JP5220160B2 - Reducer with motor - Google Patents

Description

    The present invention relates to a reduction gear with a motor configured by assembling a rotation shaft of a drive motor to an input shaft while maintaining a coaxial relationship.

    As a conventional reduction gear with a motor, for example, the one described in Patent Document 1 below is known.

JP-A-5-44792

  This is constructed by assembling the rotation axis of the drive motor arranged in parallel with the speed reducer while maintaining a coaxial relationship with the input shaft, and both ends of the input shaft in the axial direction are fixed portions of the speed reducer. The casing is rotatably supported via a bearing and a carrier, while the rotating shaft of the drive motor is also rotatably supported at both axial ends by a fixed portion of the drive motor via a bearing. And the input shaft of these reduction gears and the rotating shaft of a drive motor are couple | bonded by the coupling in the edge part which mutually adjoins.

    However, such a conventional speed reducer with a motor has a problem that the axial length becomes long.

  An object of this invention is to provide the reduction gear with a motor which can shorten axial length.

The purpose is that an internal gear supporting a large number of internal teeth pins constituting internal teeth on the inner periphery, and a smaller number of external teeth are formed on the outer periphery while meshing with the internal teeth pins. a rotatably supported input shaft speed reducer having a pinion, met motorized reduction gear is constructed by assembling while keeping coaxial relationship with the rotation shaft of the drive motor which is arranged axially speed reducer And both ends of the input shaft in the axial direction are rotatably supported by a pair of bearings on a fixed portion of the speed reducer, and an eccentric portion for eccentrically rotating the pinion of the speed reducer on the input shaft between the pair of bearings. Further, the rotation shaft of the drive motor is substantially disc-shaped, and the radially inner end of the rotation shaft is positioned at the end of the input shaft that is close to the drive motor on the axially outer side than the pair of bearings. Combine and rotate the rotating shaft While performed by the pair of bearings also lifting, said drive motor comprises a plurality of permanent magnets exhibiting annular as a whole is secured to the radially outer end of the rotary shaft, of the reduction gear in the radial direction outer side of the permanent magnet have a coil fixed to the fixed portion, the inner diameter of the permanent magnet can be achieved by having a smaller than the pitch circle diameter of the internal gear.

  In the present invention, the axial length can be shortened.

1 is a front sectional view showing a first embodiment of the present invention. It is front sectional drawing which shows 2nd Embodiment of this invention. FIG. 3 is a view taken along arrows I-I in FIG. 2.

Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.
In FIG. 1, reference numeral 11 denotes a reduction gear with a motor used for winding an elevator. The reduction gear with a motor 11 has a fixing member 12 fixed to a fixed frame (not shown), and the fixing member 12 has a large diameter. A disk-shaped large-diameter portion 13, a small-diameter disk-shaped small-diameter portion 14 continuous with one side surface of the large-diameter portion 13, and a plurality of column portions projecting from one side surface of the small-diameter portion 14 toward one side And 15. Here, the other end surface of the large-diameter portion 13 is a flat surface except for the radially outer end portion.

Reference numeral 16 denotes a bottomed cylindrical case as a fixed portion, and the open end (one end) of the case 16 is fixed to the other side surface of the large-diameter portion 13, so that between the case 16 and the large-diameter portion 13 A disk-shaped sealed space 17 is formed in the upper part. 18 is a cylindrical coil fixed to the outer end of the case 16 in the radial direction. The inner side of the coil 18 in the radial direction has a substantially disk shape coaxial with the input shaft 21 of the eccentric oscillating speed reducer 20. rotary shaft 19 is provided, a plurality of permanent magnets 22 which exhibits a circular is fixed as a whole Rukoto disposed along the coil 18 in the radially outer end of the rotary shaft 19. As a result, the coil 18 is disposed radially outside the permanent magnet 22. The case 16, the coil 18, the rotary shaft 19, and the permanent magnet 22 described above constitute a drive motor 23, in this case, an electric motor, which is arranged in parallel with the speed reducer 20 in the axial direction . Here, at the radially inner end of the rotary shaft 19, the other end of the input shaft 21, that is, the end close to the drive motor 23, is integrally rotated outside the pair of bearings 50 described later in the axial direction. As a result, when the coil 18 is energized, the permanent magnet 22 rotates around the axis, but this rotation is transmitted to the input shaft 21 through the rotating shaft 19 and rotates the input shaft 21. To do.

  26 is a substantially cylindrical intermediate member splined to the other end of the input shaft 21, between the intermediate member 26 and the drive motor 23, that is, on the radially inner side of the drive motor 23, the intermediate member 26, A braking means 27 for applying a braking force to the rotating portion of the drive motor 23, that is, the rotating shaft 19 and the permanent magnet 22, is accommodated via the input shaft 21. If the drive motor 23 has a cylindrical shape and the braking means 27 is housed inside the drive motor 23 in the radial direction, the drive motor 23 and the braking means 27 overlap with each other in the radial direction. The speed reducer 11 is thin by reducing its axial length by the axial length of the braking means 27.

  The braking means 27 comprises a single braking device and has a fixing member 28 fixed to the case 16, and this fixing member 28 has a pair of fixing walls 29a and 29b separated in the axial direction. Reference numerals 30a and 30b denote a pair of brake plates arranged in a pair between the fixed walls 29a and 29b. Here, the brake plates 30a and 30b have radially inner ends that are the outer periphery of the intermediate member 26. Are splined together. As a result, the brake plates 30a and 30b can move in the axial direction between the fixed walls 29a and 29b, and rotate integrally with the permanent magnet 22 and the rotary shaft 19 of the drive motor 23 via the intermediate member 26 and the input shaft 21. It will be connected as possible.

  31a and b are a pair of axially movable armatures arranged between the brake plates 30a and b, and these armatures 31a and b are formed in a plurality of semicircular recesses formed at the radially outer ends thereof. The pins 32a and 32b fixed to the fixed walls 29a and b are inserted, so that the radial movement is restricted. Reference numeral 33 denotes a receiving member disposed between the armatures 31a and 31b and fixed to the fixing member 28. The receiving member 33 has a braking plate 30a attached to the corresponding fixing wall 29a via the armature 31a, and A plurality of springs 34a, b that press the braking plate 30b against the corresponding fixed wall 29b via the armature 31b are housed.

  When the brake plates 30a, b are pressed against the fixed walls 29a, b via the armatures 31a, b by the urging force of the springs 34a, b arranged between the brake plates 30a, b, the brake plates 30a, The rotation of b is regulated by the frictional resistance between the fixed walls 29a and 29b, and a braking force is applied to the rotating shaft 19 and the permanent magnet 22 of the drive motor 23. If the braking force is applied by pressing the two braking operation parts having the braking plates 30a and b operating in this way against the pair of fixed walls 29a and 29b, respectively, the driving motor 23 is simultaneously applied to two places. Since braking is performed, the braking force is doubled, and even when one of them fails, braking can be performed on the other, improving safety. Thus, the braking means 27 (one braking device) has two braking operation parts inside, in other words, since two mechanical operation parts operate for one electric signal, safety is improved. In addition to the improvement, the reduction gear 11 with the motor can be reduced in size.

  35 is an annular electromagnet disposed between the brake plates 30a and b by being housed in the receiving member 33. When the electromagnet 35 is energized, the armatures 31a and b are attracted and moved closer to each other. Let When the armatures 31a and 31b are moved close to each other in this way, the springs 34a and b are contracted by being pushed by the armatures 31a and 31b. The motor 23 is released from braking. The fixing member 28, the brake plates 30a and 30b, the armatures 31a and 31b, the receiving member 33, the springs 34a and 34b, and the electromagnet 35 as a whole constitute the disc-shaped brake means 27 having a cylindrical shape.

  And, on the other side of the speed reducer 20, the drive motor 23 and the braking means 27 are assembled while maintaining a coaxial relationship. The speed reducer 20 is fixed to one side surface of the column portion 15. A ring-shaped end plate 37 is provided. The fixing member 12 and the end plate 37 described above constitute a carrier 38 as a fixing portion of the speed reducer 20 as a whole. Since the carrier 38 is cantilevered only by the fixing member 12 being fixed to the fixing frame, not the both ends, the reduction gear 11 with the motor can be miniaturized. 39 is a cylindrical rotatable internal gear that surrounds the small-diameter portion 14, the column portion 15, and the end plate 37 from the outside in the radial direction, and this internal gear 39 includes the inner periphery of both axial ends thereof, the small-diameter portion 14, and the end plate 37. The carrier 38 is rotatably supported by a pair of bearings 40 interposed between the outer periphery and the outer periphery.

  Further, a plurality of sheave grooves 41 extending continuously in the circumferential direction are formed on the outer periphery of the internal gear 39, and an elevator car is connected to one end and a counterweight is connected to the other end of these sheave grooves 41. The main rope not shown is hung around. As a result, the internal gear 39 is integrated with the sheave. This eliminates the need for attaching the sheave to the internal gear 39 and simplifies the structure of the reduction gear 11 with the motor.

The inner periphery of the internal gear 39 is supported in a state where a large number of internal teeth pins 42 constituting the internal teeth are inserted almost in the center in the axial direction, and these internal teeth pins 42 extend in the axial direction. They are equidistant in the circumferential direction. Reference numeral 43 denotes a roller follower having the same number of cylinders as the inner tooth pins 42. The roller followers 43 are rotatably fitted to the outer side of the central portion of the inner tooth pin 42 in the axial direction. The inner diameter of the permanent magnet 22 is smaller than the pitch circle diameter of the internal gear 39.

  Reference numeral 46 denotes a plurality of, in this case, three ring-shaped pinions arranged between the small diameter portion 14 and the end plate 37 in the internal gear 39. The number of the internal tooth pins 42 is arranged on the outer periphery of each pinion 46. A slightly smaller number of external teeth 47 are formed. The external teeth 47 of these pinions 46 mesh with the internal gear pins 42 of the internal gear 39 via the roller follower 43. The meshed state is shifted by 180 degrees between the adjacent pinions 46. Since the outer teeth 47 of the pinion 46 are engaged with the roller follower 43 of the rotatable inner tooth pin 42 in this way, the engagement between the inner tooth pin 42 and the outer teeth 47 is a rolling contact, and the frictional resistance is greatly increased. As a result, the transmission efficiency is improved and the rotational sound is reduced.

  50 is a pair of bearings interposed between the carrier 38 and the input shaft 21 loosely fitted in the central portion of the carrier 38, both ends of the axial direction of the input shaft 21 by the bearing 50, respectively Are supported by the carrier 38, that is, the fixed portion of the speed reducer 20, so as to be rotatable with both ends. Further, the input shaft 21 has three eccentric portions 51 that are eccentric by an equal distance from the rotational axis at the axial center between the bearings 50. Among the eccentric portions 51, the adjacent eccentric portions 51 are 180 degrees apart. Only out of phase. These eccentric portions 51 are inserted into the pinion 46 with the roller bearings 52 interposed therebetween.

  As a result, when the input shaft 21 is driven and rotated by the drive motor 23, the eccentric portion 51 rotates eccentrically, causing the adjacent pinion 46 to rotate eccentrically (revolve) with the phase shifted by 180 degrees. At this time, since the number of the internal teeth pins 42 and the number of the external teeth 47 are slightly different, the rotation of the input shaft 21 is greatly decelerated by the eccentric rotation of the pinion 46 and transmitted to the internal gear 39. The gear 39 is rotated at a low speed and the main rope is driven.

  Reference numeral 55 denotes a crankshaft which is disposed between the pillar portions 15 in the circumferential direction and is the same number of crankshafts as the pillar portions 15. Both ends of the crankshaft 55 in the axial direction are connected to the small diameter portion 14 and the end plate 37 via bearings 56. It is rotatably supported. Further, the same number (three) of eccentric portions 57 as the eccentric portions 51 of the input shaft 21 are formed in the central portion of the crankshaft 55 in the axial direction, and these eccentric portions 57 respectively have roller bearings 58 interposed therebetween. The pinion 46 is inserted in a state. Thus, the pinion 46 is supported by the carrier 38 so as to be eccentrically rotatable.

  59 is a cover attached to one end of the end plate 37, and this cover 59 closes one end opening of the through hole of the carrier 38 into which the input shaft 21 is loosely fitted. One side surface of the cover 59 is located on the same plane as one side surface of the end plate 37. As a result, the one side end surface of the speed reducer 20 is also a flat surface like the other side end surface. Thus, if both side end surfaces of the speed reducer 20 are flat surfaces, the drive motor 23 and the braking means 27 can be mounted on any side end surface of the speed reducer 20. As a result, the degree of freedom of mounting is reduced. Increased layout will be rich.

  The input shaft 21, the carrier 38, the internal gear 39, the pinion 46, the crankshaft 55, and the cover 59 as a whole constitute the speed reducer 20 that decelerates the rotation of the drive motor 23 and outputs it to the sheave (internal gear 39). To do. If the speed reducer 20 is a center crank type as described above, the speed reducer 20 and the drive motor 23 can be easily arranged on the same axis. Further, as described above, both ends in the axial direction of the input shaft 21 of the speed reducer 20 are rotatably supported by the pair of bearings 50 on the carrier 38 (fixed portion) of the speed reducer 20, respectively. Since the rotary shaft 19 of the drive motor 23 is coupled to the other end close to the drive motor 23, the rotary shaft 19 can also be supported by the pair of bearings. Can be released from the rotating support by 23.

  61 is a seal member interposed between the outer periphery of the other end of the input shaft 21 and the inner periphery of the other end of the carrier 38, 62 and 63 are the outer periphery of the other end of the internal gear 39 and the inner periphery of the other end of the carrier 38 ( Sealing members interposed between the inner circumference of the large-diameter portion 13 and between the inner circumference of one end of the internal gear 39 and the outer circumference of the other end of the carrier 38 (the outer circumference of the end plate 37). All the openings of the speed reducer 20 are closed by the members 61, 62, and 63, and the inside of the speed reducer 20 is sealed. When the inside of the speed reducer 20 is sealed by the seal members 61, 62, 63 in this way, it is necessary to arrange another seal member between the speed reducer 20, the drive motor 23, and the braking means 27 when assembled. As a result, the above-described assembly work is facilitated.

  66 is an encoder as a detector that is arranged radially inside the braking means 27 and is fixed to the case 16, and a rotating portion of the encoder 66 is connected to the intermediate member 26, and the rotation of the intermediate member 26 The number of rotations of the sheave (internal gear 39) is detected by detecting the number. Thus, when the encoder 66 is arranged radially inward of the braking means 27, even when a detector such as the encoder 66 is added to the reduction gear 11 with the motor, the axial length of the reduction gear 11 with the motor increases. Can be prevented.

Next, the operation of the first embodiment of the present invention will be described.
When the elevator car is moved up and down, the coil 18 of the drive motor 23 is energized to rotate the permanent magnet 22 together with the rotary shaft 19. At the same time, the electromagnet 35 of the braking means 27 is energized to attract the armatures 31a, b, release the braking plates 30a, b from the pressing force of the springs 34a, b, and release the drive motor 23 from braking. As a result, the rotation of the rotating shaft 19 is transmitted to the input shaft 21 without being braked from the braking means 27, and the input shaft 21 is rotated.

  When the input shaft 21 rotates in this way, the pinion 46 rotates eccentrically (revolves). At this time, the number of the internal teeth pins 42 and the number of the external teeth 47 are slightly different, so the rotation of the input shaft 21 Is greatly decelerated by the eccentric rotation of the pinion 46 and transmitted to the internal gear 39, causing the internal gear 39 (sheave) to rotate at a low speed. As a result, the main rope hung around the sheave groove 41 travels and the car moves up and down. At this time, the rotation speed of the internal gear 39 is detected by the encoder 66, and the height position of the car is controlled.

  Next, when stopping the raising and lowering of the car, the energization to the coil 18 is interrupted to stop the drive motor 23, the energization to the electromagnet 35 is also interrupted, and the armatures 31a and 31b are attracted by the electromagnet 35. Stop. As a result, the brake plates 30a, b and the armatures 31a, b are moved toward the fixed walls 29a, b by the urging force of the springs 34a, b, and are pressed against the fixed walls 29a, b, respectively. As a result, the rotation of the brake plates 30a, b is restricted by the frictional resistance between the fixed walls 29a, 29b, the braking force is applied to the drive motor 23, and the raising / lowering of the car is stopped.

    2 and 3 are views showing a second embodiment of the present invention. In the figure, 71 is a braking means housed inside the drive motor 23 in the radial direction, and this braking means 71 applies a braking force to the rotating shaft 19 and the permanent magnet 22 which are rotating parts of the drive motor 23. . The braking means 71 has a ring-shaped fixing member 72 fixed to the case 16, and a plurality of guide screws 73a and 73b are screwed and fixed to the outer periphery of the fixing member 72.

  74a and b are a pair of arcuate shoes that are disposed 180 degrees apart in the circumferential direction, and here are a pair of arcuate shoes. These shoes 74a and 74b are arranged on the outer side in the radial direction of the fixing member 72, and the guide screws 73a and 73b are slidably inserted. As a result, the shoes 74a, b are supported by the fixing member 72 via the guide screws 73a, 73 so as to be movable in the radial direction.

  75a and b are a pair of arcuate plates that can contact the inner periphery of the fixing member 72. These arcuate plates 75a and 75b and the shoes 74a and b are a pair of connecting rods 76a that penetrate the fixing member 72 in the radial direction. , B are connected to each other. 77a and b are pairs of springs housed in the fixing member 72 so as to surround the connecting rods 76a and b, and these springs 77a and 77b apply a biasing force toward the radially outer side to the shoes 74a and b. Thus, the shoes 74a and 74b are pressed against the inner periphery of the rotary shaft 19 and the permanent magnet 22 which are the rotating parts of the drive motor 23, thereby applying a braking force to the rotary shaft 19 and the permanent magnet 22.

  If the braking force is applied by pressing the two braking operation parts having the shoes 74a and 74b against the inner periphery of the rotary shaft 19 in this way, braking is simultaneously applied to the drive motor 23 at two locations. As a result, the braking force is doubled, and even if one of them fails, the remaining brake can be performed. Thus, since the braking means 71, that is, one braking device has two braking operation parts inside, the safety is improved and the reduction gear 11 with the motor can be miniaturized.

  78a and b are a pair of electromagnets housed in a fixing member 72 between the springs 77a and 77b. When these electromagnets 78a and 78b are energized, the shoes 74a and b are attracted to the springs 77a and b. Move radially inward against As a result, the shoes 74a, b are separated from the rotating shaft 19, and the rotating portion of the drive motor 23 is released from braking. The fixing member 72, the guide screws 73a and b, the shoes 74a and b, the arc plates 75a and b, the connecting rods 76a and b, the springs 77a and b, and the electromagnets 78a and b, as a whole, form the drum-type braking means 71. Configure. In this way, the rotating shaft 19 (usually a separate braking drum) to which a braking force is applied from the shoes 74a, 74b can be shared with the rotating portion of the drive motor 23. The attached speed reducer 11 can be reduced in size with a simple structure.

  81a and b are a pair of release levers extending substantially in the radial direction, with the radially inner ends rotatably supported by the fixing member 72 via pins 82a and b, and the release levers 81a and 81b are arranged in the radial direction. The inner ends engage with the outer peripheries of the arcuate plates 75a and 75b, while a wire (not shown) is connected to the outer ends in the radial direction.

  Then, in the case of manually releasing the braking to the drive motor 23 in the event of failure where the energization to the electromagnets 78a and b cannot be controlled, by pulling the wire and swinging the release levers 81a and 81b upright, The arc-shaped plates 75a, 75b, the connecting rods 76a, 76b, and the shoes 74a, b are integrally moved radially inward against the springs 77a, 77b. Reference numeral 83 denotes a cooling fin fixed to the outer periphery of the case 16. Other configurations and operations are the same as those in the first embodiment.

    In the above-described embodiment, the cylindrical roller follower 43 is fitted to the outside of the internal tooth pin 42. However, in this invention, a cylindrical bearing is fitted to the outside of the internal tooth pin. You may do it. In the above-described embodiment, the crankshaft 55 having the eccentric portion 57 is inserted into the pinion 46. However, in the present invention, a cylindrical pin may be inserted. Furthermore, in the above-described embodiment, the eccentric oscillating speed reducer 20 is used as the speed reducer, but this kind of speed reducer may be of any kind.

  The present invention can be applied to the industrial field of a reduction gear with a motor configured by assembling a rotary shaft of a drive motor to an input shaft while maintaining a coaxial relationship.

11 ... Reducer with motor 19 ... Rotating shaft
20 ... Reducer 21 ... Input shaft
23 ... Drive motor 38 ... Fixed part

Claims (3)

A reduction gear having an internal gear on which a large number of internal teeth pins constituting internal teeth are supported on the inner periphery, and a pinion that meshes with the internal teeth pins and has a smaller number of external teeth on the outer periphery than the internal teeth pins. A reduction gear with a motor configured by assembling a rotation shaft of a drive motor arranged in parallel with the reduction gear in an axial direction to an input shaft rotatably supported by the reduction gear , Both ends in the axial direction are rotatably supported by a pair of bearings on a fixed part of the speed reducer, and an eccentric part for eccentrically rotating the pinion of the speed reducer is provided on the input shaft between the pair of bearings, and the drive The rotating shaft of the motor is substantially disc-shaped, and the radially inner end of the rotating shaft is coupled to the end of the input shaft adjacent to the drive motor on the axially outer side than the pair of bearings. The pair of rotation supports While performing the receiving, the drive motor comprises a plurality of permanent magnets exhibiting annular as a whole is secured to the radially outer end of the rotary shaft is fixed to the fixing portion of the reduction gear in the radial direction outer side of the permanent magnet and have a coil, a motor with reduction gear, characterized in that the inner diameter of the permanent magnet and smaller than the pitch circle diameter of the internal gear.     The reduction gear with a motor according to claim 1, wherein braking means for applying a braking force to the rotation shaft of the drive motor is housed inside the drive motor in the radial direction.     The reduction gear with a motor according to claim 2, wherein a detector for detecting the rotational speed of the input shaft is arranged on the radially inner side of the braking means.

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