JP2017213665A - Driving machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve weight reduction of a gear case and thereby achieve weight reduction and downsizing of a driving machine.SOLUTION: A driving machine has: a planetary gear reduction mechanism 30 provided at a power transmission path between an electric motor and a piston; a gear case 50 which houses multiple gears including a ring gear 33 forming the planetary gear reduction mechanism 30; and a nose cover 40 including a second holding part 42 into which the gear case 50 is inserted. A first engagement part 43 is provided at the second holding part 42, an outer engagement part 53 is provided on an outer peripheral surface of the gear case 50, an inner engagement part 54 is provided on an inner peripheral surface of the gear case 50, and a second engagement part 33a is provided on an outer peripheral surface of the ring gear 33. The outer engagement part 53 and the first engagement part 43 are engaged with each other so as to overlap with each other in a longitudinal direction, and the inner engagement part 54 and the second engagement part 33a are engaged with each other so as to overlap with each other in the longitudinal direction.SELECTED DRAWING: Figure 6

Description

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

  The driving machine includes a piston accommodated in a cylinder so as to be reciprocable, 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 as the piston reciprocates. The driving machine further includes a supply mechanism that supplies a stopper to the moving path (injection path) of the driver blade. When the driver blade rises to a predetermined position as the piston moves from the bottom dead center to the top dead center, the supply mechanism supplies a stopper to the injection passage. Thereafter, when the driver blade descends as the piston moves from the top dead center to the bottom dead center, the stop waiting in the injection passage is struck by the driver blade. The hit stopper is driven out from an injection port which is an outlet of the injection passage, and is driven into a wood or a gypsum board.

  As 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 and moves 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 by the pressure of air compressed as the piston moves toward the top dead center.

  Since the piston moves to the top dead center side while compressing air, a large force is required to move the piston to the top dead center side. Therefore, a speed reduction mechanism that increases the torque by reducing the rotation speed of the electric motor is provided. For example, a planetary gear reduction mechanism is provided on a power transmission path for transmitting the output of the electric motor to the piston. Each gear constituting the planetary gear speed reduction mechanism is housed in a gear case provided in the housing of the driving machine, and an electric motor is disposed 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, the gear case is required to have sufficient strength and is required to be 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 is fixed to each other by a metal band (steel band) straddling the gear case and the motor housing (Patent Document 1).

JP 2014-069289 A

  The metal gear case is heavy, which contributes to the reduction in size and weight of the driving machine. In addition, 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 assembly steps.

  An object of the present invention is to reduce the weight of the gear case and to reduce the size and weight of the 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 accompanying movement of a piston. The driving machine is provided in an electric motor that is a driving source of the piston, a power transmission path between the electric motor and the piston, and houses a plurality of gears constituting a reduction mechanism and the plurality of gears. And a holding member including a first holding part into which the cylinder is inserted and a second holding part into which the gear case is inserted. A plurality of first engaging portions extending along the axial direction are provided in the second holding portion at intervals along the circumferential direction, and a plurality of first engaging portions extending along the axial direction are provided on the outer peripheral surface of the gear case. Outer engagement portions are provided at intervals along the circumferential direction, and a plurality of inner engagement 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 second engaging portions extending along the axial direction are provided at intervals along the circumferential direction on at least one outer peripheral surface of the plurality of gears. The outer engagement portion and the first engagement portion engage with each other so as to overlap each other in the longitudinal direction, and restrict relative rotation between the gear case and the holding member. The inner engagement portion and the second engagement portion are engaged with each other so as to overlap each other in the longitudinal direction, and the gear case and the gear on which the second engagement portion is provided are relative to each other. Regulate rotation. The outer engagement portion and the inner engagement portion are formed at the same position in the circumferential direction of the gear case.

  According to the present invention, the gear case can be reduced in weight, and the driving machine can be reduced in size and weight.

It is sectional drawing which shows the whole structure of a driving machine. It is an exploded view which shows the accommodation condition of the nose cover and 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, (b) is sectional drawing of a ring gear.

  Hereinafter, an example of an embodiment of a driving machine according to 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. 1 has a housing 2. The housing 2 includes a cylinder case 3, a motor case 4, and a handle 5. The cylinder case 3 contains a cylinder 10, and the motor case 4 contains an electric motor 22. The motor case 4 and the handle 5 extend substantially parallel to each other from the cylinder case 3, and the end of the motor case 4 and the 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, actually, another housing half 2a having substantially the same shape as the housing half 2a shown in the figure is prepared. .

  Refer to FIG. 1 again. A piston 11 is accommodated in the cylinder 10 so as to be able to reciprocate. The piston 11 reciprocates between the top dead center and the bottom dead center along the axial direction of the cylinder 10 inside the cylinder 10. In the cylinder 10, a piston chamber 12 whose volume increases or 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 the lower surface of the piston 11. The driver blade 20 is integral with the piston 11 and reciprocates together with the piston 11. Specifically, a nose portion 7 is provided at the tip 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 as the piston 11 reciprocates. In the following description, the reciprocating direction of the piston 11 and the driver blade 20 in FIG. That is, the vertical direction in FIG. 1 is defined as the vertical direction.

  A magazine 8 that houses a large number of fasteners is attached to the housing 2. The stoppers accommodated in the magazine 8 are supplied to the injection passage one by one by a supply mechanism provided in the magazine 8. The driver blade 20 strikes the heads of the stoppers that are sequentially supplied to the injection passage. The stopper hitting the head passes through the injection passage, is driven out from the injection port that 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 in the vicinity of the driver blade 20. The wheel 21 is formed integrally with a drive shaft 21 a that extends in a direction orthogonal to the central axis of the cylinder 10 and the driver blade 20. However, there is also an embodiment in which the separate wheel 21 and drive shaft 21a are fixed to each other. Further, a plurality of pins are attached to the wheel 21 at intervals along the circumferential direction, and 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 speed reduction mechanism 30 in the present embodiment is a planetary gear speed reduction mechanism. The electric motor 22 is operated by electric power supplied from the battery 23 attached to the connecting portion 6 of the housing 2. In addition, a controller 24 as a control unit is accommodated in the connection unit 6. The controller 24 is a microcomputer composed of a CPU, ROM, RAM, and the like, and controls the electric motor 22. The electric motor 22 is a brushless motor, and the controller 24 controls the motor current supplied to the electric motor 22 by turning ON / OFF the switching element of the drive circuit.

  Above the cylinder 10, a pressure accumulation container (chamber) 14 that forms a pressure accumulation chamber (gas chamber) 13 is provided, and the pressure accumulation chamber 13 communicates with the piston chamber 12. The piston chamber 12 and the pressure accumulating chamber 13 are preliminarily filled with high-pressure gas (compressed air in this embodiment). 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 is operated based on the control of the controller 24. When the electric motor 22 is actuated, the rotational driving force output from the electric motor 22 is transmitted to the wheel 21 via the speed reduction mechanism (planetary gear speed 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 are sequentially engaged, the driver blade 20 is gradually pushed up, and the piston 11 is moved from the bottom dead center side. Move toward the top dead center. That is, the driver blade 20 and the piston 11 are raised. After that, 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 moving direction of the driver blade 20 are engaged, the piston 11 reaches the top dead center. Thus, a power transmission path is provided between the electric motor 22 and the piston 11, and the planetary gear speed reduction mechanism 30 is provided in this power transmission path.

  In the process of moving (raising) the piston 11 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 of the compressed air (air pressure) in the piston chamber 12 and the pressure accumulating chamber 13 causes the piston 11 to move from the top dead center to the bottom dead center, and the driver blade 20 descends. To do.

  The nose portion 7 is provided with a push lever 7a. The push lever 7a is held so as to be movable in the vertical direction, and is always urged downward by a coil spring. The handle 5 is provided with a trigger 5a. The electric motor 22 operates in a state where 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 driving mode includes a “single 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 while the operation of the trigger 5a is maintained. The “continuous firing mode” in which the driving operation is sequentially performed by repeating the above.

  As shown in FIG. 2, a metal holding member 40 and a synthetic resin gear case 50 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 includes a first holding portion 41 and a second holding portion 42 that are substantially cylindrical. However, the nose cover 40 is an aluminum die-cast product, and the first holding part 41 and the second holding part 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 housed in the second holding portion 42 of the nose cover 40, and one end side 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 central axis of the first holding part 41 coincides with the central axis of the cylinder 10, and the central axis of the second holding part 42 coincides with the central axis of the drive shaft 21a. That is, the central axis (axial direction) of the first holding part 41 and the central axis (axial direction) of the second holding part 42 are orthogonal to each other. However, as shown in FIG. 2, the first holding part 41 is offset with respect to the second holding part 42, and the central axes of the first holding part 41 and the second holding part 42 do not intersect.

  As shown in FIGS. 2 and 3, the second holding portion 42 is provided with first engaging 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 engaging portions 43 are provided around the opening 44 at regular intervals along the opening 44. Further, a notch 45 is formed between each pair of first engaging portions 43 adjacent in the circumferential direction of the second holding portion 42. In other words, one first engagement portion 43 is formed on each side of each notch 45. That is, the first engaging portions 43 and the notches 45 are alternately provided 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 made of polyamide resin. A small diameter portion 50a having a relatively small outer diameter is formed on one end side in the axial direction of the gear case 50, and a large diameter portion 50b having a relatively large outer diameter is formed on the other end side in the axial direction. As a result, a step 52 that 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, there is a boundary (step 52) between the small diameter portion 50a and the large diameter portion 50b at substantially the center in the axial direction of the gear case 50.

  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 integrated with the nose cover 40. Specifically, the small diameter portion 50 a of the gear case 50 is inserted into 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 engaging portion 53 and the notch 45 abut against the end surface of the opening 44 (the end surface of each first engaging portion 43). That is, the insertion length of the gear case 50 with respect to the second holding portion 42 is equal to the entire length of the small diameter portion 50 a of the gear case 50. In other words, the insertion length of the gear case 50 with respect to 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 outer engagement portion 53 is an elongated protrusion extending in the axial direction of the gear case 50, and extends vertically across the step 52 to straddle 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 the longitudinal direction of each outer engagement portion 53 is formed in the corresponding notch 45. It is inserted. Specifically, a portion (tip portion 53 a) that protrudes toward the small diameter portion 50 a beyond the step 52 of each outer engagement portion 53 is inserted into the notch 45. As a result, the outer engagement portion 53 and the first engagement 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 is not rotatable with respect to the nose cover 40. Specifically, both side surfaces of the tip end portion 53 a of the outer engagement portion 53 are opposed to the side surfaces of the two first engagement portions 43 adjacent to both sides of the notch 45.

  On the other hand, a part (base end portion 53 b) of the outer engagement portion 53 that is not inserted into the notch 45 engages with the housing 2. As shown in FIG. 2, an engagement groove 4 a is formed on the inner surface of the motor case 4. It is desirable that at least one, preferably 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 the engagement of a part of the outer engagement portion 53 (tip portion 53 a) and the first engagement portion 43, and is attached to the housing 2 via the nose cover 40. Fixed. At the same time, the gear case 50 is fixed to the housing 2 (the motor case 4) by the engagement of the other part (base end portion 53b) of the outer engaging portion 53 and the engaging groove 4a.

  As shown in FIGS. 2 and 4, a plurality of inner engagement 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 inner engagement portion 54 is an elongated groove extending in the axial direction of the gear case 50.

  Further, as shown in FIG. 4A, the outer engagement portion 53 and the inner engagement portion 54 are formed at the same position in the circumferential direction of the gear case 50. That is, the inner engagement portion 54 is formed directly behind (below) the outer engagement portion 53. In other words, the outer engagement portion 53 is formed directly above the inner engagement 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 speed reduction mechanism 30 in the present embodiment is a multistage speed reduction mechanism including a plurality of ring gears 31, 32, 33. The ring gears 31, 32, 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. 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 drawing, a plurality of second engaging portions 33 a extending along the axial direction are provided on the outer peripheral surface of the ring gear 33 at intervals along the circumferential direction. Further, as shown in FIG. 6, a plurality of second engaging portions 31 a and 32 a extending along the axial direction are also spaced apart along the circumferential direction on the outer peripheral surfaces of the ring gears 31 and 32 other than the ring gear 33. Is provided.

  The second engaging portions 31a, 32a, 33a provided on the ring gears 31, 32, 33 are elongated projections extending in the axial direction of the ring gears 31, 32, 33, respectively. On the other hand, as described above, the inner engagement 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. And as FIG. 6 shows, each 2nd engaging part 31a, 32b, 33c is fitted to the corresponding inner side engaging part 54. As shown in FIG. That is, the second engaging portions 31a, 32a, and 33a that are elongated protrusions are fitted into the inner engaging portion 54 that is an elongated groove. As a result, the inner engagement portion 54 and the second engagement portions 31a, 32a, 33a engage with each other so as to overlap each other in the longitudinal direction, and the gear case 50 and the second engagement portion are provided. The relative rotation with the ring gears 31, 32, 33 is restricted. In other words, the ring gears 31, 32, 33 are not rotatable 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 engagement portions 31 a, 32 a, 33 a of the ring gears 31, 32, 33 and the inner engagement 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. Furthermore, the gear case 50 is made non-rotatable with respect to the nose cover 40 by the outer engagement portion 53 and the first engagement portion 43 that are engaged with each other so as to overlap each other. The overlapping direction of the outer engagement portion 53 and the first engagement portion 43 is a direction that intersects the direction of torque received by the gear case 50. Therefore, the torque received by the gear case 50 is effectively received by the nose cover 40. Thus, in this embodiment, the engagement direction 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 it is the synthetic resin gear case 50 whose intensity | strength is low compared with metal, it is neither twisted nor damaged by torque. Further, the gear case 50 is not moved by torque.

  Further, as shown in FIG. 6, the outer engagement portion 53 and the inner engagement 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 the engagement between the outer engagement portion 53 of the gear case 50 and the first engagement portion 43 of the nose cover 40. Located directly below the area. Further, the outer engagement portion 53 and the inner engagement portion 54 have a length that is ½ or more of the entire length of the gear case 50, and the outer engagement portion 53 extends around the entire length of the gear case 50. It is engaged with the member. Specifically, a part (front end portion 53a) of the outer engagement portion 53 is engaged with the nose cover 40, and the remaining part (base end portion 53b) is engaged with the housing 2 (motor case 4). Yes. Therefore, twisting and breakage of the gear case 50 due to torque can be prevented more reliably.

  In addition, the inner engagement portion 54 of the gear case 50 with which the ring gears 31, 32, 33 are engaged and the outer engagement portion 53 of the gear case 50 with which the nose cover 40 is engaged are in the circumferential direction (torque direction) of the gear case 50. In the same position. Thereby, 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, among the three ring gears 31, 32, 33, the largest torque acts on the ring gear 33 in the final stage. Therefore, the dimension of the ring gear 33 in the axial direction is larger than the dimension of the other ring gears 31 and 32 in the same direction. Accordingly, the entire length of the second engagement portion 33 a provided in the ring gear 33 is longer than the total length of the second engagement portions 31 a and 32 a provided in the other ring gears 31 and 32. That is, the fitting length between the second engaging portion 33 a and the inner engaging portion 54 is longer than the fitting length between the other second engaging portions 31 a and 32 a and the inner engaging portion 54. Furthermore, as described above, the substantially entire length of the second engagement portion 33 a 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 expanded, and the torque is dispersed.

  The present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the scope of the invention. For example, the speed reduction mechanism is not limited to the planetary gear speed reduction mechanism, and the number of stages is not limited to three. Further, 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 or the like can be adopted.

DESCRIPTION OF SYMBOLS 1 Driving machine 2 Housing 3 Cylinder case 4 Motor case 4a Engagement groove 5 Handle 6 Connection 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 Deceleration mechanism (planet (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 portion 42 second holding portion 43 first engaging portion 44 opening 50 gear case 50a small diameter portion 50b large diameter portion 52 step 53 outer engagement portion 53a distal end portion 53b proximal end portion 54 inner engagement portion

Claims (5)

A driving machine for driving a stopper into a material to be driven by pressure fluctuation in a cylinder accompanying movement of a piston,
An electric motor as a drive 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 that houses the plurality of gears;
A holding member comprising a first holding part into which the cylinder is inserted and a second holding part into which the gear case is inserted;
The second holding portion is provided with a plurality of first engaging portions extending along the axial direction 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,
A plurality of inner engaging portions extending along the axial direction are provided on the inner peripheral surface of the gear case at intervals along the circumferential direction,
A plurality of second engaging portions extending along the axial direction are provided at intervals along the circumferential direction on at least one outer peripheral surface of the plurality of gears,
The outer engagement portion and the first engagement portion engage with each other so as to overlap each other in the longitudinal direction, and restrict relative rotation between the gear case and the holding member,
The inner engagement portion and the second engagement portion are engaged with each other so as to overlap each other in the longitudinal direction, and the gear case and the gear on which the second engagement portion is provided are relative to each other. Regulate the rotation,
The outer engagement portion and the inner engagement portion are formed at the same position in the circumferential direction of the gear case.
Driving machine. A notch is formed between each pair of the first engaging portions adjacent 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 projection in the longitudinal direction as the outer engagement portion is inserted into the corresponding notch,
The driving machine according to claim 1. A groove as the inner engagement portion is formed on the inner peripheral surface of the gear case,
A projection as the second engagement portion is formed on the outer peripheral surface of the gear,
The protrusion as the second engaging portion is fitted in the corresponding groove,
The driving machine according to claim 1 or 2. The speed reduction mechanism is a planetary gear speed reduction mechanism;
The second engagement portion is provided on the outer peripheral surface of the ring gear constituting the planetary gear reduction mechanism.
The driving machine according to claim 3. The planetary gear reduction mechanism is a multistage reduction mechanism having a plurality of the ring gears,
The second engaging portion provided in each ring gear is fitted in the groove as the inner engaging portion,
The driving machine according to claim 4.

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