JP6665694B2 - Driving machine - Google Patents

Description

  The present invention relates to a driving machine for driving a fastener such as a nail or a pin into a material to be driven such as wood or gypsum board.

  The driving machine has a piston housed reciprocally in a cylinder, and a driver blade integrated with the piston. The piston reciprocates between the top dead center and the bottom dead center in the cylinder, and the driver blade reciprocates with the reciprocation of the piston. The driving machine further has a supply mechanism for supplying a stopper on the movement path (injection passage) of the driver blade. The supply mechanism supplies a stopper to the injection passage when the driver blade rises to a predetermined position as the piston moves from the bottom dead center to the top dead center. Thereafter, when the driver blade descends in accordance with the movement of the piston from the top dead center to the bottom dead center, a stop waiting in the injection passage is hit by the driver blade. The hitting tool is driven out of the injection port, which is the exit of the injection path, and is driven into wood, gypsum board, or the like.

  As a means for reciprocating the piston as described above, there is a driving machine using air pressure (gas spring). The piston in this type of driving machine is driven by an electric motor to move from the bottom dead center side to the top dead center side. The piston moves from the top dead center to the bottom dead center due to the pressure of the air compressed as the piston moves toward the top dead center.

  Since the piston moves toward the top dead center while compressing air, a large force is required to move the piston toward the top dead center. Therefore, a speed reduction mechanism for reducing the rotation speed of the electric motor to increase the torque is provided. For example, a planetary gear reduction mechanism is provided on a power transmission path that transmits the output of the electric motor to the piston. Each gear constituting the planetary gear reduction mechanism is housed in a gear case provided in a housing of the driving machine, and an electric motor is arranged adjacent to the gear case. The output shaft of the electric motor enters the gear case and is connected to the input gear of the planetary gear reduction mechanism.

  When torque is input to the planetary gear reduction mechanism, a reaction force acts on the ring gear. The reaction force acting on the ring gear is received by the gear case to which the ring gear is fixed. Therefore, it is required that the gear case has sufficient strength and that the gear case is firmly fixed.

  Therefore, in the prototype structure, a metal gear case was used, and the gear case was firmly fixed to the electric motor. For example, the gear case has been fixed to each other by a metal band (steel band) straddling the gear case and the motor housing (Patent Document 1).

JP-A-2014-069289

  The metal gear case is heavy, which is one of the factors that hinders the size and weight of the driving machine. Further, the structure in which the gear case and the electric motor are fixed to each other by the steel band causes an increase in the number of parts and an increase in the number of assembling steps.

  An object of the present invention is to reduce the weight of a gear case and reduce the size and weight of a driving machine.

  The driving machine according to the present invention is a driving machine that drives a stopper into a material to be driven by pressure fluctuation in a cylinder caused by movement of a piston. The driving machine houses an electric motor that is a driving source of the piston, a plurality of gears that are provided in a power transmission path between the electric motor and the piston, and that constitute a reduction mechanism, and the plurality of gears. And a holding member including a first holding portion into which the cylinder is inserted and a second holding portion into which the gear case is inserted. A plurality of first engagement portions extending along the axial direction are provided at the second holding portion at intervals along the circumferential direction, and a plurality of first engagement portions extending along the axial direction are provided on the outer peripheral surface of the gear case. Outer engaging portions are provided at intervals along the circumferential direction, and a plurality of inner engaging portions extending along the axial direction are provided at an inner circumferential surface of the gear case at intervals along the circumferential direction. A plurality of second engaging portions extending along the axial direction are provided on at least one outer peripheral surface of the plurality of gears at intervals along the circumferential direction. The outer engaging portion and the first engaging portion are engaged with each other so as to overlap with each other in the respective longitudinal directions, and regulate relative rotation between the gear case and the holding member. The inner engaging portion and the second engaging portion are engaged with each other so as to overlap with each other in the respective longitudinal directions, and the relative position between the gear case and the gear provided with the second engaging portion. Regulate rotation. The outer engaging portion and the inner engaging portion are formed at the same position in a circumferential direction of the gear case.

  ADVANTAGE OF THE INVENTION According to this invention, weight reduction of a gear case is implement | achieved, and the compaction and weight reduction of a driving machine are achieved.

It is sectional drawing which shows the whole structure of a driver. FIG. 3 is an exploded view showing a state of housing a nose cover and a gear case in a housing. It is a top view of a nose cover. (A) is a front view of a gear case, (b) is a side view of a gear case. It is an assembly drawing of a gear case and a nose cover. It is sectional drawing which shows the accommodation condition of the gear in a gear case. (A) is a front view of a ring gear, and (b) is a cross-sectional view of the ring gear.

  Hereinafter, an example of an embodiment of a driving machine of the present invention will be described in detail with reference to the drawings. The driving machine according to the present embodiment is a driving machine that drives a stopper into a material to be driven by pressure fluctuation in a cylinder accompanying movement of a piston. In the drawings referred to in the following description, the same or substantially the same members are denoted by the same reference numerals.

  The driving machine 1 shown in FIG. The housing 2 includes a cylinder case 3, a motor case 4, and a handle 5. The cylinder case 3 houses a cylinder 10, and the motor case 4 houses an electric motor 22. The motor case 4 and the handle 5 extend substantially parallel to each other from the cylinder case 3, and an end of the motor case 4 and an end of the handle 5 are connected to each other by a connecting portion 6. The housing 2 has two housing halves 2a (FIG. 2) formed of a synthetic resin such as nylon or polycarbonate, and the housing 2 is assembled by abutting the two housing halves 2a. Although only one housing half 2a is shown in FIG. 2, another housing half 2a having substantially the same shape as the illustrated housing half 2a is actually prepared. .

  FIG. 1 is referred to again. A piston 11 is accommodated in the cylinder 10 so as to be able to reciprocate. The piston 11 reciprocates inside the cylinder 10 between the top dead center and the bottom dead center along the axial direction of the cylinder 10. In the cylinder 10, a piston chamber 12 whose volume increases and decreases as the piston 11 reciprocates is defined by the inner peripheral surface of the cylinder 10 and the upper surface of the piston 11. The illustrated piston 11 is located at the top dead center, and the volume of the piston chamber 12 is minimized.

  A driver blade 20 is connected to a lower surface of the piston 11. The driver blade 20 is integral with the piston 11 and reciprocates with the piston 11. Specifically, a nose portion 7 is provided at the end of the cylinder case 3, and an injection passage is provided inside the nose portion 7. The driver blade 20 reciprocates in the injection passage with the reciprocation of the piston 11. In the following description, the reciprocating direction of the piston 11 and the driver blade 20 in FIG. 1 is defined as a vertical direction. That is, the vertical direction in FIG. 1 is defined as the vertical direction.

  A magazine 8 for accommodating a large number of fasteners is attached to the housing 2. The stoppers housed in the magazine 8 are supplied one by one to the injection passage by a supply mechanism provided in the magazine 8. The driver blade 20 hits the head of the stopper sequentially supplied to the injection passage. The fastener whose head has been hit passes through the injection passage, is ejected from the injection outlet, which is the exit of the injection passage, and is driven into a material to be driven such as wood or gypsum board.

  A wheel 21 is provided near the driver blade 20. The wheel 21 is formed integrally with a drive shaft 21 a extending in a direction orthogonal to the central axis of the cylinder 10 and the driver blade 20. However, in some embodiments, the separate wheel 21 and the drive shaft 21a are fixed to each other. A plurality of pins are attached to the wheel 21 at intervals along the circumferential direction, while the driver blade 20 is provided with a plurality of racks along the axial direction.

  The motor case 4 houses an electric motor 22 that is a drive source of the wheel 21, and an output shaft 22 a of the electric motor 22 is connected to a drive shaft 21 a of the wheel 21 via a speed reduction mechanism 30. The reduction mechanism 30 in the present embodiment is a planetary gear reduction mechanism. The electric motor 22 is operated by electric power supplied from a battery 23 mounted on the connecting portion 6 of the housing 2. Further, a controller 24 as a control unit is housed inside the connection unit 6. The controller 24 is a microcomputer including a CPU, a ROM, a RAM, and the like, and controls the electric motor 22. The electric motor 22 is a brushless motor, and the controller 24 controls a motor current supplied to the electric motor 22 by turning on / off a switching element of a drive circuit.

  Above the cylinder 10, a pressure accumulator (chamber) 14 that forms a pressure accumulator (gas chamber) 13 is provided, and the pressure accumulator 13 communicates with the piston chamber 12. The piston chamber 12 and the pressure accumulating chamber 13 are filled in advance with a high-pressure gas (in this embodiment, compressed air). When the piston 11 located at a position lower than the top dead center is moved to the position shown in FIG. 1 (top dead center), the electric motor 22 operates based on the control of the controller 24. When the electric motor 22 operates, the rotational driving force output from the electric motor 22 is transmitted to the wheel 21 via the reduction mechanism (planetary gear reduction mechanism) 30, and the wheel 21 rotates in a predetermined direction. When the wheel 21 rotates, a plurality of pins provided on the wheel 21 and a plurality of racks provided on the driver blade 20 sequentially engage, the driver blade 20 is gradually pushed up, and the piston 11 is moved from the bottom dead center side. Move toward top dead center. That is, the driver blade 20 and the piston 11 rise. Thereafter, when the wheel 21 rotates until the pin located on the most downstream side in the rotation direction of the wheel 21 and the rack located on the lowermost side in the movement direction of the driver blade 20 are engaged, the piston 11 reaches the top dead center. As described above, the power transmission path is provided between the electric motor 22 and the piston 11, and the planetary gear reduction mechanism 30 is provided in this power transmission path.

  As the piston 11 moves (ups) as described above, the air in the piston chamber 12 is sent into the pressure accumulating chamber 13 and compressed. Thereafter, when the engagement between the pin and the rack is released, the pressure (air pressure) of the compressed air in the piston chamber 12 and the pressure accumulation chamber 13 causes the piston 11 to move from the top dead center to the bottom dead center, and the driver blade 20 descends. I do.

  The nose portion 7 is provided with a push lever 7a. The push lever 7a is held movably in the up-down direction, and is constantly urged downward by a coil spring. The handle 5 is provided with a trigger 5a. When the push lever 7a is pressed against the driven member, moves upward against the bias of the coil spring, and the trigger 5a is operated, the electric motor 22 operates. The driving mode includes a “single-shot mode” in which the driving operation is performed only when the trigger 5a is operated after the pressing operation of the push lever 7a, and a pressing operation of the push lever 7a in a state where the operation of the trigger 5a is maintained. "Repeating mode" in which the driving operation is sequentially performed by repeating the above operation.

  As shown in FIG. 2, a holding member 40 made of metal and a gear case 50 made of synthetic resin are provided in the housing 2. In the following description, the holding member 40 may be referred to as a “nose cover 40”.

  As shown in FIGS. 2 and 3, the nose cover 40 has a substantially cylindrical first holding portion 41 and a second holding portion 42. However, the nose cover 40 is an aluminum die-cast product, and the first holding portion 41 and the second holding portion 42 are integrally formed.

  As shown in FIG. 1, a part (lower part) of the cylinder 10 is inserted into the first holding part 41 of the nose cover 40. That is, the nose cover 40 holds the cylinder 10 at a predetermined position in the cylinder case 3 in cooperation with a rib or the like formed on the inner surface of the cylinder case 3. The wheel 21 is accommodated in the second holding portion 42 of the nose cover 40, and one end of the drive shaft 21 a of the wheel 21 is rotatably supported by a bearing provided in the second holding portion 42. ing.

  Here, the center axis of the first holding part 41 matches the center axis of the cylinder 10, and the center axis of the second holding part 42 matches the center axis of the drive shaft 21a. That is, the central axis (axial direction) of the first holding unit 41 is orthogonal to the central axis (axial direction) of the second holding unit 42. However, as shown in FIG. 2, the first holding portion 41 is offset with respect to the second holding portion 42, and the central axes of the first holding portion 41 and the second holding portion 42 do not intersect.

  As shown in FIGS. 2 and 3, the second holding portion 42 is provided with first engagement portions 43 extending in the axial direction at intervals along the circumferential direction. As shown in FIG. 2, an opening 44 into which the gear case 50 is inserted is provided at one end of the second holding portion 42. The plurality of first engagement portions 43 are provided around the opening 44 at regular intervals along the opening 44. A notch 45 is formed between each pair of first engaging portions 43 adjacent to each other in the circumferential direction of the second holding portion 42. In other words, one first engaging portion 43 is formed on each side of each notch 45. That is, the first engagement portions 43 and the notches 45 are provided alternately around the opening 44 of the second holding portion 42.

  As shown in FIGS. 2 and 4, the gear case 50 has a substantially cylindrical appearance as a whole. The gear case 50 in the present embodiment is formed of a polyamide resin. A small-diameter portion 50a having a relatively small outer diameter is formed at one axial end of the gear case 50, and a large-diameter portion 50b having a relatively large outer diameter is formed at the other axial end. As a result, a step 52, which is a boundary between the small diameter portion 50a and the large diameter portion 50b, exists on the outer peripheral surface of the gear case 50. In the present embodiment, a boundary (step 52) between the small diameter portion 50a and the large diameter portion 50b exists substantially at the center of the gear case 50 in the axial direction.

  As shown in FIGS. 2 and 5, a part of the gear case 50 is inserted into the second holding portion 42 of the nose cover 40 and is integrated with the nose cover 40. Specifically, the small diameter portion 50 a of the gear case 50 is inserted into the inside of the second holding portion 42 from the opening 44 of the second holding portion 42. The small diameter portion 50a is inserted into the second holding portion 42 until the end surface of the outer engagement portion 53 and the notch 45 hit the end surface of the opening portion 44 (the end surface of each first engagement portion 43). That is, the insertion length of the gear case 50 into the second holding portion 42 matches the entire length of the small diameter portion 50a of the gear case 50. In other words, the insertion length of the gear case 50 into the second holding portion 42 is defined by the position of the step 52.

  As shown in FIG. 4, a plurality of outer engaging portions 53 extending in the axial direction are provided on the outer peripheral surface of the gear case 50 at intervals along the circumferential direction. Each of the outer engagement portions 53 is an elongated protrusion extending in the axial direction of the gear case 50, and extends across the step 52 and straddles the large-diameter portion 50b and the small-diameter portion 50a.

  As shown in FIG. 5, when the small diameter portion 50 a (FIG. 4) of the gear case 50 is inserted into the second holding portion 42, a part of each of the outer engagement portions 53 in the longitudinal direction is formed into the corresponding notch 45. Will be posted. Specifically, portions (tip portions 53a) of the respective outer engagement portions 53 projecting toward the small-diameter portion 50a beyond the step 52 are inserted into the notches 45. As a result, the outer engaging portion 53 and the first engaging portion 43 engage with each other so as to overlap each other in the longitudinal direction, and the relative rotation between the gear case 50 and the nose cover 40 is restricted. In other words, the gear case 50 cannot be rotated with respect to the nose cover 40. Specifically, both side surfaces of the distal end portion 53a of the outer engaging portion 53 face the side surfaces of the two first engaging portions 43 on both sides of the notch 45, respectively.

  On the other hand, a part of the outer engaging portion 53 that is not inserted into the notch 45 (the base end portion 53b) engages with the housing 2. As shown in FIG. 2, an engagement groove 4a is formed on the inner surface of the motor case 4. It is desirable that at least one, desirably a plurality of engagement grooves 4a be formed. When the assembled nose cover 40 and gear case 50 are accommodated in the motor case 4, the base end portion 53b (FIG. 5) of the outer engagement portion 53 engages with the engagement groove 4a.

  As described above, the gear case 50 is fixed to the nose cover 40 by engagement of a part (the distal end portion 53 a) of the outer engagement portion 53 and the first engagement portion 43, and is fixed to the housing 2 via the nose cover 40. Fixed. At the same time, the gear case 50 is fixed to the housing 2 (motor case 4) by engagement of another part (the base end part 53b) of the outer engagement part 53 with the engagement groove 4a.

  As shown in FIGS. 2 and 4, a plurality of inner engaging portions 54 extending along the axial direction are provided on the inner peripheral surface of the gear case 50 at intervals along the circumferential direction. Each of the inner engaging portions 54 is an elongated groove extending in the axial direction of the gear case 50.

  Further, as shown in FIG. 4A, the outer engaging portion 53 and the inner engaging portion 54 are formed at the same position in the circumferential direction of the gear case 50. That is, the inner engaging portion 54 is formed directly behind (directly below) the outer engaging portion 53. In other words, the outer engaging portion 53 is formed right above the inner engaging portion 54.

  As shown in FIG. 6, a plurality of gears constituting the planetary gear reduction mechanism 30 are accommodated in the gear case 50. The planetary gear reduction mechanism 30 in the present embodiment is a multi-stage reduction mechanism including a plurality of ring gears 31, 32, and 33. The ring gears 31, 32, and 33 are arranged in a line in this order along the power transmission direction, and are fixed to the gear case 50 so as not to rotate. Note that a lock ring 34 for preventing reverse rotation is disposed between the ring gear 31 and the ring gear 32, and a spacer 35 is disposed between the ring gear 32 and the ring gear 33.

  FIG. 7A is a front view of the final stage ring gear 33, and FIG. 7B is a cross-sectional view of the final stage ring gear 33. As shown in the figure, a plurality of second engaging portions 33a extending along the axial direction are provided on the outer peripheral surface of the ring gear 33 at intervals along the circumferential direction. As shown in FIG. 6, a plurality of second engaging portions 31a and 32a extending along the axial direction are also provided on the outer peripheral surfaces of the ring gears 31 and 32 other than the ring gear 33 at intervals along the circumferential direction. Is provided.

  The second engagement portions 31a, 32a, 33a provided on the respective ring gears 31, 32, 33 are elongated projections extending in the axial direction of the respective ring gears 31, 32, 33. On the other hand, as described above, the inner engaging portion 54 provided on the inner peripheral surface of the gear case 50 is an elongated groove extending in the axial direction of the gear case 50. Then, as shown in FIG. 6, each of the second engaging portions 31a, 32b, 33c is fitted to the corresponding inner engaging portion 54. That is, the second engaging portions 31a, 32a, and 33a, which are elongated projections, are fitted to the inner engaging portions 54, which are elongated grooves. As a result, the inner engaging portion 54 and the second engaging portions 31a, 32a, 33a are engaged with each other so as to overlap each other in the longitudinal direction, and the gear case 50 and the second engaging portion are provided. Relative rotation with respect to the ring gears 31, 32, 33 is restricted. In other words, the ring gears 31, 32, and 33 cannot rotate with respect to the gear case 50. Therefore, the torque (reaction force) acting on the ring gears 31, 32, 33 is received by the gear case 50.

  Here, the overlapping direction of the second engaging portions 31a, 32a, 33a of the ring gears 31, 32, 33 and the inner engaging portion 54 of the gear case 50 intersects the direction of the torque acting on the ring gears 31, 32, 33. Direction. Therefore, the torque acting on the ring gears 31, 32, 33 is effectively received by the gear case 50. Further, the gear case 50 cannot be rotated with respect to the nose cover 40 by the outer engaging portion 53 and the first engaging portion 43 which are engaged with each other so as to overlap with each other. The overlapping direction of the outer engaging portion 53 and the first engaging portion 43 is a direction that intersects with the direction of the torque received by the gear case 50. Therefore, the torque received by the gear case 50 is effectively received by the nose cover 40. As described above, in the present embodiment, the direction of engagement of the plurality of engagement portions in the gear case 50 and the direction of torque acting on each portion intersect. For this reason, even if the gear case 50 is made of a synthetic resin having a lower strength than that of a metal case, the gear case 50 is not twisted or damaged by the torque. Further, the gear case 50 does not move due to the torque.

  Further, as shown in FIG. 6, the outer engaging portion 53 and the inner engaging portion 54 of the gear case 50 have substantially the same length. Therefore, the engagement region between the inner engagement portion 54 of the gear case 50 and the second engagement portion 33 a of the ring gear 33 is determined by the engagement between the outer engagement portion 53 of the gear case 50 and the first engagement portion 43 of the nose cover 40. It is located just below the area. Further, the outer engaging portion 53 and the inner engaging portion 54 have a length equal to or more than 全長 of the entire length of the gear case 50, and the outer engaging portion 53 extends around the entire length of the gear case 50. Engaged with the member. Specifically, part of the outer engaging portion 53 (the distal end portion 53a) is engaged with the nose cover 40, and the remaining part (the proximal end portion 53b) is engaged with the housing 2 (the motor case 4). I have. Therefore, the torsion and breakage of the gear case 50 due to the torque are more reliably prevented.

  In addition, the inner engaging portion 54 of the gear case 50 with which the ring gears 31, 32, 33 engage and the outer engaging portion 53 of the gear case 50 with which the nose cover 40 engages are formed in the circumferential direction of the gear case 50 (the direction of torque). In the same position. Thus, the torque acting on the ring gears 31, 32, 33 is more effectively received by the gear case 50, and the torque received by the gear case 50 is more effectively received by the nose cover 40.

  Here, of the three ring gears 31, 32, 33, the largest torque acts on the ring gear 33 at the last stage. Therefore, the axial dimension of the ring gear 33 is made larger than the axial dimensions of the other ring gears 31 and 32. Accordingly, the entire length of the second engagement portion 33a provided on the ring gear 33 is longer than the entire length of the second engagement portions 31a and 32a provided on the other ring gears 31 and 32. That is, the fitting length between the second engaging portion 33a and the inner engaging portion 54 is longer than the fitting length between the other second engaging portions 31a and 32a and the inner engaging portion 54. Further, as described above, the substantially entire length of the second engagement portion 33a is located directly below the engagement region between the outer engagement portion 53 and the first engagement portion 43. As a result, the ring gear 33 on which the largest torque acts is more firmly fixed to the gear case 50. Further, the pressure receiving area of the gear case 50 with respect to the ring gear 33 is increased, and the torque is dispersed.

  The present invention is not limited to the above embodiment, but can be variously modified without departing from the gist thereof. For example, the reduction mechanism is not limited to the planetary gear reduction mechanism, and the number of stages is not limited to three. In addition, the metal material that forms the nose cover is not limited to aluminum, and the resin material that forms the gear case is not limited to polyamide resin, and any material including a metal material can be used.

DESCRIPTION OF SYMBOLS 1 Driving machine 2 Housing 3 Cylinder case 4 Motor case 4a Engagement groove 5 Handle 6 Connecting part 7 Nose part 8 Magazine 10 Cylinder 11 Piston 12 Piston chamber 20 Driver blade 21 Wheel 22 Electric motor 23 Battery 24 Controller 30 Reduction mechanism (planetary) (Gear reduction mechanism)
31, 32, 33 Ring gears 31a, 32a, 33a Second engaging portion 34 Lock ring 35 Spacer 40 Holding member (nose cover)
41 First holding part 42 Second holding part 43 First engaging part 44 Opening 50 Gear case 50a Small diameter part 50b Large diameter part 52 Step 53 Outer engaging part 53a Tip part 53b Base end part 54 Inner engaging part

Claims (5)

A driving machine for driving a stop into a material to be driven by pressure fluctuation in a cylinder accompanying movement of a piston,
An electric motor that is a driving source of the piston;
A plurality of gears provided in a power transmission path between the electric motor and the piston, and constituting a reduction mechanism,
A gear case accommodating the plurality of gears;
A holding member including a first holding portion into which the cylinder is inserted and a second holding portion into which the gear case is inserted,
A plurality of first engaging portions extending along the axial direction are provided on the second holding portion at intervals along the circumferential direction,
On the outer peripheral surface of the gear case, a plurality of outer engaging portions extending along the axial direction are provided at intervals along the circumferential direction,
On the inner peripheral surface of the gear case, a plurality of inner engaging portions extending along the axial direction are provided at intervals along the circumferential direction,
A plurality of second engagement portions extending along the axial direction are provided on at least one outer peripheral surface of the plurality of gears at intervals along the circumferential direction,
The outer engagement portion and the first engagement portion are engaged with each other so as to overlap each other in the respective longitudinal directions, and regulate relative rotation between the gear case and the holding member,
The inner engaging portion and the second engaging portion are engaged with each other so as to overlap each other in the respective longitudinal directions, and a relative position between the gear case and the gear provided with the second engaging portion is provided. Regulate the rotation,
The outer engagement portion and the inner engagement portion are formed at the same position in a circumferential direction of the gear case.
Driving machine. Notches are respectively formed between the first engaging portions of each set adjacent to each other in the circumferential direction of the second holding portion,
A projection as the outer engagement portion is formed on the outer peripheral surface of the gear case,
A part of the protrusion as the outer engagement portion in the longitudinal direction is inserted into the corresponding notch,
The driving machine according to claim 1. A groove is formed on the inner peripheral surface of the gear case as the inner engaging portion,
A projection is formed on the outer peripheral surface of the gear as the second engagement portion,
The protrusion as the second engagement portion is fitted in the corresponding groove.
The driving machine according to claim 1 or 2. The reduction mechanism is a planetary gear reduction mechanism,
The second engagement portion is provided on an outer peripheral surface of a ring gear constituting the planetary gear reduction mechanism,
The driving machine according to claim 3. The planetary gear reduction mechanism is a multi-stage reduction mechanism having a plurality of the ring gears,
The second engagement portion provided on each of the ring gears is fitted in the groove as the inner engagement portion,
The driving machine according to claim 4.

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