JP2008032142A - Driving device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a driving device capable of being miniaturized. <P>SOLUTION: This driving device 1a is provided with a rotation power source 11, a front stage side driving gear 141 and a rear stage side driving gear 143 receiving transmission of rotation power of the rotation power source 11, a front stage side driven gear 151 for outputting rotation power to the outside in the interlocking relationship with the front stage side driving gear 141, a rear stage side driven gear 152 for outputting rotation power to the outside in the interlocking relationship with the rear stage side driving gear 143, and a one-way clutch mechanism 18 arranged between the rear stage side driving gear 143 and the rear stage side driven gear 152. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a drive device, and more particularly to a drive device that can output a plurality of rotational powers.

  As a configuration for driving a plurality of parallel loads using a single rotational power source, a plurality of gear trains are branched in parallel from the drive shaft of the rotational power source, and an output force gear of each gear train or A configuration in which each load is driven by an output shaft may be used. However, according to such a configuration, when a large load is applied to one output gear or output shaft and the rotation stops, the drive shaft of the rotational power source is also locked and the rotation is stopped. As a result, another output gear or Transmission of rotational power to the output shaft is also stopped.

  As a configuration that can output rotational power without stopping the rotation of other output gears or output shafts even when rotation is stopped due to a large load on a specific output gear or output shaft, each output gear from the drive shaft Or the structure which provides a friction mechanism before reaching each output shaft is mentioned. However, in the configuration in which the friction mechanism is provided, power transmission efficiency is reduced due to frictional resistance. For this reason, in order to ensure the output torque of the output gear or the output shaft, a large output requires a rotational power source, which may result in an increase in the size and cost of the device.

  Therefore, a configuration has been proposed in which a plurality of differential mechanisms are provided between the rotational power source and the output gear or output shaft, and the rotational power from the rotational power source is distributed by the differential mechanism. For example, in Patent Document 1, a single rotational power is branched into a plurality of rotational powers by a differential mechanism using a bevel gear, and the branched rotational powers are arranged on a plurality of output shafts arranged coaxially with a drive shaft. A communication configuration is disclosed. In addition, this Patent Document 1 uses a coupled planetary gear device to branch a single rotational power source into a plurality of rotational powers, and the plurality of branched rotational powers are arranged coaxially with the drive shaft. A configuration for transmitting to the output shaft is also disclosed.

  According to such a configuration, even when a large load is applied to a certain output gear or output shaft and the rotation cannot be performed, the drive shaft can continue to rotate. For this reason, transmission of rotational power can be continued with respect to another output gear or an output shaft.

JP-T 9-500709

  However, the differential mechanism using the bevel gear has a complicated structure, and the length in the direction of the drive shaft and the output shaft increases. Further, the configuration using the coupled planetary gear device also increases the length in the direction of the drive shaft and the output shaft. For this reason, it is difficult to reduce the size of the apparatus. Furthermore, since many types of gears are required, there is a risk of increasing the component cost.

  In a configuration in which the drive device outputs two rotational powers from one rotational power source, when there is rotational power output from one, the rotational power is also output from the other, and one outputs rotational power. If not, the other will not output rotational power.

  In view of the above circumstances, the problem to be solved by the present invention is to provide a driving device that can be reduced in size, to provide a driving device that can simplify the structure, or to determine the type or number of components. Providing a drive device that can be reduced, or providing two rotational power output systems, and when generating rotational power in a certain direction, the rotational power is output from both output systems, In the case of generating rotational power in a direction, a drive device that can output rotational power from only one output system is provided.

  In order to solve the above-described problems, the present invention provides a driving source and a driving device in which a driving force from the driving source is transmitted to an output unit via a transmission gear. A front gear and a rear gear disposed in the rear stage, and the output section has one output section to which driving force is transmitted from the front stage gear and the other output to which driving power is transmitted from the rear gear. The rear gear is composed of a driving gear driven by the front gear and a driven gear connected to the driving gear via a one-way clutch, and the rear gear is driven by the front gear. A driving gear coupled to the driving gear via a one-way clutch, and a driving force transmitted to the driving gear by forward rotation of the front gear is transmitted to the driven gear via a one-way clutch. And said The driving force transmitted to the other output unit and the other output unit and transmitted to the driving gear by the reverse rotation of the front gear is disconnected by the one-way clutch and transmitted only to one output unit. It is a summary.

  Here, it is preferable to have a blocking member that enters the rotation locus of the driven gear by reverse rotation of the front gear and prevents the driven gear and the driving gear from rotating.

  The rotation center of the blocking member is formed coaxially with the front gear, and the vicinity of the rotation center of the blocking member is in contact with the front gear in the axial direction and can be rotated by friction. The blocking member advances out of the rotation locus of the driven gear by the forward rotation of the front gear, and enters the rotation locus of the driven gear by the reverse rotation of the front gear and provides the driven gear and the driving gear. It is preferable to have a configuration that prevents rotation.

  The transmission gear has a planetary gear mechanism between the drive source and the front gear, and the planetary gear mechanism is a planetary gear support gear that rotatably supports a sun gear and planet gears meshed with the sun gear; An internal gear meshed with the planetary gear, and any one of the sun gear, the planetary gear support gear, and the internal gear is an input gear to which a driving force of the drive source is input, and the input It is preferable that any two of the sun gear, the planetary gear support gear, and the ring gear except for the gears are respectively connected to one front gear and the other front gear that are formed in two lines on the rear side from the front gear. .

  It is preferable that the front gear and the rear gear, which are formed in two lines on the rear side from the front gear, are arranged coaxially.

  According to the present invention, when the front gear rotates in the forward direction, rotational power is output from the front gear to the outside, and the rotational power transmitted from the front gear to the driving gear of the rear gear is a one-way clutch. Is transmitted to the driven gear of the rear stage side gear via the, and output to the outside. When the front gear rotates in the reverse direction, rotational power is output to the outside from the front gear, but when the reverse rotational power is transmitted from the front gear to the driving gear of the rear gear, the one-way clutch is Rotational power is not transmitted to the driven gear of the side gear, and the rear stage side gear does not output rotational power to the outside. Thus, when the front stage side gear rotates in the forward direction, rotational power is output from both the front stage side gear and the rear stage side gear, and when the front stage side gear rotates in reverse, only the front stage side gear outputs rotational power, and the rear stage side gear. Can be configured not to output rotational power. And such operation | movement can be implement | achieved with a train of trains from a rotational power source, and size reduction of a drive device and simplification of a structure can be achieved.

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

  FIG. 1 is an exploded perspective view (partially including a partial cross-sectional view) schematically showing the configuration of the drive device according to the first embodiment of the present invention. In FIG. 1, the casing is omitted.

  The drive device 1 a according to the first embodiment includes a rotational power source 11, a first transmission gear 13, a front-side gear 201, a rear-side gear 202, a claw wheel 16, and a key 17. The front stage gear 201 includes a front stage driving gear 141, a front stage driven gear 151, and an intermediate transmission gear 143. The rear stage side gear 202 includes a rear stage side driving gear 142, the one-way clutch mechanism 18, and a rear stage side driven gear 152.

  The drive device 1a according to the first embodiment branches a single rotational power output from the rotational power source 11 into two rotational powers, and each of the branched two rotational powers is connected to a front-side driven gear 151. It can be output to the outside via each of the rear side driven gears 152.

  The transmission path of the rotational power in the drive device 1a according to the first embodiment will be briefly described. The rotational power of the rotational power source 11 is transmitted from the first transmission gear 13 to the front-side driving gear 141. The rotational power transmitted to the front-stage driving gear 141 is transmitted to each of the front-stage driven gear 151 and the intermediate transmission gear 143 formed integrally with the front-stage driving gear 141. The rotational power transmitted to the intermediate transmission gear 143 is transmitted to the rear-stage driven gear 152 via the rear-stage driving gear 142 and the one-way clutch mechanism 18.

  The direction of rotation of the front driven gear 151 is determined according to the direction of rotation of the rotational power of the rotational power source 11. In other words, the front-stage driven gear 151 can output either rotational power in the normal direction or reverse direction depending on the direction of rotation of the rotational power of the rotational power source 11. On the other hand, the second-stage driven gear 152 can output rotational power of rotation in a specific direction by the one-way clutch mechanism 18, the ratchet wheel 16, and the key 17, but is opposite to the specific direction. The rotation power of the rotation is not output.

  Accordingly, when the rotational power source 11 generates rotational power of rotation in a specific direction, the driving device 1a according to the first embodiment includes the front-stage driven gear 151 and the rear-stage driven gear 152, respectively. The rotational power corresponding to the direction of rotation of the rotational power of 11 is output. The ratio of the rotational speeds of the front side driven gear 151 and the rear side driven gear 152 is determined by the ratio of the number of teeth of the intermediate transmission gear 143 and the rear side driving gear 142.

  When the rotational power source 11 generates rotational power that rotates in a direction opposite to the specific direction, only the front driven gear 151 outputs reverse rotational power, and the rear driven gear 152 Does not output rotational power.

  For convenience of explanation below, the rotational power of the rotational power of the gears 13, 141, 142, 151, 152 and the rotational power source 11 when both the front-stage driven gear 151 and the rear-stage driven gear 152 can output rotational power. The direction is referred to as “forward rotation”. Further, the rotation direction of the rotational power of each of the gears 13, 141, 142, 151 and the rotational power source 11 when only the front-side driven gear 151 can output rotational power is the reverse rotation. ".

  That is, when the rotational power source 11 generates forward rotational power, each of the front-stage driven gear 151 and the rear-stage driven gear 152 can output forward rotational power to the outside, and the rotational power source 11 is reversely rotated. When the rotational power is generated, the front-stage driven gear 151 outputs the reverse rotational power to the outside, and the rear-stage driven gear 152 does not output the rotational power.

  In FIG. 1, the rotation directions indicated by the arrows a, c, e, g, and i for the gears 13, 141, 142, 151, and 152 are positive rotations, and the arrows b, d, f, h, and j indicate the rotation directions. The direction of rotation is reverse.

  The specific configuration of the drive device 1a according to the first embodiment is as follows.

  Various known rotational power sources can be applied to the rotational power source 11. For example, various known electric motors such as a servo motor can be applied. A first transmission gear 13 is provided on the rotating shaft 12 of the rotating power source 11 (which becomes a driving shaft in the driving device 1a according to the first embodiment). The first transmission gear 13 is a parallel shaft gear (referred to as a gear that transmits rotational motion in parallel secondary sections; the same applies hereinafter) or a cylindrical gear (a gear whose pitch circle diameter does not change along the rotational axis direction). The same shall apply hereinafter). For example, a spur gear can be applied.

  The front-stage driving gear 141, the intermediate transmission gear 143, and the front-stage driven gear 151 of the front-stage gear 201 are configured to be able to rotate integrally. Specifically, it has the following configuration. An intermediate transmission gear 143 is integrally provided on one end surface (the end surface facing the starboard in FIG. 1) of the front-side driving gear 141. Further, a fitting hole 1411 is formed on the other end surface (the end surface facing left front in FIG. 1). For example, if the front drive gear 141 and the intermediate transmission gear 143 are resin-molded, a configuration in which these are integrally molded can be applied.

  The front-side driven gear 151 is provided with a fitting projection 1511 on one end face (the end face facing the starboard in FIG. 1). The fitting protrusion 1511 is fitted into a fitting hole 1411 provided on the end surface of the front-stage driving gear 141. Accordingly, the front-stage driving gear 141, the intermediate transmission gear 143, and the front-stage driven gear 151 can be rotated coaxially and integrally. The front-side driving gear 141 is engaged with the first transmission gear 13 and can receive rotational power from the first transmission gear 13. As described above, the front-side driving gear 141, the intermediate transmission gear 143, and the front-side driven gear 151 are compound gears that use the front-side driving gear 141 as a drive gear and the intermediate transmission gear 143 and the front-stage driven gear 151 as a driven gear. Constitute.

  A common central axis of the front-side driving gear 141, the intermediate transmission gear 143, and the front-side driven gear 151 and the rotation shaft 12 of the rotational power source 11 are set in parallel. A parallel shaft gear or a cylindrical gear can be applied to the front drive gear 141 and the intermediate transmission gear 143. The type and configuration of the front-stage driven gear 151 are appropriately set according to the configuration on the side that receives power transmission from the front-stage driven gear 151.

  A parallel shaft gear or a cylindrical gear can be applied to the rear drive gear 142. This rear-stage driving gear 142 meshes with the intermediate transmission gear 143 and can receive transmission of rotational power from the intermediate transmission gear 143. The configuration of the rear-stage driven gear 152 is appropriately set according to the configuration on the side that receives power transmission from the rear-stage driven gear 152. The intermediate transmission gear 142 and the rear side driven gear 152 are arranged coaxially and are connected by the one-way clutch mechanism 18.

  The configuration of the one-way clutch mechanism 18 is as follows. The one-way clutch mechanism 18 includes a drive shaft 183 provided on the rear-stage driving gear 142, a driven shaft 184 provided on the rear-stage driven gear 152, and a coil spring 181.

  The drive shaft 183 is formed as a cylindrical hollow shaft that protrudes in the direction of the rotation axis from one end surface of the rear drive gear 142. The drive shaft 183 is provided with a slit 182. The coil spring 181 is formed in a diameter that can be loosely inserted into the drive shaft 183, and an engagement portion 1811 is provided at one end of the coil spring 181. The engaging portion 1811 has a configuration in which, for example, one end of a wire forming the coil spring 181 is bent and raised outward. The driven shaft 184 is a columnar shaft that protrudes in the direction of the rotation axis from one end surface of the rear-stage driven gear 152 and has a diameter that can be loosely inserted inside the coil spring 181.

  The coil spring 181 is loosely inserted into the drive shaft 183, and the driven shaft 184 is loosely inserted inside the coil spring 181. When the coil spring 181 is loosely inserted into the drive shaft 183, the engaging portion 1811 of the coil spring 181 engages with a slit 182 provided on the drive shaft 183. For this reason, the coil spring 181 cannot rotate inside the drive shaft 183.

  When the drive shaft 183 rotates in a certain direction (the direction of the arrow g in FIG. 1, that is, forward rotation), the coil spring 181 is formed by friction between the inner peripheral surface of the coil spring 181 and the outer peripheral surface of the driven shaft 184. A tension in the circumferential direction is applied to the wire, and the diameter of the coil spring 181 is reduced. The coil spring 181 tightens the driven shaft 184, and the driven shaft 184 rotates integrally with the drive shaft 183 by the frictional force generated by the tightening.

  On the other hand, when the drive shaft 183 rotates in a direction opposite to the specific direction (the direction of the arrow h, that is, reverse rotation), the diameter of the coil spring 181 increases. For this reason, the frictional force between the coil spring 181 and the driven shaft 184 is reduced, and the coil spring 181 is likely to idle around the outer peripheral surface of the driven shaft 184.

  On one end surface of the rear side driven gear 152 (preferably the end surface on which the driven shaft 184 is not provided), a claw wheel 16 that rotates integrally with the rear side driven gear 152 is provided. For example, if the rear-stage driven gear 152 is resin-molded, a configuration in which the rear-stage driven gear 152, the ratchet wheel 16, and the driven shaft 184 are integrally molded can be applied. On the outer periphery of the claw wheel 16, serrated claws that are uneven along the circumferential direction are provided.

  The key 17 is a substantially rod-shaped member, and an engagement portion 173a that can be engaged with the claw on the outer peripheral surface of the claw wheel 16 is provided at the tip thereof. The base end portion of the key 17 is supported so as to be rotatable (or swingable) coaxially or substantially coaxially with the rotation center of the front driven gear 151. The base end portion of the key 17 may be one end surface of the front driven gear 151 (as shown in FIG. 1, the end surface on which the fitting protrusion 1511 is not provided) by the washer 171 and the spring 172. Contact in a biased state (preferably).

  The base end portion of the key 17 may be configured to urge and contact the end surface of the front driven gear 151, and is not limited to the above configuration. For example, a configuration using a spring washer, a configuration using a leaf spring, a configuration using an elastic body such as rubber, or the like, or a configuration in which an elastic pressing piece is provided in a casing (not shown) may be used.

  Therefore, in a state where the rotation of the key 17 is not hindered, the key 17 rotates integrally with the front-stage driven gear 151 by the frictional force between the key 17 and the end surface of the front-stage driven gear 151. On the contrary, in a state where the rotation of the key 17 is hindered (for example, a state where an external force is applied to the key 17 or a state where the key 17 is in contact with some member), the key 17 does not rotate. The front-side driven gear 151 can be rotated by sliding with the side driven gear 151.

  According to the one-way clutch mechanism 18, the ratchet wheel 16, and the key 17, when the front-stage driven gear 151 rotates in the forward direction, the engagement portion 173 a of the key 17 moves in a direction away from the hook wheel 16. When the engaging portion 173a of the key 17 and the claw of the claw wheel 16 are engaged, the engaging portion 173a of the key 17 is pushed out from the rotation locus of the claw wheel 16 by the outer peripheral surface of the claw wheel 16, The This engagement is released. Therefore, the second output gear 152 can rotate (forward rotation) without being blocked by the key 17. The driven shaft 184 rotates integrally with the drive shaft 183 by friction between the inner peripheral surface of the coil spring 181 and the outer peripheral surface of the driven shaft 184. Accordingly, the rotational power transmitted to the rear-stage driving gear 142 is transmitted to the rear-stage driven gear 152 via the one-way clutch mechanism 18.

  On the other hand, when the front-stage driven gear 151 rotates in the reverse direction, the key 17 rotates and the engaging portion 173a enters the rotation locus of the ratchet wheel 16 and engages with the claw of the tooth wheel 16. For this reason, the reverse rotation of the rear driven gear 152 is prevented by the key 17. When the rear driving gear 142 rotates in the reverse direction, the frictional force between the coil spring 181 and the driven shaft 184 is reduced. Accordingly, in this case, the drive shaft 183 and the coil spring 181 idle on the driven shaft 184, and the rear-stage driven gear 152 does not rotate (reversely rotate). Therefore, the rotational power transmitted to the rear-stage driving gear 142 is not transmitted to the rear-stage driven gear 152.

  When such a one-way clutch mechanism 18, the ratchet wheel 16 and the key 17 are applied, rotational power in only one direction can be reliably transmitted with a small and simple configuration. In addition, the position where this nail | claw 16 and the key 17 are provided is not limited to the said position. The installation position is not limited as long as the operation can be performed. The one-way clutch mechanism 18 provided between the rear-stage driving gear 142 and the rear-stage driven gear 152 is not limited to the above-described configuration, and various known one-way clutches can be applied. For example, a non-reversing clutch such as a ratchet clutch or a roller clutch may be used. In short, when the rear-stage driving gear 142 rotates forward, the rotational power can be transmitted from the rear-stage driving gear 142 to the rear-stage driven gear 152. When the rear-stage driving gear 142 rotates in the reverse direction, the rear-stage driving gear 142 transmits the rear-stage driven gear. Any configuration that does not transmit rotational power to the gear 152 may be used.

  The operation of the drive device 1a according to the first embodiment having such a configuration is as follows.

  The rotational power of the rotational power source 11 is transmitted to the front drive gear 141 via the first transmission gear 13. Then, it is transmitted from the front-stage driving gear 141 to the front-stage driven gear 151 and the intermediate transmission gear 143. The rotational power transmitted to the front side driven gear 151 can be output to the outside. The rotational power transmitted to the intermediate transmission gear 143 is further transmitted to the rear drive gear 142 of the rear gear 202.

  FIG. 2 is a plan view schematically showing the operation of the driving device 1a according to the first embodiment. Specifically, FIG. 2A shows a state where the front-stage driven gear 151 and the rear-stage driven gear 152 are rotating forward, and FIG. 2B shows a state where the front-stage driven gear 151 rotates reversely and The state which the side driven gear 152 has stopped is shown.

  When the rotational power source 11 generates forward rotational power, forward rotational power is transmitted to the front driven gear 151. Therefore, the front-stage driven gear 151 can output the rotational power of the normal rotation to the outside.

  As shown in FIG. 2A, when the front driven gear 151 rotates in the forward direction (rotates in the direction of arrow e in the figure), the key 17 rotates integrally by the frictional force with the end surface of the front driven gear 151. The engaging portion 173a moves away from the claw wheel 16. For this reason, the engaging portion 173 a of the key 17 comes out of the rotation locus of the claw wheel 16, and the engaging portion 173 a of the key 17 does not interfere with the rotation of the claw wheel 16.

  Further, as described above, when the rotational power of the positive rotation of the rotational power source 11 is transmitted to the rear-stage driving gear 142 and the rear-stage driving gear 142 rotates in the forward direction, the one-way clutch mechanism 18 includes the intermediate transmission gear 173a and the rear-stage driven gear. The gear 152 is connected so that rotational power can be transmitted. Therefore, the rear-stage driven gear 152 rotates in the forward direction (rotates in the direction of arrow i in the drawing), and the rotational power of the forward rotation can be output to the outside.

  As described above, when the hook wheel 16 is rotated forward with the engaging portion 173a of the key 17 engaged with the pawl of the hook wheel 16, the engaging portion 173a of the key 17 is Extruded from within the rotation trajectory. Therefore, even if the engaging portion 173a of the key 17 rotates integrally with the front-stage driven gear 151 and does not move away from the claw wheel 16, the claw wheel 16 (and the rear-stage driven gear 152) is moved by the engaging portion 173a of the key 17. Rotation is not hindered.

  Thus, when the rotational power source 11 generates forward rotational power, the front-side driven gear 151 and the rear-side driven gear 152 can output positive rotational power to the outside.

  As shown in FIG. 2B, when the rotational power source 11 generates reverse rotational power, the reverse rotational power is transmitted to the front driven gear 151. Therefore, the front side driven gear 151 can output the rotational power of reverse rotation (rotation in the direction of arrow f in the figure) to the outside. On the other hand, when the rotational power source 11 generates reverse rotational power and the rear-stage driving gear 142 rotates reversely, the frictional force between the coil spring 181 and the driven shaft 184 in the one-way clutch mechanism 18 decreases. When the front-stage driven gear 151 rotates in the reverse direction, the key 17 rotates positively integrally with the front-stage driven gear 151, and the engaging portion 173a enters the rotation locus of the ratchet wheel 16 and engages with the claw. As a result, the ratchet wheel 16 and the rear side driven gear 152 cannot be rotated in the reverse direction.

  Thus, when the rotational power source 11 generates reverse rotational power, the front-side driven gear 151 can output reverse rotational power to the outside. However, the rear-stage driven gear 152 does not rotate and does not output the reverse rotational power to the outside. Then, the engaging portion 173a of the key 17 engages with the claw of the claw wheel 16, and the claw wheel 16 is locked. Therefore, even if a force that reversely rotates the rear-stage driven gear 152 is applied from the outside, the rear-stage driven gear 152 cannot be reversely rotated.

  As described above, the drive device 1a according to the first embodiment, when the rotational power source 11 generates rotational power of rotation in a specific direction, the front-stage driven gear 151 and the rear-stage driven gear 152 are According to the direction of rotation of the rotational power of the rotational power source 11, rotational power having a predetermined rotational speed ratio can be output. When the rotational power source 11 generates rotational power in the direction opposite to the specific direction, the front-side driven gear 151 outputs rotational power in the direction opposite to the specific direction, and the rear-stage driven gear. The gear 152 does not output rotational power. In this case, even if a force is applied to the rear side driven gear 152 from the outside, the rear side driven gear 152 does not rotate in the direction opposite to the certain direction.

  In the first embodiment, the configuration using the ratchet wheel 16 and the key 17 is shown as the configuration for preventing the reverse rotation of the rear-stage driven gear 152, but the present invention is not limited to this configuration. Therefore, a configuration that does not use a claw wheel will be described. FIG. 3 is an external perspective view schematically showing a configuration of a main part of a drive device that does not use a ratchet wheel. In addition, the same code | symbol is attached | subjected and used for the same part as the said drive device, and description is abbreviate | omitted.

  As shown in FIG. 3, an engaging portion 173b is formed at the tip of the key 17 of the driving device 1b. The engaging portion 173b can engage with the outer peripheral surface of the rear-stage driven gear 152, that is, the teeth. When the front side driven gear 151 rotates in the reverse direction, the key 17 rotates integrally with the front side driven gear 151, and the engaging portion 173 b engages with the teeth of the rear side driven gear 152. As a result, the rear side driven gear 152 cannot rotate.

  Even if it is such a structure, there can exist an effect similar to the above-mentioned.

  Next, a second embodiment of the present invention will be described. FIG. 4 is a plan view schematically showing a configuration of a gear train included in the drive device according to the second embodiment of the present invention. The drive device 5 according to the second embodiment includes a rotational power source 51, a second transmission gear 52, four transmission gears 531, 532, 533, 534, a differential mechanism 54, and a first output mechanism. 55 and a second output mechanism 56.

  The differential mechanism 54 branches the single rotational power of the rotational power source 51 into two rotational powers. The first output mechanism 55 and the second output mechanism 56 further branch from each of the two rotational powers branched by the differential mechanism 54 into two rotational powers. Each of the first output mechanism 55 and the second output mechanism 56 is a gear train having the same configuration as that obtained by removing the rotational power source 11 and the first transmission gear 13 from the drive device 1a according to the first embodiment. Is provided. In FIG. 4, the toothed wheel and the key included in the first output mechanism 55 and the second output mechanism 56 are omitted.

  Thus, the drive device 5 according to the second embodiment can branch the single rotational power of the rotational power source 51 into four rotational powers. And two of the four rotational powers can output both forward and reverse rotational powers according to the rotational direction of the rotational power transmitted to the first output mechanism 55 and the second output mechanism 56, respectively. The other two output rotational power in one direction of rotation and do not output rotational power in the opposite direction.

  In the following description, the names of the elements and members constituting the first output mechanism 55 and the second output mechanism 56 are the corresponding elements or members of the drive device 1a according to the first embodiment. The name shall be used.

  Various known rotational power sources such as various electric motors can be applied to the rotational power source 51 of the driving device 5 according to the second embodiment. For example, various servo motors can be applied. A second transmission gear 52 is provided on the rotation shaft 57 of the rotational power source 51.

  The second transmission gear 52 meshes with the third transmission gear 531. Further, the third transmission gear 531 and the fourth transmission gear 532 are configured to be able to rotate integrally, and are rotatably supported by a common center shaft 535. The fourth transmission gear 532 meshes with the fifth transmission gear 533, and the fifth transmission gear 533 further meshes with the input gear 541 of the differential mechanism 54.

  Thus, the rotational power of the rotational power source 51 is differentially transmitted via the second transmission gear 52, the third transmission gear 531, the fourth transmission gear 532, and the fifth transmission gear 533. It is transmitted to the input gear 541 of the mechanism 54. The rotational speed of the rotational power transmitted to the input gear 541 of the differential mechanism 54 is adjusted by the third transmission gear 531, the fourth transmission gear 532, and the fifth transmission gear 533. Further, the distance between the rotation shaft 57 of the rotational power source 51 and the center shaft 542 of the differential mechanism 54 can be adjusted.

  The rotational shaft 57 of the rotational power source 51, the central shaft 535 of the third transmission gear 531 and the fourth transmission gear 532, the central shaft (not shown) of the fifth transmission gear 533, and the center of the differential mechanism 54 The shafts 542 are set parallel to each other. The second transmission gear 52, the third transmission gear 531, the fourth transmission gear 532, the fifth transmission gear 533, and the input gear 541 of the differential mechanism 54 are all parallel shaft gears such as spur gears. Or a cylindrical gear is applied.

  The differential mechanism 54 includes an input gear 541, a planetary gear mechanism, and two sets of output gears 547 and 548. Hereinafter, for convenience of explanation, one of the two output gears of the differential mechanism 54 is referred to as a “first intermediate output gear 547”, and the other is referred to as a “second intermediate output gear 548”.

  The differential mechanism 54 can branch the rotational power transmitted to the input gear 541 into two rotational powers by the planetary gear mechanism. One of the two branched rotational powers can be transmitted to the first intermediate output gear 547 and the other can be transmitted to the second intermediate output gear 548.

  The planetary gear mechanism includes a sun gear 543, a plurality of planetary gears 544, a planetary gear carrier 545, and an internal gear 546. The sun gear 543 is configured to rotate integrally with the input gear 541. The planetary gear 544 meshes with the sun gear 543 and is rotatably supported by the planetary gear carrier 545. The planetary gear carrier 545 is configured to rotate integrally with the first intermediate output gear 547. The internal gear 546 meshes with the planetary gear 544 and is configured to rotate integrally with the second intermediate output gear 548.

  The input gear 541, the sun gear 543, the planetary gear carrier 545, and the first intermediate output gear 547 are rotatably supported by a common central shaft 542, respectively. The internal gear 546 and the second intermediate output gear 548 are rotatably supported by the input gear 541 and / or the sun gear 543 and can rotate concentrically with the input gear 541 and the sun gear 543.

  The operation of the differential mechanism 54 having such a configuration is as follows. When rotational power is transmitted to the input gear 541, the sun gear 543 rotates integrally with the input gear 541. The rotation of the sun gear 543 causes the planetary gear 544 to rotate and / or revolve around the sun gear 543. Then, the planetary gear carrier 545 rotates integrally with the revolution of the planetary gear 544, and the first intermediate output gear 547 rotates integrally with the planetary gear carrier 545.

  Further, the internal gear 546 rotates as the planetary gear 544 rotates and / or revolves, and the second intermediate output gear 548 rotates integrally with the internal gear 546.

  Thus, the differential mechanism 54 branches the rotational power transmitted to the input gear 541 into two rotational powers, and can transmit one of the branched two rotational powers to the first intermediate output gear 547 and the other to the first power. Can be transmitted to the second intermediate output gear 548.

  The rotational speeds and transmitted torques of the first intermediate output gear 547 and the second intermediate output gear 548 of the differential mechanism 54 are transmitted to the first intermediate output gear 547 and the second intermediate output gear 548, respectively. It changes automatically according to the applied load. When a large load is applied to one of the first intermediate output gear 547 and the second intermediate output gear 548 and the rotation stops, the corresponding torque is transmitted to the other. As a result, even if one of the first intermediate output gear 547 and the second intermediate output gear 548 stops, the rotation of the other can be continued without stopping.

  For example, when the load applied to the first intermediate output gear 547 increases, the rotational speed of the first intermediate output gear 547, that is, the revolution speed of the planetary gear 544, decreases according to the amount of increase in the load. And a rotation speed becomes large according to the variation | change_quantity of revolution speed. As a result, the ratio of the rotational power transmitted from the sun gear 543 to the first intermediate output gear 547 and the second intermediate output gear 548 is reduced to the first intermediate output gear 547, and the second intermediate output gear 547 is reduced. The ratio transmitted to the output gear 548 increases.

  On the other hand, when the load applied to the second intermediate output gear 548 increases, the rotation speed of the second intermediate output gear 548, that is, the rotation speed of the internal gear 546 decreases according to the increase in the load. Even if the internal gear 546 is subjected to a load that reduces the rotation speed, the planetary gear 544 changes its rotation speed and / or revolution speed and continues to revolve. Therefore, the first intermediate output gear 547 Rotation can be continued. In this case, the rotational power transmitted from the sun gear 543 to the first intermediate output gear 547 and the second intermediate output gear 548 has a higher ratio of transmission to the first intermediate output gear 547, and the second The ratio transmitted to the intermediate output gear 548 becomes smaller.

  Changes in the respective rotational speeds accompanying changes in the loads applied to the first intermediate output gear 547 and the second intermediate output gear 548 are caused by the sun gear 543, the planetary gear 544, the planetary gear carrier 545, and the internal gear 546, respectively. It is automatically determined according to the applied force and reaction force. For this reason, optimal rotational power is automatically transmitted according to the load applied to each of the first intermediate output gear 547 and the second intermediate output gear 548.

  The first intermediate output gear 547 meshes with the front drive gear 551 of the first output mechanism 55. The second intermediate output gear meshes with the sixth transmission gear 534, and the sixth transmission gear 534 further meshes with the front drive gear 561 of the second output mechanism 56. Accordingly, one of the two rotational powers branched from the differential mechanism 54 is transmitted from the first intermediate output gear 547 to the front-stage driving gear 551 of the first output mechanism 55. The other is transmitted from the second intermediate output gear 548 to the front drive gear 561 of the second output mechanism 56 via the sixth transmission gear 534.

  The sixth transmission gear 534 adjusts the direction and speed of rotation of the rotational power transmitted from the second intermediate output gear 548 to the front-stage driving gear 561 of the second output mechanism 56. In the differential mechanism 54, there may occur a case where the revolving direction and revolving speed of the planetary gear 544 are different from the revolving direction and revolving speed of the internal gear 546. As a result, the rotation direction and the rotation speed of the first intermediate output gear 547 and the second intermediate output gear 548 may be different from each other.

  Therefore, a sixth transmission gear 534 is interposed between the second intermediate output gear 548 and the front-side driving gear 561 of the second output mechanism 56 to transmit to the front-side driving gear 561 of the second output mechanism 56. The rotational direction and rotational speed of the rotating power to be adjusted are adjusted. Then, rotational power having the same direction of rotation and the same or almost the same rotational speed can be transmitted to each of the front-stage driving gear 551 of the first output mechanism 55 and the front-stage driving gear 561 of the second output mechanism 56. Like that.

  The sixth transmission gear 534 also has a function of adjusting the inter-axis distance between the second intermediate output gear 548 and the front-stage driving gear 561 of the second output mechanism 56. That is, by interposing the sixth transmission gear 534, the front-stage driving gear 551 of the first output mechanism 55 and the front-stage driving gear 561 of the second output mechanism 56 can be disposed coaxially.

  Note that the drive device 5 according to the second embodiment shown in FIG. 4 includes a single gear (that is, a sixth gear) between the second intermediate output gear 548 and the front drive gear 561 of the second output mechanism 56. The transmission gear 534) is interposed, but the number and configuration of the gears interposed between the second intermediate output gear 548 and the front drive gear 561 of the second output mechanism 56 are not limited. . For example, in order to adjust the rotational speed, a compound gear composed of gears having different numbers of teeth is provided, one of the compound gears meshes with the second intermediate output gear 548, and the other is coupled to the second output mechanism 56. The structure which meshes | engages with the front | former stage side drive gear 561 may be sufficient.

  Each structure of the 1st output mechanism 55 and the 2nd output mechanism 56 is substantially the same as the structure remove | excluding the rotational power source 11 and the 1st transmission gear 13 from the drive device 1a concerning 1st embodiment. That is, the first output mechanism 55 and the second output mechanism 56 are, respectively, the front-stage driving gears 551, 561, the intermediate transmission gears 553, 563, the rear-stage driving gears 552, 562, and the front-stage driven gear 555. , 565, rear side driven gears 556, 566, and one-way clutch mechanisms 554, 564 are provided. Further, although not shown, a key and a claw wheel are provided.

  That is, in the driving device 1a according to the first embodiment, the front-stage driving gear 141 meshes with the first transmission gear 13 and receives the rotational power (see FIG. 1), whereas the second embodiment has the second embodiment. The first output mechanism 55 and the second output mechanism 56 of the driving device 5 are engaged with the first intermediate output gear 547 and the sixth transmission gear 534 of the differential mechanism 54, respectively, and receive transmission of rotational power. Configured as follows. Therefore, detailed description of the first output mechanism 55 and the second output mechanism 56 is omitted.

  When the rotational power source 51 generates forward rotational power, the first-stage driven gears 555 and 565 and the second-stage driven gears 556 and 566 of the first output mechanism 55 and the second output mechanism 56, respectively. Therefore, a total of four positive rotational powers can be output to the outside, two each. On the other hand, when the rotational power source 51 generates reverse rotational power, the first-stage driven gears 555 and 565 of the first output mechanism 55 and the second output mechanism 56 respectively generate reverse rotational power. It can output to the outside, and the rear-stage driven gears 556 and 566 do not rotate.

  The rotational shaft 57 of the rotational power source 51, the central shaft 542 of the differential mechanism 54, the central shafts of the respective gears included in each of the first output mechanism 55 and the second output mechanism 56, and third to sixth transmission gears. The central axes of 531 to 534 are arranged in parallel to each other. Therefore, the gears included in the second transmission gear 52, the third to sixth transmission gears 531 to 534, the differential mechanism 54, the first output mechanism 55, and the second output mechanism 56 are parallel to a spur gear or the like. A shaft gear or a cylindrical gear can be applied.

  By arranging the central axes in parallel, the rotational power source 51, the third to sixth transmission gears 531 to 534, the differential mechanism 54, the first output mechanism 55, and the second output. The mechanism 56 can be arranged in parallel. Furthermore, a cylindrical gear such as a spur gear or a parallel shaft gear can be applied to each gear constituting the gear train of the driving device 5 according to the second embodiment. Therefore, it is possible to shorten the dimensions in the central axis direction of the driving device 5 according to the second embodiment.

  When the load applied to the front-stage driven gear 555 or the rear-stage driven gear 556 of the first output mechanism 55 changes, the load applied to the first intermediate output gear 547 of the differential mechanism 54 changes according to this change. When the load applied to the front side driven gear 565 or the rear side driven gear 566 of the second output mechanism 56 changes, the load applied to the second intermediate output gear 548 changes in accordance with this change. Then, as described above, the differential mechanism 54 automatically distributes the optimum rotational power according to the change in the load applied to the first intermediate output gear 547 and the second intermediate output gear 548.

  Specifically, when a large load is applied to at least one of the front driven gear 555 and the rear driven gear 556 of the first output mechanism 55, a large load is applied to the first intermediate output gear 547, The rotational speed of the one intermediate output gear 547 decreases. For this reason, the rotation speed of the first-stage driven gear 555 and the second-stage driven gear 556 of the first output mechanism 55 decreases while maintaining the rotation speed ratio constant.

  When at least one of the front-stage driven gear 555 and the rear-stage driven gear 556 of the first output mechanism 55 is subjected to a larger load and stops rotating, the rotation of the first intermediate output gear 547 stops, The rotation of both the front-stage driven gear 555 and the rear-stage driven gear 556 of one output mechanism 55 stops.

  The differential mechanism 54 automatically distributes to the second intermediate output gear 548 the rotational power corresponding to the decrease or stoppage of the rotation speed of the first intermediate output gear 547. For this reason, the ratio of the rotational power transmitted to the second intermediate output gear 548 increases, and as a result, the rotational power transmitted to the front-stage driven gear 565 and the rear-stage driven gear 566 of the second output mechanism 56 increases. Become.

  The same applies when a large load is applied to at least one of the front side driven gear 565 and the rear side driven gear 566 of the second output mechanism 56 to reduce the rotation speed or when the rotation stops. That is, the rotational power whose rotational speed has been reduced or stopped by the load applied to the front-stage driven gear 565 and the rear-stage driven gear 566 of the second output mechanism 56 is transferred to the first intermediate output gear 547 by the differential mechanism 54. As a result, the rotational power transmitted to the front side driven gear 555 and the rear side driven gear 556 of the first output mechanism 55 is increased.

  As described above, even when a large load is applied to any of the front-side driven gears 555 and 565 and the rear-side driven gears 556 and 566 of the first output mechanism 55 or the second output mechanism 56, the differential The magnitude of the rotational power automatically distributed by the mechanism 54 is adjusted. Further, even if the rotation of one of the first-stage driven gears 555 and 565 or the second-stage driven gears 556 and 566 of the first output mechanism 55 and the second output mechanism 56 stops, the other continues to output the rotational power. be able to. Therefore, even when a large load is applied to at least one of the front side driven gears 555 and 565 and the rear side driven gears 556 and 566 of the first output mechanism 55 or the second output mechanism 56, the driving according to the second embodiment is performed. It is possible to prevent the device 5 from being able to output rotational power as a whole and a reduction in output.

  Next, a specific configuration of the drive device 5 according to the second embodiment will be described. FIG. 5 is an exploded perspective view (partially including a partial cross-sectional view) schematically showing a configuration of a main part of the drive device 5 according to the second embodiment, and FIGS. 6 and 7 are cross-sectional views of the drive device 5. It is. FIGS. 6A and 7A show the configuration from the rotational power source 51 to the first output mechanism, and FIGS. 6B and 7B show the second output mechanism from the rotational power source 51. The structure over is shown. In FIG. 5, the casing 8 is omitted.

  As shown in FIG. 5 to FIG. 7, the second transmission gear 52 is provided on the rotation shaft 57 of the rotational power source 51, and the second transmission gear 52 meshes with the third transmission gear 531. FIG. 5 shows a configuration in which a servo motor is applied as the rotational power source 51.

  The third transmission gear 531 and the fourth transmission gear 532 have a structure in which gears having different numbers of teeth are integrally coupled in the axial direction (in other words, the third transmission gear 531 and the fourth transmission gear 532. The third transmission gear 531 is a driving gear and the fourth transmission gear 532 is a driven gear), and is supported by a common central shaft 535 so as to be integrally rotatable. A configuration in which the third transmission gear 531 and the fourth transmission gear 532 are integrally formed of, for example, a resin material can be applied.

  The fourth transmission gear 532 meshes with the fifth transmission gear 533. The fifth transmission gear 533 is rotatably supported by the center shaft 536 and further meshes with the input gear 541 of the differential mechanism 54.

  The input gear 541 has a substantially disk shape, and is provided with a substantially cylindrical projection portion 5411 that projects along the direction of the central axis 542 on one end face thereof. A sun gear 543 is provided at the tip of the protrusion 5411. In other words, the input gear 541 and the sun gear 543 of the differential mechanism 54 constitute a compound gear having the input gear 541 as a drive gear and the sun gear 543 as a driven gear. The input gear 541 and the sun gear 543 are formed with shaft holes into which the center shaft 542 can be freely inserted. A configuration in which the input gear 541 and the sun gear 543 are integrally formed of, for example, a resin material can be applied.

  The internal gear 546 is formed in a ring shape or a cylindrical shape having a short axial length. The second intermediate output gear 548 is formed in a disk shape. The internal gear 546 and the second intermediate output gear 548 are integrally connected. Therefore, the internal gear 546 and the second intermediate output gear 548 have a shape in which a circumferential standing wall is provided along the outer peripheral edge of one surface of the disk as a whole. Then, teeth are provided in the vicinity of the tip of the inner peripheral surface of the standing wall to constitute an internal gear 546. Further, teeth are provided on the outer peripheral surface on the proximal end side of the standing wall to constitute a second intermediate output gear 548.

  At the center of the internal gear 546 and the second intermediate output gear 548, a through hole is formed through which the protruding portion 5411 of the input gear 541 can be loosely inserted. A configuration in which the internal gear 546 and the second intermediate output gear 548 are integrally formed of, for example, a resin material can be applied.

  The planetary gear 544 has a disk shape or a cylindrical shape, and an axial hole is formed at the center thereof. The drive device 5 according to the second embodiment shown in FIG. 5 includes three planetary gears 544, but the number is not limited.

  The first intermediate output gear 547 is formed in an open disc shape. The planetary gear carrier 545 is formed in a cylindrical container shape having a shallow bottom (see a view from arrow a. The view from the arrow a is a view of the planetary gear 544 and the planetary gear carrier 545 as seen from the direction of the arrow a). . A central shaft 5451 for rotatably supporting the planetary gear 544 is provided at a portion corresponding to the inside of the bottom surface of the cylindrical container.

  The first intermediate output gear 547 and the planetary gear carrier 545 have a configuration in which they are coupled together. That is, the combined body as a whole has a cylindrical container shape with a shallow bottom. Then, teeth are provided on the outer peripheral surface in the vicinity of the opening of the portion corresponding to the side wall of the cylindrical container to constitute the first intermediate output gear 547. A portion corresponding to the bottom surface of the container functions as the planetary gear carrier 545. In addition, a shaft hole into which a common central shaft 542 of the input gear 541 and the combined body of the sun gear 543 can be loosely inserted is formed in a portion corresponding to the bottom surface of the cylindrical container.

  The first intermediate output gear 547 and the planetary gear carrier 545 can be configured to be integrally formed of, for example, a resin material.

  Further, the central shaft 542 of the input gear 541 and the sun gear 543 and the central shaft 536 of the fifth transmission gear 533 are set in parallel to each other.

  The assembly structure of the differential mechanism 54 is as follows.

  The projection 5411 of the input gear 541 and the sun gear 543 are loosely inserted into the through hole of the combined body of the internal gear 546 and the second intermediate output gear 548 from the side where the second intermediate output gear 548 is provided. Then, the sun gear 543 is projected through the through-hole to the side where the internal gear 546 is provided. As a result, the combined body of the internal gear 546 and the second intermediate output gear 548 is rotatably supported by the protruding portion 5411 of the input gear 541. Further, the input gear 541 and the second intermediate output gear 548 are close to each other along the direction of the central axis 542.

  The central shaft 5451 of the planetary gear carrier 545 is loosely inserted into the shaft hole of the planetary gear 544. Thereby, the planetary gear 544 is rotatably supported by the planetary gear carrier 545.

  A combined body of the internal gear 546 and the second intermediate output gear 548 and the first intermediate output gear 547 are arranged coaxially, and the first intermediate output gear 547 and the second intermediate output gear 548 are It arranges so that it may adjoin. Then, the planetary gear 544 supported by the planetary gear carrier 545 meshes with both the sun gear 543 and the internal gear 546.

  The first intermediate output gear 547 has a shape like a shallow cylindrical container, and a combined body of the internal gear 546 and the second intermediate output gear 548 is one on the side where the internal gear 546 is provided. The portion fits inside the first intermediate output gear 547. Then, in a state where a part of the combined body of the internal gear 546 and the second intermediate output gear 548 is fitted in the first intermediate output gear 547, the second intermediate output gear 548 protrudes to the outside. Therefore, the first intermediate output gear 547 and the second intermediate output gear 548 are close to each other in the direction of the central axis 542.

  In this manner, the input gear 541, the first intermediate output gear 547, and the second intermediate output gear 548 of the differential mechanism 54 are arranged close to each other in the direction of the central shaft 542. Further, since the central shaft 542 of the differential mechanism 54 and the rotational shaft 57 of the rotational power source 51 are parallel to each other, the differential mechanism 54 and the rotational power source 51 are arranged in a direction perpendicular to the axial direction (that is, in series). (In parallel rather than). Therefore, the center axis direction dimension of each gear of the driving device 5 according to the second embodiment can be reduced, and downsizing can be achieved.

  Then, the first intermediate output gear 547 meshes with the front drive gear 551 of the first output mechanism 55. Further, the second intermediate output gear 548 meshes with the sixth transmission gear 534, and the sixth transmission gear 534 meshes with the front drive gear 561 of the second output mechanism 56.

  The configurations of the first output mechanism 55 and the second output mechanism 56 are substantially the same as those obtained by removing the rotational power source 11 and the first transmission gear 13 from the drive device 1a according to the first embodiment as described above. It is. Note that, in FIG. 5, the elements or members constituting the first output mechanism 55 and the second output mechanism 56 of the drive device 5 according to the second embodiment are omitted from description. The same reference numerals as those of each element or each member of the corresponding driving device 1a according to the first embodiment are given.

  The first output mechanism 55 and the second output mechanism 56 have a configuration that is substantially mirror-symmetric in the direction of the rotation axis of each gear. Accordingly, the parts of the first output mechanism 55 and the second output mechanism 56 can be made common, and the parts cost can be reduced. In particular, if a resin gear is applied to each gear, it is possible to reduce the production cost by using a common gear molding die.

  Further, when the front-side driving gears 551 and 561 are disposed between the front-side driven gears 555 and 556 and the intermediate transmission gears 553 and 563, the front-side driving gears 551 and 561 and the intermediate transmission gears 553 and 563 are arranged. And the front-side driven gears 555 and 556, the rear-side driving gears 552 and 562, the rear-side driven gears 556 and 566, and the one-way clutch mechanisms 554 and 464 are arranged side by side. 551, 561 can be disposed between the rear drive gears 552, 562 and the rear driven gears 556, 566.

  Accordingly, the axial direction dimensions of the gears of the first output mechanism 55 and the second output mechanism 56 are determined by combining the rear-stage driving gears 552, 562, the rear-stage driven gears 556, 566, and the one-way clutch mechanisms 554, 564. The dimensions required for accommodating the three-dimensional object can be limited, and the axial dimension of each gear of the first output mechanism 55 and the second output mechanism 56 can be reduced.

  The central axis 57 of the rotational power source 51 and the central axes of the output gears 555, 556, 565, 566 are set in parallel. The central axis of other gears included in the first output mechanism 55 and the second output mechanism 56, the central axis 542 of the differential mechanism, and the central axis of each transmission gear are also the rotational axis 57 of the rotational power source 51 and each central axis. It is set parallel to the central axis of the output gears 555, 556, 565, 566.

  Therefore, parallel shaft gears such as spur gears or cylindrical gears can be applied to the gears incorporated in the drive device 5 according to the second embodiment, except for the output gears 555, 556, 565, 566. Therefore, the structure can be simplified and the drive device can be reduced in size as compared with a configuration using a helical gear or the like. Each output gear 555, 556, 565, 566 has a configuration corresponding to the configuration on the side that receives the transmission of rotational power.

  The drive device 5 according to the second embodiment has a configuration using the claw wheel 16 and the key 17. However, as shown in the modification of the first embodiment, the drive gears 556 and 566 at the rear stage side are key. The structure which 17 engagement parts 173b are engaged may be sufficient.

  Each of the two sets of output mechanisms receives the rotational power from the planetary gear mechanism, so that even when a large load is applied to one of the two sets of output mechanisms, the corresponding rotational power is distributed to the other. be able to. Therefore, the drive device can continue to output the rotational power without stopping as a whole.

  Further, in the configuration including two sets of output mechanisms, the planetary gear mechanism and the two sets of output mechanisms can be arranged in parallel by arranging them coaxially, and as a result, the axial dimension of the drive device is shortened. Can be achieved.

(Effect of this embodiment)
As described above, according to the driving devices 1a and 1b of the present embodiment, when the front gear 201 rotates in the forward direction, rotational power is output from the front driven gear 151 to the outside and the middle of the front gear 201 is provided. The rotational power transmitted from the transmission gear 143 to the driving gear 142 of the rear gear 202 is transmitted to the rear driven gear 152 via the one-way clutch mechanism 18 and output to the outside. When the front gear 201 rotates in reverse, rotational power is output from the front driven gear 151 to the outside. However, the intermediate transmission gear 143 of the front gear 201 rotates backward to the rear driving gear 142 of the rear gear 202. When the rotational power is transmitted, the one-way clutch mechanism 18 does not transmit the rotational power to the rear-stage driven gear 152, and the rear-stage gear 152 does not output the rotational power to the outside. As described above, when the front gear 201 rotates in the forward direction, the rotational power is output from both the front gear 201 and the rear gear 20, and when the front gear 201 rotates in the reverse direction, only the front gear 201 outputs the rotational power. The rear gear 202 can be configured not to output rotational power. And such operation | movement can be implement | achieved by the one line of train wheel from the rotational power source 11, and size reduction of the drive devices 1a and 1b and simplification of a structure can be achieved.

  Further, according to the driving devices 1a and 1b of the present embodiment, when the front gear 201 rotates in the reverse direction, the blocking member, that is, the key 17, enters the rotation locus of the rear driven gear 152 of the rear gear 202, and the rear driven The gear 152 is prevented from rotating with the rear-stage driving gear 142. Therefore, when the front gear 201 rotates in the reverse direction, the rear driving gear 152 of the rear gear 202 can be prevented from rotating.

  According to the driving device 5 of the present embodiment, each of the two sets of output mechanisms receives transmission of rotational power from the planetary gear mechanism, so that even when a large load is applied to one of the two sets of output mechanisms, it Can be distributed to the other. Therefore, the drive device 5 can continue to output the rotational power without stopping as a whole.

  According to the drive device 5 of this embodiment, the planetary gear mechanism and the two sets of output mechanisms can be arranged in parallel by arranging the two sets of the front gear and the rear gear on the driving shaft. As a result, the axial dimension of the drive device 5 can be shortened.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an exploded perspective view (partially including a partial cross-sectional view) schematically showing a configuration of a main part of a drive device according to a first embodiment of the present invention. FIG. 2 is a plan view schematically showing the operation of the drive device, in which (a) shows a state in which a front-stage driven gear and a rear-stage driven gear are normally rotated, and (b) is a rear-stage in which the front-stage driven gear is reversely rotated. The state which a side driven gear stops is shown. FIG. 10 is an exploded perspective view (including a partial cross-sectional view in part) schematically showing a configuration of a main part of a drive device according to a modified example. It is the top view which showed typically the structure of the gear train of the drive device concerning 2nd embodiment of this invention. FIG. 3 is an exploded perspective view (partially including a partial cross-sectional view) schematically showing a configuration of a main part of the drive device. It is sectional drawing which showed typically the structure of the principal part of the said drive device. It is sectional drawing which showed typically the structure of the principal part of the said drive device.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1a Drive apparatus concerning 1st embodiment 11 Rotation power source 12 Rotation shaft of a rotation power source 13 1st transmission gear 141 Front-stage drive gear 1411 Fitting hole of front-stage drive gear 142 Rear-stage drive gear 143 Intermediate transmission gear 151 Front-side driven gear 1511 Driven shaft of the front-side driven gear 152 Rear-side driven gear 16 Claw wheel 17 Key 171 Washer 172 Spring 173a Engaging portion 18 One-way clutch mechanism 181 Coil spring 1811 Coil spring engaging portion 182 Drive shaft slit 183 Drive Shaft 184 Driven shaft

Claims (5)

  In the driving device in which the driving source and the driving force from the driving source are transmitted to the output unit via the transmission gear, the transmission gear is interlocked with each other, the front gear disposed in the front stage and the rear stage disposed in the rear stage. And the output portion includes one output portion to which a driving force is transmitted from the front gear and the other output portion to which a driving force is transmitted from the rear gear, and the rear gear is the front gear. A driving gear connected by a gear and a driven gear connected to the driving gear via a one-way clutch, and the rear gear includes a driving gear driven by the front gear and a one-way clutch connected to the driving gear. The driving force transmitted to the driving gear by forward rotation of the front gear is transmitted to the driven gear via a one-way clutch, and the one output unit and the other gear Output section Output, the driving device, characterized in that the driving force transmitted to the driving gear by the reverse rotation of the front gear is transmitted only to one output section is cut by the one-way clutch.   2. The drive device according to claim 1, further comprising a blocking member that enters a rotation locus of the driven gear by reverse rotation of the front gear and prevents rotation of the driven gear and the driving gear.   The blocking member is configured such that the center of rotation of the blocking member is coaxial with the front gear, and the vicinity of the rotation center of the blocking member is in contact with the front gear in the axial direction and can be rotated by friction. Is moved out of the rotation trajectory of the driven gear by forward rotation of the front gear, and enters the rotation trajectory of the driven gear by reverse rotation of the front gear to rotate the driven gear and the driving gear. The driving device according to claim 2, wherein blocking is performed.   The transmission gear has a planetary gear mechanism between the drive source and the front gear, and the planetary gear mechanism is a planetary gear support gear that rotatably supports a sun gear and planet gears meshed with the sun gear; An internal gear meshed with the planetary gear, and any one of the sun gear, the planetary gear support gear and the internal gear is used as an input gear to which the driving force of the drive source is input, and the input Any two of the sun gear, the planetary gear support gear, and the ring gear excluding the gears are respectively connected to one front gear and the other front gear that are formed in two stages on the rear side from the front gear. The drive device according to any one of claims 1 to 3. Each of the front-stage gears in which the rear stage side is formed in two lines from the front-stage gears and the rear-stage gears are arranged coaxially.

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