shaft. Since it is small and there is no need to form a bolt hole in the casing, it can be used with a larger bearing than the conventional one as an output side carrier bearing, so if it is the same size, it will receive a larger radial load than the conventional planetary roller reducer Can do.

  That is, this planetary roller type speed reducer is more compact than a conventional planetary roller type speed reducer as long as the allowable torque and the allowable radial load are equal.

  According to the present invention, the planetary roller type speed reducer can be made compact. As a result, it is possible to realize a planetary roller type speed reducer in which the allowable torque and the allowable radial load are the same as those of the planetary gear type speed reducer, and the engagement with the external member is the same as that of the planetary gear type speed reducer.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a side sectional view showing the overall structure of a planetary roller type speed reducer according to the first embodiment of the present invention. FIG. 2 is a cross-sectional view taken along the line II-II in FIG.

  The planetary roller type speed reducer 10 is a planetary structure in which a plurality of planetary rollers 16 and a sun roller 18 forming an input part are assembled in a tightly fitted state to a casing 12 and a ring roller 14 formed integrally with the casing 12. A roller unit 20, an output carrier 22 disposed on one output side So in the axial direction of the planetary roller unit 20 to form an output unit, an input carrier 24 disposed on the other input side Si, and the planetary roller unit 20 A carrier unit 34 having a plurality of connecting members 26 for inserting and connecting the input side carrier 24 and the output side carrier 22, an input side carrier bearing 30 disposed between the input side carrier 24 and the casing 12, and an output side An output side carrier bearing 32 disposed between the carrier bearing 32 and the casing 12, and an output side carrier 2, the carrier unit 34 and an input side carrier 24 and the connecting member 26 is rotatably supported at both ends state the casing 12.

  The casing 12 is a cylindrical body, and a ring roller 14 is integrally formed on an inner peripheral portion near the center in the axial direction. The casing 12 has a flange 36 formed outside the ring roller 14 in the radial direction, and an attachment hole 38 for attaching the casing 12 to an external member is formed in the flange 36. The ring roller 14, the planetary roller 16, and the sun roller 18 are assembled in a tight fit state by a shrink fit method.

  The sun roller 18 is provided with an input shaft mounting portion 18A that protrudes toward the input side Si, and an axial spline that engages with the input shaft 40 is formed on the outer periphery of the input shaft mounting portion 18A. Further, the sun roller 18 is provided with a protrusion 18B protruding to the output side So, and the protrusion 18B is rotatably supported by the output side carrier 22 via a bearing 39. The movement of the sun roller 18 in the axial direction is restricted by the bearing 39 and the input shaft 40.

  The input shaft 40 has a hollow structure and an axial spline is formed on the inner periphery of one end, and is engaged with the input shaft mounting portion 18 </ b> A of the sun roller 18. An inner lid 41 is fitted and closed on the inner peripheral portion of the input shaft 40 on the side farther from the sun roller 18 than the spline, and the lubricating oil used in the planetary roller unit 20 is removed from the spline engaging portion. It is designed to block leakage.

  Further, the other end of the input shaft 40 is formed with a friction coupling portion 40A for friction coupling to a motor shaft (not shown). A slit 40B is formed in a direction perpendicular to the axial direction between the friction coupling portion 40A and other portions. The friction coupling portion 40A is formed with a slit (not shown) along the axial direction in a part of the circumferential direction, and a bolt that passes through one side of the slit and is screwed into the other side. The inner diameter of the friction coupling portion 40A is reduced by a fastening force (not shown), and is configured to be coupled to a motor shaft (not shown) or the like by a friction force.

  The input shaft 40 is accommodated in a cylindrical input shaft casing 42 and is rotatably supported by the casing 42 via a bearing 44. An oil seal 48 is installed between the input shaft 40 and the input shaft casing 42 and on the opposite side of the bearing 44 from the planetary roller unit 20. The input shaft casing 42 is coupled to the casing 12 by bolts 46. The input shaft casing 42 is formed with a working hole 42A for screwing / unscrewing the bolt of the friction coupling portion 40A.

  A pair of partition plates 50 in the form of ring plates are provided on both sides of the planetary roller 16 and the ring roller 14 in the axial direction. The planetary roller 16 has a width slightly smaller than that of the ring roller 14, so that the planetary roller 16 can smoothly rotate between the pair of partition plates 50.

  The connecting member 26 includes a bolt 26A, a collar 26B, a pin member 26C that is inserted into the planetary roller 16 and extracts a revolution component, and a sleeve 26D. The bolt 26 </ b> A penetrates the input side carrier 24, is inserted between the plurality of planetary rollers 16, and is screwed to the output side carrier 22. The collar 26B is fitted to the outer periphery of the bolt 26A and is positioned by being sandwiched between the input side carrier 24 and the output side carrier 22. In addition, the output side of the screw hole of the output side carrier 22 into which the connecting member 26 is screwed is closed. The pin member 26 </ b> C is fitted to the input side carrier 24 and the output side carrier 22 and passes through the planetary roller 16. The sleeve 26D is loosely fitted to the inner periphery of the planetary roller 16 and is fitted to the outer periphery of the pin member 26C. The sleeve 26D is disposed between the input side carrier 24 and the output side carrier 22, and the planetary roller 16 and the pin member 26C are connected to each other. It can be rotated smoothly. The planetary roller 16 is slightly smaller in width than the collar 26B and the sleeve 26D, so that the planetary roller 16 can smoothly rotate between the input side carrier 24 and the output side carrier 22.

  The output-side carrier 22 is a disc-like body and is connected with bolts 26A and pin members 26C. The output carrier 22 is integrally formed with an output shaft 23 that protrudes toward the output side. The outer periphery of the output side carrier 22 has a stepped shape with a slightly smaller outer diameter on the planetary roller unit 20 side, and the inner ring of the output side carrier bearing 32 is fitted to the small diameter portion. The large-diameter portion of the output-side carrier 22 is in contact with the end surface of the output-side carrier bearing 32 in the axial direction. An oil seal 52 is installed between the large diameter portion of the output side carrier 22 and the casing 12. A recess 22 </ b> C for holding the bearing 39 is formed in the vicinity of the center of the input side of the output side carrier 22.

  The input-side carrier 24 is a ring-shaped body, and the outer periphery has a stepped shape with the input-side end portion having an outer diameter larger than that of the other portion. Is in contact with the axial end face.

  The input side carrier bearing 30 and the output side carrier bearing 32 have an outer diameter larger than the inner diameter of the ring roller 14 and are installed in the vicinity of the ring roller 14. Here, “the input-side carrier bearing 30 is installed in the vicinity” means that the axial distance between the input-side carrier bearing 30 and the ring roller 14 is smaller than the width of the input-side carrier bearing 30. This means that the input-side carrier bearing 30 is installed. The same applies to the output side carrier bearing 32. The input-side carrier bearing 30 and the output-side carrier bearing 32 are angular ball bearings. The input-side carrier 24 and the output-side carrier 22 are sandwiched and pressurized from both sides in the axial direction by the input-side carrier 24 and the output-side carrier 22, and are preloaded and mounted. ing. Specifically, the input-side carrier bearing 30 has an input-side end face of the inner ring in contact with the input-side carrier 24 and an output-side end face of the outer ring in contact with the partition plate 50. On the other hand, the output side carrier bearing 32 has an output side end face of the inner ring in contact with the output side carrier 22 and an input side end face of the outer ring in contact with the partition plate 50. Preload is applied to the input-side carrier bearing 30 and the output-side carrier bearing 32 by the fastening force of the bolt 26A.

  Next, the operation of the planetary roller type speed reducer 10 will be described.

  In the planetary roller type speed reducer 10, the ring roller 14 is formed integrally with the casing 12, and the casing 12 is also formed integrally with a portion for accommodating the input side carrier bearing 30 and the output side carrier bearing 32. Since it is not necessary to form a bolt hole for coupling with the casing on the outer side in the radial direction of the ring roller 14, it is compact in the radial direction. Further, since the rigidity of the ring roller 14 integrated with the casing 12 is high, a large pressure can be applied to the planetary roller unit 20 as much. Therefore, if the sizes are the same, a larger torque can be transmitted than the conventional planetary roller type speed reducer. Moreover, since the flange 12 is formed in the casing 12 in the radial direction outer side of the ring roller 14, the rigidity of the ring roller 14 is also improved in this respect. In other words, when the allowable torque is equal, the planetary roller type speed reducer 10 is more compact than the conventional planetary roller type speed reducer.

  The carrier unit 34 is connected to the casing 12 by the input side carrier bearing 30 and the output side carrier bearing 32 in the input side carrier 24 arranged on the input side of the planetary roller unit 20 and the output side carrier 22 arranged on the output side. Since it is supported in the holding state, when a radial load is applied to the output shaft 23, the reaction force acting on the output-side carrier bearing 32 and the input-side carrier bearing 30 causes the carrier unit to output the carrier and output on one side of the planetary roller unit. It is suppressed to be smaller than the reaction force acting on the output shaft of the conventional planetary roller type speed reducer supported by the bearing on the shaft and the bearing supporting the carrier, and is larger than the conventional planetary roller type speed reducer if the size is the same. Can receive radial load.

  Further, when a radial load is applied to the output shaft 23, a reaction force can be applied to the planetary roller unit 20, but the rigidity of the ring roller 14 is high and the rigidity of the planetary roller unit 20 is also high. It is possible to receive a larger radial load than the planetary roller type speed reducer.

  Further, the input-side carrier bearing 30 and the output-side carrier bearing 32 are angular ball bearings, and are sandwiched between the input-side carrier 24 and the output-side carrier 22 so as to be pressurized in the axial direction, and a preload is applied to close the gap. Since it is mounted in a state, the runout of the output shaft 23 is suppressed even if a radial load that tends to cause a large deformation is applied to the carrier unit 34. Further, since the input side carrier bearing 30 and the output side carrier bearing 32 are angular bearings, a thrust load acting on the carrier unit 34 can also be received.

  Further, since the input side carrier bearing 30 and the output side carrier bearing 32 are installed in the vicinity of the ring roller 14, the input side carrier bearing 30 and the output side carrier bearing 32 are more compact in the axial direction than the conventional structure in which the carrier is supported by the bearing at the output shaft portion. . Since the input side carrier bearing 30 and the output side carrier bearing 32 have an outer diameter larger than the inner diameter of the ring roller 14, they can receive a large radial load even if the distance between them in the axial direction is small.

  That is, when the allowable torque and the allowable radial load are equal, the planetary roller type speed reducer 10 is more compact in both the radial direction and the axial direction than the conventional planetary roller type speed reducer.

  Here, how to assemble the planetary roller type speed reducer 10 will be briefly described.

  First, the casing 12 is heated, and the planetary roller 16 and the sun roller 18 are assembled to the ring roller 14 with the inner diameter of the ring roller 14 slightly enlarged. As the casing 12 is cooled, the inner diameter becomes smaller, and the ring roller 14, the planetary roller 16, and the sun roller 18 are pressurized in the radial direction.

  The input side carrier 24, the output side carrier 22, the input side carrier bearing 30, the output side carrier bearing 32, etc. are assembled to the planetary roller unit 20 assembled in this way, and the bolt 26A is inserted from the input side Si and tightened. As a result, the carrier unit 34 is assembled to the planetary roller unit 20.

  Further, the bearing 44, the oil seal 48, and the input shaft 40 are assembled to the input shaft casing 42. In this state, the spline of the input shaft 40 is fitted from the input side Si to the input shaft mounting portion 18A of the sun roller 18, The input shaft casing 42 and the casing 12 are fastened with bolts 46.

  Thereby, the assembly of the planetary roller type speed reducer 10 is completed. Thus, the planetary roller type speed reducer 10 is easy to assemble and has good productivity. Note that a bolt 26A for connecting the input side carrier 24 and the output side carrier 22 may be inserted into the output side carrier 22 from the output side and screwed into the input side carrier 24. The structure penetrates the carrier 22. In contrast, as in the first embodiment, the bolt 26A for connecting the input side carrier 24 and the output side carrier 22 is inserted from the input side Si and is screwed to the output side carrier 22, so that the output side The output side of the bolt hole of the carrier 22 can be closed. That is, without providing a seal or the like between the bolt 26 and the bolt hole, leakage of lubricating oil from this portion can be reliably prevented, the structure is simple, and the reliability is high.

  Next, a second embodiment of the present invention will be described.

  FIG. 3 is a side sectional view showing the overall structure of the planetary roller type speed reducer 60 according to the second embodiment.

  The planetary roller type speed reducer 60 has an input shaft 64 in a state where the input shaft mounting portion 62A protruding to the input side Si of the sun roller 62 is tightly fitted by press-fitting to the planetary roller type speed reducer 10 according to the first embodiment. Are configured to be frictionally coupled to each other. Further, the bolt 66 connecting the input side carrier 24 and the output side carrier 22 penetrates the output side carrier 22 and is screwed into the input side carrier 24. Other configurations are the same as those of the planetary roller type speed reducer 10, and thus the same reference numerals as those in FIG.

  In the input shaft 64, the inner peripheral portion near one end in the axial direction is a cylindrical surface, and the input shaft attaching portion 62A is press-fitted into this portion, and the sun roller 62 is coupled thereto. Since the sun roller 62 is restricted in its axial movement by the input shaft 64, no bearing is provided to restrict the axial movement of the sun roller 62. Accordingly, the sun roller 62 is not formed with a protrusion protruding toward the output side So.

  Similar to the planetary roller type speed reducer 10, the planetary roller type speed reducer 60 is more compact than a conventional planetary roller type speed reducer when the allowable torque and the allowable radial load are the same. Since the shaft mounting portion 62A is coupled to the input shaft 64 by press-fitting and there is no backlash in the rotational direction, no rotational fluctuation occurs. Furthermore, since the input shaft mounting portion 62A of the sun roller 62 is coupled to the input shaft 64 in a tightly fitted state, a seal or the like is not provided between the input shaft mounting portion 62A and the input shaft 64. Lubricating oil leakage can be reliably prevented, the structure is simple, and the reliability is high.

  Since the planetary roller type speed reducer 60 is assembled differently from the planetary roller type speed reducer 10, the method for assembling the planetary roller type speed reducer 60 will be briefly described.

  First, the input shaft 64 is assembled to the sun roller 62 in a tightly fitted state by a method such as shrink fitting or press fitting, and further, the sun roller 62, the input shaft 64, the bearing 44, and the oil seal 48 are assembled to the input shaft casing 42. Further, the input side carrier 24 and the input side carrier bearing 30 are assembled to the casing 12.

  Next, the planetary roller unit 20 is assembled with the ring roller 14 (casing 12) by assembling the planetary roller unit 20 and the planetary roller unit 20 with the bolt 46 by the shrink-fitting method as in the case of the planetary roller type speed reducer 10. The casing 12 and the input shaft casing 42 are coupled.

  Finally, the output side carrier 22 and the output side carrier bearing 32 are assembled, and the bolt 66 is inserted into the output side carrier 22 and screwed into the input side carrier 24. Thereby, the assembly of the planetary roller type speed reducer 60 is completed. Thus, the planetary roller type speed reducer 60 is also easy to assemble and has good productivity.

  Next, a third embodiment of the present invention will be described.

  FIG. 4 is a side sectional view showing the overall structure of the planetary roller type speed reducer 70 according to the third embodiment.

  In the planetary roller type speed reducer 70, the output shaft 23 is omitted from the planetary roller type speed reducer 10 according to the first embodiment, and a screw hole 72A for attachment to an external member is formed in the output side carrier 72. ing. Moreover, the hole in which the pin member 26C is fitted in the output side carrier 72 is opened only on the planetary roller unit 20 side, and the other is closed. The input side carrier bearing 74 and the output side carrier bearing 76 are non-angular type ball bearings. Further, a needle bearing 66D is fitted between the pin member 26C and the planetary roller 16 in order to increase transmission efficiency. Other configurations are the same as those of the planetary roller type speed reducer 10, and thus the same reference numerals as those in FIG.

  Thus, since the output shaft is omitted and the output side carrier 72 is configured to be coupled with the mating member, further downsizing in the axial direction is achieved. In this case, even if a radial load is applied to the output-side carrier 72, the output-side carrier 72 has a small moment because the output shaft portion is omitted.

  Next, a fourth embodiment of the present invention will be described.

  FIG. 5 is a side sectional view showing the overall structure of the reduction gear series 80 according to the fourth embodiment.

  The reducer series 80 includes the planetary roller type speed reducer 10 according to the first embodiment, and a planetary gear type speed reducer 90 having an allowable torque and an allowable radial load equivalent to the planetary roller type speed reducer 10. The roller type speed reducer 10 and the planetary gear type speed reducer 90 are characterized in that the attachment of the mounting portion to the external member is common. The common attachment of the mounting portion to the external member means that the elements coupled to the external member in the mounting portion are common, and specifically, in the present embodiment, both of the output shaft 23 and the flange mounting The positional relationship of the holes 38 is equal. In the present application, “permissible torque is equal” means that the difference in the maximum value of input torque (motor output capacity) is within 10%. In addition, “equivalent radial load is equal” means that the difference between the maximum allowable radial loads acting on the output side carrier is within 10%.

  In the reduction gear series 80, the outer dimension of the casing of the planetary roller type speed reducer 10 and the outer dimension of the casing of the planetary gear type speed reducer 90 are substantially equal. In this application, “the casing dimensions are substantially equal” means that the casing casing main dimensions such as the length of the casing in the axial direction and the outer diameter or width of the casing in the direction perpendicular to the axial direction. This means that the difference is within 10%.

  In the reduction gear series 80, the outer diameter Dr of the ring roller 16 of the planetary roller type reduction gear 10 is equal to the outer diameter Dg of the ring gear 91 of the planetary gear type reduction gear 90. In the present application, the “outer diameter of the ring roller” means a minimum width in a radially outer portion of the ring roller. For example, if the radially outer portion of the ring roller is a stepped cylinder, the outer diameter of the small diameter portion corresponds to the outer diameter of the ring roller, and the outer periphery of the radially outer portion of the ring roller is square. The width of two parallel surfaces corresponds to the outer diameter of the ring roller. In the case of a rectangle, the smaller one of the two parallel widths corresponds to the outer diameter of the ring roller, and there is no circular or square part on the outer side in the radial direction of the ring roller. In the case where it is configured only by a part having a different radius depending on the part, such as a flange shape, the outer diameter of the part having the substantially smallest radius on the outer periphery corresponds to the outer diameter of the ring roller. In the present application, “the outer diameter of the ring roller is equal to the outer diameter of the ring gear” means that the difference between the two is within 10%.

  The planetary gear type speed reducer 90 includes a planetary gear unit 92. The structure of the planetary gear type speed reducer 90 other than the planetary gear unit 92 is similar to that of the planetary roller type speed reducer 10, and thus the description thereof is omitted.

  The reducer series 80 includes a planetary roller type reducer 10 and a planetary gear type reducer 90, and a plurality of planetary roller type reducers and planetary gear type reducers (not shown) having different allowable torques and allowable radial loads. These sets of planetary roller type reduction gears and planetary gear type reduction gears also have the same shape and size of the mounting portion to the external member. Further, the outer dimensions of the casing are substantially equal, and the outer diameter of the ring roller and the outer diameter of the ring gear are also the same.

  In the case where the allowable torque and the allowable radial load are the same, the planetary roller type speed reducer 10 is conventionally known to have a larger planetary roller type speed reducer than the planetary gear type speed reducer. Thus, it is more compact than the conventional planetary roller type speed reducer, so that the output torque and the allowable radial load are the same as the planetary gear type speed reducer 90, and the shape and dimensions of the mounting portion to the external member are the same. Furthermore, the outer dimensions of the casing are almost equal.

  The reducer series 80 has a common installation space with the planetary roller type reducer 10 and the planetary gear type reducer 90, and can easily be selected based on the difference in function depending on the application. can do. Further, for example, the planetary gear type speed reducer 90 is used for an application where the planetary roller type speed reducer 10 is used, and conversely, the planetary roller type speed reducer 90 is used for an application where the planetary gear type speed reducer 90 is used. It is easy to use the machine 10, and the speed reducer series 80 is highly versatile.

  In the first to fourth embodiments, the ring roller 14, the planetary roller 16, and the sun roller 18 are assembled in a tight-fitting state by a shrink-fitting method. However, the ring roller 14, The planetary roller 16 and the sun roller 18 may be assembled with a tight fit.

  In the fourth embodiment, the planetary gear unit 92 of the planetary gear type reduction gear 90 is a simple planetary gear mechanism. For example, another planetary gear mechanism such as an inscribed rocking planetary gear mechanism is adopted. It is good also as a reduction gear series comprised with a planetary gear type reduction gear and a planetary roller reduction gear.

  The present invention can be used in various fields such as industrial machines, production facilities, and transportation equipment.

1 is a side sectional view showing the overall structure of a planetary roller type speed reducer according to a first embodiment of the present invention. Sectional view along the line II-II in FIG. Side sectional view which shows the whole structure of the planetary roller type reduction gear which concerns on 2nd Embodiment of this invention. Side sectional view which shows the whole structure of the planetary roller type reduction gear which concerns on 3rd Embodiment of this invention. Side sectional view which shows the structure of the reduction gear series which concerns on 4th Embodiment of this invention. A graph schematically showing the relationship between the outer diameter of the ring roller of the conventional planetary roller type reduction gear, the outer diameter of the ring gear of the planetary gear type reduction device, and the allowable torque. A graph schematically showing the relationship between the outer diameter of the ring roller of the conventional planetary roller type reduction gear, the outer diameter of the ring gear of the planetary gear type reduction device, and the allowable radial load.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10, 60, 70 ... Planetary roller type speed reducer 12 ... Casing 14 ... Ring roller 16 ... Planetary roller 18, 62 ... Sun roller 18A, 62A ... Input shaft attaching part 20 ... Planetary roller unit 22, 72 ... Output side carrier 23 ... Output shaft 24 ... input side carrier 26 ... connecting member 26A ... bolt 26B, 26D ... collar 26C ... pin member 28 ... pin member 30, 74 ... input side carrier bearing 32, 76 ... output side carrier bearing 34 ... carrier unit 36 ... flange 38 ... Mounting hole 40, 64 ... Input shaft 80 ... Reducer series 90 ... Planetary gear type reducer 91 ... Ring gear

Claims (11)

A casing,
A planetary roller unit formed by assembling a plurality of planetary rollers, sun rollers, and a ring roller integrally formed with the casing;
An output side carrier disposed on one side in the axial direction of the planetary roller unit, an input side carrier disposed on the other side, and a plurality of connections through which the planetary roller unit is inserted to connect the input side carrier and the output side carrier A carrier unit having members;
An input-side carrier bearing disposed between the input-side carrier and the casing;
An output-side carrier bearing disposed between the output-side carrier and the casing;
A planetary roller type speed reducer characterized in that the carrier unit is rotatably supported by the casing integral with the ring roller in a state of being supported by both ends. In claim 1,
The sun roller is configured such that an axial spline is formed and engaged with the input shaft in the spline;
The carrier unit has a configuration in which at least some of the plurality of connecting members are bolts, and the bolts pass through the input-side carrier and are screwed into the output-side carrier. Machine. In claim 1,
The sun roller is configured to be frictionally coupled to the input shaft in a tight fit state,
The carrier unit has a configuration in which at least a part of the plurality of connecting members is a bolt, and the bolt penetrates the output-side carrier and is screwed to the input-side carrier. Machine. In any one of Claims 1-3,
The planetary roller type speed reducer characterized in that the input side carrier bearing and the output side carrier bearing have an outer diameter larger than an inner diameter of the ring roller and are installed in the vicinity of the ring roller. In any one of Claims 1-4,
The input-side carrier bearing and the output-side carrier bearing are either angular ball bearings or tapered roller bearings, and are mounted so as to be sandwiched between the input-side carrier and the output-side carrier from both sides in the axial direction. Planetary roller speed reducer. In any one of Claims 1-5,
At least a part of the plurality of connecting members of the carrier unit is a pin member that passes through the planetary roller. In any one of Claims 1-6,
An installation hole for attaching the casing to an external member is formed in the casing. In claim 7,
A planetary roller type speed reducer characterized in that a flange is formed on a radially outer side of the ring roller in the casing, and the mounting hole is formed in the flange. A planetary roller type speed reducer according to any one of claims 1 to 8, and a planetary gear type speed reducer having an allowable torque equivalent to the planetary roller type speed reducer,
The planetary roller type speed reducer and the planetary gear type speed reducer share the same mounting portion with an external member. In claim 9,
The planetary roller type speed reducer and the planetary gear type speed reducer have substantially the same outer dimensions of the casing. In claim 9 or 10,
A reduction gear series, wherein an outer diameter of a ring roller of the planetary roller type reduction gear is equal to an outer diameter of a ring gear of the planetary gear reduction gear.

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