WO2017126321A1 - Réducteur et moteur à réducteur - Google Patents

Réducteur et moteur à réducteur Download PDF

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Publication number
WO2017126321A1
WO2017126321A1 PCT/JP2017/000075 JP2017000075W WO2017126321A1 WO 2017126321 A1 WO2017126321 A1 WO 2017126321A1 JP 2017000075 W JP2017000075 W JP 2017000075W WO 2017126321 A1 WO2017126321 A1 WO 2017126321A1
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WO
WIPO (PCT)
Prior art keywords
gear
wall
motor
damper
output shaft
Prior art date
Application number
PCT/JP2017/000075
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English (en)
Japanese (ja)
Inventor
田中　稔
Original Assignee
プラトー株式会社
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Filing date
Publication date
Application filed by プラトー株式会社 filed Critical プラトー株式会社
Publication of WO2017126321A1 publication Critical patent/WO2017126321A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/14—Construction providing resilience or vibration-damping
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears

Definitions

  • the present invention relates to a speed reducer that decelerates rotation of a motor and outputs it from an output shaft, and a motor with a speed reducer equipped with the speed reducer.
  • electric motors are often used as drive sources for vehicle wiper devices, power window devices, sunroof devices, and the like.
  • one unit is formed as a motor with a reduction gear in which the reduction gear is attached to the electric motor.
  • Patent Document 1 As such a motor with a reduction gear, the one shown in Patent Document 1 is known.
  • a gear case is fixed to the motor, and a rotation shaft of the motor projects inside the gear case.
  • a worm is connected to the rotation shaft, and an output gear ( A worm wheel) and a one-stage reduction structure in which an output shaft for external transmission is fitted to the output gear.
  • FIG. 16 shows a specific configuration of the output gear of the motor with a reduction gear shown in Patent Document 1.
  • the output gear 7 divides a portion between the insertion hole 7b formed at the center and the outer teeth into three parts at intervals of 120 ° in the circumferential direction, and is a fan-shaped partition space portion opened to the hub 9 side. 7a, 7a, 7a.
  • An external output shaft is rotatably inserted into the insertion hole 7b.
  • the damper 8 has a fan shape corresponding to the partition space portion 7a, and a cut portion 8a is formed at the center of the outer peripheral arc portion.
  • the hub 9 is made of a metal plate, and has three projecting pieces 9a cut and raised on the damper 8 side.
  • a shaft hole 9b is provided in the center of the shaft for connecting to the end of the external output shaft in a non-rotating state, and each projecting piece 9a is engaged with the cut portion 8a of the damper 8.
  • the cover 10 is formed of a circular thin plate member made of metal or resin.
  • the cover 10 has the groove part 10a for each protrusion piece 9a of the hub 9 to each fit.
  • At the center of the cover 10 there is an insertion hole 10b through which the external output shaft is rotatably inserted. In the assembled state, the cover 10 closes the opening 9c formed in the hub 9 by cutting and raising the protruding piece 9a.
  • the output gear 7 is rotated through the worm by driving the motor, and the cover 10 and the hub 9 are rotated through the damper 8 by the rotation of the output gear 7.
  • the external output shaft connected to is decelerated and driven. Further, when the external output shaft is restrained due to some obstacle from the driven body connected to the external output shaft, the hub 9 connected to the external output shaft stops simultaneously, while the output gear 7 continues to rotate. Thus, the impact force generated therewith is absorbed by compressing the damper 8 provided between the cover 10 engaged with the hub 9 and the output gear 7 in the rotation direction of the output gear 7. I have to.
  • the output gear 7 stops after rotating to some extent with respect to the hub 9 and the cover 10.
  • the driving force is transmitted from the output gear 7 to the external output shaft through the damper 8 and the hub 9.
  • a driving force is directly transmitted to the external output shaft from a hub 9 made of a metal plate. Therefore, a large torque is applied between the hub 9 and the external output shaft.
  • the hub 9 is a thin metal plate and a large torque is applied thereto, there is a limit to reducing the thickness, and it is necessary to use a thick metal plate as it is. It is an obstacle.
  • the three dampers 8 are made of rubber, there is a problem that it is difficult to reduce the weight.
  • the rubber damper 8 absorbs the impact force.
  • the output gear 7 rotates to some extent with respect to the hub 9 and the cover 10, but the rotation angle is small, and there is a problem that the output gear 7 does not function effectively against a large impact and a complicated impact.
  • the parts such as the output gear 7, the three dampers 8, the cover 10, and the hub 9 are necessary, and that the number of parts is large and the cost is high.
  • an object of the present invention is to provide a reduction gear and a motor with a reduction gear that can be reduced in weight and cost.
  • a speed reducer is a speed reducer that decelerates the rotation of a motor and outputs the reduced speed from an output shaft.
  • the speed reducer is disposed in a gear case and rotatably in the gear case, and is connected to the worm shaft of the motor.
  • an output gear that is rotatably disposed in the gear case and meshes with the worm directly or via an intermediate gear, and the output shaft is fitted to the fitting portion provided at the center at the engaging portion.
  • the output gear has a gear tooth formed on the outer wall, a recess is formed on one side surface, and a plurality of protrusions are formed on the inner wall of the recess at predetermined intervals in the circumferential direction.
  • a resin gear body a ring portion having a plurality of grooves recessed in the outer wall at a required interval in the circumferential direction, and provided at the center of the ring portion, and the engagement portion of the output shaft on the inner wall Cylinder with spline groove to fit It has a damper part provided with the above-mentioned fitting part and a bent part, and has a plurality of damper pieces which connect between the inner wall of the ring part and the outer wall of the fitting part, and the whole is integrally formed of synthetic resin. And a power transmission member housed in the recess of the gear body so that the protrusion of the gear body fits into the groove.
  • a motor with a speed reducer is a motor with a speed reducer comprising a motor and a speed reducer that decelerates the rotation of the motor and outputs it from an output shaft, the speed reducer comprising: a gear case;
  • the worm is rotatably disposed in the gear case, and is rotatably disposed in the gear case, and meshes with the worm directly or through an intermediate gear, and is provided at the center.
  • the cylindrical fitting portion can be formed as a fitting portion that is long in the axial direction and has one end projecting laterally from the ring portion and the damper portion.
  • the engaging portion of the output shaft that fits into the fitting portion of the power transmission body may be a synthetic resin engaging portion formed around a core metal body. It is preferable to mix carbon fiber into the engaging portion made of synthetic resin.
  • the output shaft has a metal external transmission gear on one end side, and the external transmission gear can be fixed to the core metal via a resin injected around the core metal. .
  • the damper piece extends laterally from both outer walls of the inward projecting part projecting inward of the ring part, and is bent in the opposite direction in the middle. Thereafter, the first damper pieces formed symmetrically to reach the outer wall of the fitting portion and the inner wall of the ring portion between the adjacent grooves extend halfway through the first
  • the second damper piece is formed in two symmetrical shapes that are bent in opposite directions at positions different from the curved part of the damper piece and then reach the outer wall of the fitting portion. it can.
  • the damper part in the power transmission body is composed of a plurality of damper pieces made of synthetic resin that connect the ring part and the fitting part. Therefore, when an impact force or a large load is applied, the damper piece bends greatly, Therefore, the rotation angle of the external output gear can be increased with respect to torque fluctuation and impact force of the output gear and the external output gear, and the rotation of the external output gear can be made smooth and quiet.
  • the output gear is composed of a synthetic resin gear body and a synthetic resin power transmission body, the weight can be greatly reduced.
  • the damper and hub are integrated as a synthetic resin power transmission body. As a result, it is possible to reduce the number of parts and reduce the cost.
  • FIG. 1 is a front view showing a state where a cover of a reduction gear portion of a motor 1 with a reduction gear is removed
  • FIG. Reference numeral 2 denotes a motor, which is fixed to the gear case 11 of the speed reducer 3 by screws (not shown).
  • the motor 2 is composed of a brush motor that can rotate forward and backward.
  • the gear structure of the speed reducer 3 is housed in the gear case 11.
  • the gear case 11 includes a case main body 11A and a lid body 11B (FIG. 2).
  • the lid 11B is fixed to the case main body 11A by fixing means such as screws (not shown).
  • a rotating shaft 21 of the motor 2 protrudes into the gear case 11, and a worm 12 is fixed coaxially with the rotating shaft 21 at a tip portion thereof.
  • the other end of the worm 12 is rotatably supported by a bearing (not shown).
  • the worm 12 is preferably made of resin.
  • the rotating shaft 21 and the worm 12 may be provided integrally.
  • Reference numeral 14 denotes an intermediate gear. As shown in FIG. 2, a worm wheel 14A, a pinion gear 14B fixed on one surface of the worm wheel 14A coaxially with the worm wheel 14A, and coaxial with the worm wheel 14A.
  • the worm wheel 14A includes a locking gear 14C fixed to the other surface of the worm wheel 14A.
  • the intermediate gear 14 is preferably formed integrally with resin.
  • the worm wheel 14A meshes with the worm 12. Thereby, the first-stage deceleration is performed.
  • the pinion gear 14B is set to have fewer teeth than the worm wheel 14A.
  • the number of teeth of the pinion gear 14B is preferably as few as possible to increase the reduction ratio, and is preferably 5-7.
  • the pinion gear 14 ⁇ / b> B meshes with an output gear 15 that is rotatably disposed in the gear case 11.
  • the output of the output gear 15 is performed through the output shaft 16.
  • the output gear 15 is made of resin.
  • FIG. 3 is an assembly diagram of the output gear 15 and the output shaft 16.
  • the output gear 15 includes a synthetic resin gear body 50 and a synthetic resin power transmission body 52.
  • the gear body 50 has a gear tooth 53 formed on the outer wall thereof, and a circular recess 54 formed on one side of the gear body 50.
  • a plurality (six in FIG. 3) of protrusions 55 are formed on the inner peripheral wall of the recess 54 at a required interval in the circumferential direction.
  • a cylindrical body 56a having a shaft hole 56 through which the output shaft 16 is rotatably inserted is provided in the center of the gear body 50.
  • the gear body 50 is formed of a hard synthetic resin.
  • FIG. 4 is a front view of the power transmission body 52, and FIG. 5 is an explanatory sectional view thereof.
  • the power transmission body 52 is integrally formed of a relatively soft synthetic resin such as polyacetal or elastomer.
  • the power transmission body 52 includes a ring portion 58, a fitting portion 59 located at the center of the ring portion 58, and a damper portion 61 having a large number of damper pieces 60 that connect the ring portion 58 and the fitting portion 59. ing.
  • a plurality (six in FIG. 4) of grooves 62 are provided on the outer wall of the ring portion 58 at a required interval in the circumferential direction.
  • the groove 60 is formed in a size that allows the projection 55 of the gear body 50 to be fitted.
  • the fitting portion 59 has a cylindrical shape, and a spline groove 65 into which the engaging portion 64 (FIG. 6) of the output shaft 16 is fitted is formed on the inner wall.
  • the fitting portion 59 has a cylindrical shape with a large diameter as much as possible, and a large number of spline grooves 65 are formed on the large-diameter inner wall. In the example of FIG. 4, there are 12 spline grooves 65.
  • the fitting portion 59 is formed in a cylindrical shape having a relatively long length, with one end projecting laterally from the ring portion 58 and the damper piece 60.
  • the fitting portion 59 is formed in a cylindrical shape that is long in the axial direction, and by providing a large number of spline grooves 65 on the inner wall, the fitting area with the output shaft 16 becomes large, and a resin fitting is made. Even in the joint portion 59, force can be transmitted to the output shaft 16 without difficulty.
  • the damper piece 60 in the damper portion 61 can transmit power from the gear body 50 to the output shaft 16 through the protrusion 55, the damper portion 61, and the fitting portion 59, and between the gear body 50 and the output shaft 16.
  • the shape and structure are not particularly limited as long as they can absorb the impact force generated in the case.
  • the damper piece 60 in the present embodiment includes two first damper pieces 60a and two second damper pieces 60b.
  • the first damper pieces 60a extend laterally from both outer walls of the inward projecting portions 66 projecting inwardly of the ring portion 58 to form the grooves 62 of the ring portion 58, and are opposed to each other in the middle. After being bent in the direction, it is composed of two damper pieces 60a and 60a that are formed symmetrically and reach the outer wall of the fitting portion 59.
  • the second damper piece 60b extends from the inner wall of the ring portion 58 between the adjacent grooves 62, and is different from the curved portion of the first damper piece 60a in the middle (a position that does not overlap spatially).
  • the second damper pieces 60b and 60b are formed in two symmetrical shapes that are bent in opposite directions to each other and reach the outer wall of the fitting portion 59. As described above, the first damper piece 60a and the second damper piece 60b are curved and provided in a range that does not overlap with each other in the ring portion 58, so that they can be efficiently arranged in the space of the ring portion 58. ing.
  • FIG. 6 is a cross-sectional view of the output shaft 16
  • FIG. 7 is a right side view thereof
  • FIG. 8 is a left side view thereof.
  • a core metal body 68 has a large diameter portion 68a, a first small diameter portion 68b, a second small diameter portion 68c, and a third small diameter portion 68d formed in this order.
  • the first small diameter portion 68b has the smallest diameter, and the diameter increases in the order of the second small diameter portion 68c and the third small diameter portion 68d.
  • Reference numeral 70 denotes a metal external output gear, which is formed in a hollow shape, and is injected around the first small diameter portion 68b of the core metal body 68 by injecting resin together with the plain washer 71 by insert molding. 72 is fixed.
  • the injection resin 72 is formed in a large diameter cylindrical shape over the second small diameter portion 68c and a part of the third small diameter portion 68d.
  • An end portion of the large-diameter injection resin 72 is formed in the engaging portion 64, and the engaging portion 64 has a protrusion 73 that fits into the spline groove 65 of the fitting portion 59 of the power transmission body 52. Is formed.
  • a cylindrical body 56a having a shaft hole 56 of the gear main body 50 is fitted into the portion of the large-diameter cylindrical injection resin 72 during assembly.
  • An e-ring circumferential groove 75 is formed in the middle of the third small diameter portion 68 d of the core metal body 68.
  • the first small-diameter portion 68b and the injection resin 72, and the injection resin 72 and the output gear 70 are engaged with each other to prevent the rotation.
  • the injection resin 72 a nylon resin having a high strength can be suitably used.
  • strength fibers such as carbon fibers to the injected resin 72 to further increase the strength.
  • FIG. 9 is a cross-sectional view showing an assembly structure of the output gear 15 and the output shaft 16.
  • the output gear 15 is assembled by housing the power transmission body 52 in the recess 54 of the gear body 50 so that the protrusion 55 fits into the groove 62 of the ring portion 58.
  • the output gear 15 is disposed in the case main body 11A so as to mesh with the pinion gear 14B of the worm wheel 14A. Next, the lid 11B is assembled.
  • the output shaft 16 has its third small diameter portion 68d inserted into the bearing portion 76 (FIG. 9) of the case main body 11A, and the protrusion 73 of the engaging portion 64 is fitted into the spline groove 65. In this manner, the output gear 15 is fitted.
  • the output shaft 16 is assembled such that the third small diameter portion 68d is supported by the bearing portion 76 and the large diameter portion of the injection resin 72 is supported by the bearing portion 77 (FIG. 9) of the lid 11B. It is done.
  • the lid body 14B is fixed to the case main body 11A with a screw or the like (not shown) to be assembled as a motor with a speed reducer.
  • the bearings 76 and 77 may be made of sintered metal impregnated with oil.
  • Reference numeral 78 denotes an e-ring.
  • the damper portion 61 in the power transmission body 52 is composed of a plurality of damper pieces 60 made of synthetic resin that connect the ring portion 58 and the fitting portion 59. Therefore, when an impact force or a large load is applied, the damper piece 60 bends greatly. Therefore, the rotation angle of the external output gear 70 can be increased with respect to the torque fluctuation and impact force of the output gear 15 and the external output gear 70, The rotation of the output gear 70 can be made smooth and quiet.
  • the damper portion 61 made of a soft synthetic resin such as polyacetal or elastomer, the amount of deflection can be increased and the impact force can be effectively absorbed.
  • the weight can be greatly reduced.
  • the overall weight can be reduced by about 20 g compared to the conventional one. Weight reduction is an extremely important matter for vehicle parts.
  • the output gear structure as shown in FIG. 16, three rubber dampers 8 and a metal hub 9 were required, but in this embodiment, the functions of the damper and the hub are combined.
  • the power transmission body 52 having an integral structure made of resin is provided, the number of parts can be reduced and the cost can be reduced.
  • the fitting portion 59 with the output shaft 16 has a large diameter and a long cylindrical shape in the axial direction, and the output shaft 16
  • the engagement portion 64 is made of resin, so that the fitting area between the two can be increased, it is possible to sufficiently withstand the large torque applied, and force can be transmitted to the output shaft 16 without difficulty. it can.
  • the metal external output gear 70 is fixed to the core metal body 68 by insert molding using the injection resin 72, but the entire output shaft 16 (external output gear 70 and core metal).
  • the body 68) may be made of synthetic resin. That is, conventionally, since the impact force applied to the output shaft 16 may momentarily reach several times the maximum torque of the motor 2, the entire output shaft is made of metal. However, in the present embodiment, as described above, since the impact force can be absorbed almost completely by the synthetic resin damper piece 60 of the damper portion 61, the torque of the output gear 16 and the external output gear 70 is the same as that of the motor 2. The maximum torque value can be set. Therefore, for the strength calculation, the entire output shaft 16 can be made of an integral structure with a nylon-based resin mixed with reinforcing fibers such as carbon fibers.
  • the advance angles of the worm 12 and the worm wheel 14A are set to be large, for example, 15 ° or more.
  • the overall transmission efficiency can be increased, for example, 60% or more, whereby the output torque can be increased. Therefore, when the same output torque is obtained, the motor can be made smaller than the conventional motor, the entire apparatus can be reduced in size, and the cost can be reduced.
  • the transmission efficiency is designed to be 40%.
  • 100/40 2.5. That is, the motor 2 requires a motor having a torque 2.5 times the required output torque.
  • 100/60 1.67.
  • the motor 2 may have a torque of 1.67 times the required output torque, and may be a conventional motor having a torque of about 70%.
  • 100/75 1.33 when the transmission efficiency is 75%.
  • the motor 2 may have a torque 1.33 times the required output torque, and may be a conventional small motor having a torque of about 50%.
  • FIGS. 10 is a plan view of the rotation restricting mechanism 17, FIG. 11 is a partially enlarged view thereof, FIG. 12 is a perspective view of the rotation restricting mechanism 17 (however, it is depicted upside down from that of FIG. 10), and FIG. It is a perspective view which shows the relationship between a 1st lever and a 2nd lever.
  • Reference numeral 24 denotes a first lever, which is provided at one end so as to be rotatable around a shaft 25.
  • the other end of the first lever 24 is provided with a lock claw 26 that is detachably engaged with the locking gear 14 ⁇ / b> C in the intermediate gear 14.
  • a first urging member (coil spring) 27 is linked to the first lever 24, and the first urging member 27 engages the first lever 24 and the locking claw 26 engages with the locking gear 14C. Energize in the direction to do.
  • a locking portion 28 having an approximately L shape is provided on the lower surface side of the first lever 24, a locking portion 28 having an approximately L shape is provided.
  • a pin 32 is provided on the distal end side of the plunger 31.
  • the pin 32 passes through a long hole 33 provided in the first lever 24.
  • the long hole 33 is provided so as to be long in the rotation direction of the first lever 24.
  • the pin 32 is positioned on one edge side of the long hole 33 when the first lever 24 is biased by the biasing member 27 and the lock claw 26 is in a position engaged with the locking gear 14C. is doing.
  • the first lever 24 is not rotated until the pin 32 contacts the edge of the other side of the long hole 33 when the electromagnetic solenoid 30 is driven and the plunger 31 is pulled.
  • the first lever 24 is rotated, whereby the lock gear 14C of the lock claw 26 is rotated. Is disengaged.
  • the second lever 36 is a second lever having an almost L shape.
  • the second lever 36 is provided so as to be rotatable about a shaft 37.
  • a hook 38 that can be locked to the locking portion 28 of the first lever 24 to prevent the rotation of the first lever 24 is provided at one end of the second lever 36.
  • a second urging member (coil spring) 39 is linked to the other end side of the second lever 36. The second urging member 39 urges the second lever 36 in the direction in which the hook 38 is engaged (contacted) with the engaging portion 28 (the counterclockwise rotation direction in FIGS. 10 and 11).
  • a pin 40 serving as a pressed portion is provided on the second lever 36.
  • the second lever 42 is a third lever, which is provided so as to be rotatable about a shaft 25 common to the first lever 24.
  • the pin 32 provided in the plunger 31 passes through the hole 43 provided in the third lever 42.
  • the hole 43 is formed in a slightly oval shape so that the third lever 42 can turn in an arc shape around the shaft 25.
  • the third lever 42 is provided with a pressing portion 44 that comes into contact with a pin 40 that is a pressed portion provided on the second lever 36.
  • the pressing portion 44 presses the pressed portion 40, and the second lever 36 is rotated in a direction in which the hook 38 is disengaged from the locking portion 28 of the first lever 24.
  • the surface of the pressing portion 44 that contacts the pressed portion 40 is formed as a cam surface 44 a that forms a required angle with respect to the pressed portion 40.
  • the rotation restricting mechanism 17 is preferably assembled on the base 46 and unitized.
  • the motor 1 with a speed reducer and the speed reducer 3 are configured as described above.
  • the operations of the motor 1 with the speed reducer and the speed reducer 3 itself are as described above.
  • the operation of the rotation restricting mechanism 17 will be described. 1 and 10 in which the motor 2 is stopped, the lock claw 26 is engaged with the locking gear 14C, and the hook 38 is engaged with the engaging portion 28, so that the first lever 24 is engaged. Is completely prevented from rotating. Therefore, for example, when the motor 1 with a speed reducer is used as a drive source for a power window of an automobile, the window can be completely locked even when an external force such as opening the window is applied at the time of stoppage. Can be reliably prevented.
  • the motor 1 with a speed reducer is used for a power seat of an automobile, even if an external force is applied to the seat due to a vehicle accident such as a collision, the seat can be prevented from moving and the driver's safety can be ensured. That is, in the motor 1 with a speed reducer according to the present embodiment, the rotation restricting mechanism 17 is provided, so that when the output of the motor is stopped, an operation that the applied devices cannot expect due to malfunction, malicious operation, etc. It is possible to reliably prevent this.
  • the electromagnetic solenoid 30 is also driven almost simultaneously.
  • the electromagnetic solenoid 30 is driven, when the plunger 31 is pulled, the third lever 42 is first rotated, and the pressing portion 44 presses the pin 40 that is the pressed portion, and the second lever 36 is moved. In FIG. 10, it is rotated in the clockwise direction, whereby the hook 38 is disengaged from the locking portion 28 (FIG. 14).
  • the first lever 24 is rotated with a time difference sufficient for the pin 32 to move in the long hole 33, the lock claw 26 is disengaged from the lock gear 14C (FIG.
  • torque from the locking gear 14C is received by being distributed (distributed) between the locking gear 14C and the locking claw 26 and between the locking portion 28 and the hook 38.
  • the static frictional force is also shared between the locking gear 14C and the locking claw 26, between the locking portion 28 and the hook 38, and the like.
  • the second lever 36 is rotated in advance of the first lever 24 as described above.
  • the electromagnetic solenoid 30 is energized, the hook 38 and the locking portion 28 are first disengaged.
  • the torque and static friction force acting between the two are shared and relatively small. Therefore, the engagement between the two is easily released.
  • the first lever 24 is rotated with a time difference, and the locking between the locking gear 14C and the locking claw 26 is released, but the torque and static friction force acting between the two are also shared and compared. Therefore, the engagement between the two is easily disengaged.
  • the output gear structure according to the present invention can be adopted for a reduction gear structure having a function without the rotation restricting mechanism.
  • the two-stage reduction gear structure has been described.
  • the output gear structure according to the present invention can also be adopted for the output gear (worm wheel) in the one-stage reduction gear structure.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Gear Transmission (AREA)

Abstract

Le problème décrit par la présente invention est de proposer un moteur à réducteur capable d'engendrer une réduction du poids et une réduction des coûts. La solution selon l'invention porte sur un moteur à réducteur (1) équipé d'un réducteur (3) qui réduit la vitesse de la rotation d'un moteur (2) et produit la rotation d'un arbre de sortie (16), un engrenage de sortie (15) comprenant : un corps d'engrenage (50) fabriqué dans une résine synthétique, de telle sorte que les dents d'engrenage (53) sont formées sur la paroi externe, une partie évidée (46) est formée sur une face latérale, et une pluralité de saillies (55) sont formées sur la paroi interne de la partie évidée (54) ; et un corps de transmission de puissance (52) qui présente une partie annulaire (58), dans la paroi externe de laquelle une pluralité de rainures (62) sont évidées, une partie d'ajustement (59), qui est disposée au centre de la partie annulaire (58) et dans la paroi interne de laquelle une partie de mise en prise (64) de l'arbre de sortie (16) s'insère, et une partie amortisseur (61), qui présente plusieurs pièces d'amortisseur (60) raccordant la paroi interne de la partie annulaire (58) à la paroi externe de la partie d'ajustement (59), ledit corps de transmission de puissance (52) étant formée d'un seul tenant à partir d'une résine synthétique, et étant logé dans la partie évidée (54) du corps d'engrenage (50) de telle sorte que les saillies (55) sont insérées dans les rainures (62).
PCT/JP2017/000075 2016-01-18 2017-01-05 Réducteur et moteur à réducteur WO2017126321A1 (fr)

Applications Claiming Priority (2)

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JP2016007389 2016-01-18
JP2016-007389 2016-01-18

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WO2017126321A1 true WO2017126321A1 (fr) 2017-07-27

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110857729A (zh) * 2018-08-22 2020-03-03 通用汽车环球科技运作有限责任公司 聚合物齿轮

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JPS6319470B2 (fr) * 1982-10-06 1988-04-22 Ngk Spark Plug Co
JPH0369927U (fr) * 1989-11-02 1991-07-12
JPH05428A (ja) * 1991-03-20 1993-01-08 Mitsui Toatsu Chem Inc 伝動部材及びそのインサート成形方法
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JP2005308012A (ja) * 2004-04-19 2005-11-04 Seiko Epson Corp 歯車、その製造方法、その歯車を備えた精密機器
JP2013545050A (ja) * 2010-11-25 2013-12-19 ヴァレオ システム テルミク 特に自動車アクチュエータ用のギア対
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US3406583A (en) * 1967-01-30 1968-10-22 Gen Motors Corp Drive mechanism having overload release means
JPS6319470B2 (fr) * 1982-10-06 1988-04-22 Ngk Spark Plug Co
JPH0369927U (fr) * 1989-11-02 1991-07-12
JPH05428A (ja) * 1991-03-20 1993-01-08 Mitsui Toatsu Chem Inc 伝動部材及びそのインサート成形方法
JP2002139122A (ja) * 2000-07-31 2002-05-17 Asmo Co Ltd ギヤードモータ
JP2005308012A (ja) * 2004-04-19 2005-11-04 Seiko Epson Corp 歯車、その製造方法、その歯車を備えた精密機器
JP2013545050A (ja) * 2010-11-25 2013-12-19 ヴァレオ システム テルミク 特に自動車アクチュエータ用のギア対
US20150047448A1 (en) * 2013-08-16 2015-02-19 Johnson Electric S.A. Gear

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