WO2007086127A1

WO2007086127A1 - Rotation output device

Info

Publication number: WO2007086127A1
Application number: PCT/JP2006/301245
Authority: WO
Inventors: Daijiro Nakamura
Original assignee: Muratechnology Co., Ltd.
Priority date: 2006-01-26
Filing date: 2006-01-26
Publication date: 2007-08-02

Abstract

A lock mechanism capable of securely locking an output shaft when the output shaft is rotated by the user after an input shaft is stopped from rotating and holding the released state of the output shaft during the rotation and generally reduced in size. A rotation output device (10) comprises a speed reduction/rotation transmission mechanism reducing the rotational speed of a spindle (3) relative to a lock ring (33) imparting a force in the reverse rotating direction to a float gear (34) and transmitting the reduced speed to the float gear (34). The lock mechanism guiding the float gear (34) to the radially outer side by the rotation of the spindle (3) comprises a locking groove (37c) transmitting the difference in speed of the spindle (3) caused by the speed reduction/rotation transmission mechanism to the float gear (34) engagement and fixing of which is released on the radially inner side and coil springs (35) biasing the float gear (34) to which the difference in speed is transmitted through the locking groove (37c) to the radial outer side.

Description

Specification

Rotation output device

Technical field

[0001] The present invention relates to a rotation output device capable of locking an output shaft of an electric tool such as an electric screwdriver after the motor is controlled to stop and the output shaft is stopped.

Background art

Conventionally, the electric power tool of the above-described example has been known that has a function of locking the output shaft (spindle) when the motor is controlled to stop (see Patent Document 1).

[0003] The lock mechanism described in Patent Document 1 provides a free angle between the output shaft and the input shaft, and is biased outward (in the locking direction) toward the output shaft, thereby fixing the fixing member. A lock mechanism is configured by providing a lock plate that engages and locks and a holding plate that restrains the position of the lock plate by a guide groove.

[0004] When the input shaft rotates (drives), this lock mechanism is free from the output shaft being locked because the holding plate restrains the lock plate in the radially inward position. When the rotating force motor stops and the input shaft stops, the output shaft rotates by the play angle due to inertia, so that the lock plate linked to the input shaft moves through the guide groove of the holding plate. By moving in the radially outward direction, the output shaft is automatically locked.

[0005] Thus, according to the lock mechanism of Patent Document 1, the output shaft is immediately locked using the inertia when the motor is stopped, so that after the stop, the user performs a rotation operation for the play angle. There is no need, and workability is extremely improved.

However, the locking mechanism using the inertia of Patent Document 1 has the following problems.

This is a problem that when the motor stops rotating at a low speed, the “rotation due to inertia” does not occur sufficiently and the automatic lock is not activated.

[0007] In this case, when the user rotates the output shaft in the same direction as the previous rotation direction, the output shaft is rotated in the same direction as the "rotation by inertia". Lock However, when the output shaft is rotated in the opposite direction, the input shaft also rotates together, so there is no relative displacement between the lock plate and the input shaft, and there is a problem that the lock is not applied at all. Arise.

[0008] Thus, unless the output shaft is locked, the function as a locking mechanism cannot be achieved. In addition, since there is no lock, the user has to turn the output shaft under the load of stopping the motor for a long period of time. Arise.

[0009] In order to solve this problem, Patent Document 1 adds a new lock operation mechanism using a planetary gear set, so that the lock plate is always used regardless of which direction the output shaft is rotated. The output shaft is configured so that relative displacement occurs between the input shaft and the output shaft is locked.

[0010] However, when such a lock operation mechanism is newly added, a complicated mechanism called a planetary gear set is required separately, which may deteriorate the reliability and durability of the lock mechanism itself. In addition, the installation space for such a lock operating mechanism is newly required, and there is a problem that the entire lock mechanism cannot be configured compactly.

[0011] Further, according to such a locking mechanism, since the holding plate restrains the locking plate in the radially inward position in the released state, the output shaft is not locked and is freely locked during normal rotation. For example, if unevenness occurs in the rotation of the motor due to insufficient power supply, etc., the inertia force is acting on the output shaft, so the lock plate is fixed to the output shaft via the holding plate. There was a risk that the output shaft would be inadvertently locked due to relative displacement between the input shaft and the input shaft.

[0012] In response to such a problem, the prior application (PCTZJP2005Z015046) has a restriction plate that restricts the movement of the position of the lock plate interposed between the lock plate and the fixing member, and the restriction plate is attached to the lock plate. In this way, the lock plate always rotates in the direction opposite to the rotation direction due to the friction between the restriction plate and the fixed member during rotation. A force is applied to suppress rotation due to inertial force.

[0013] Therefore, for example, when the motor rotates due to insufficient supply power, etc. Even when an inertial force is applied to the force shaft, the lock plate that is rotationally fixed to the output shaft via the holding plate is regulated by the force in the reverse rotation direction. This prevents relative displacement and prevents the output shaft from being locked inadvertently.

[0014] Elder force When such a restriction plate is newly added, a separate restriction plate is required in addition to the complicated mechanism of the planetary gear set that constitutes the relative rotation means, and the reliability, durability, etc. of the lock mechanism itself are required. There is a risk of worsening. In addition, it took time and effort to incorporate these new regulatory plates.

[0015] Further, since the restriction plate restricts the movement of the position of the lock plate by friction with the fixed member, when used for a long time, at least one of the restriction plate and the fixed member is worn by friction, thereby reducing durability. There was a concern.

Patent Document 1: Japanese Patent Laid-Open No. 11 37187

Disclosure of the invention

Problems to be solved by the invention

Therefore, according to the present invention, after the rotation of the input shaft is stopped, the output shaft by the user is securely locked by the rotation of the output shaft, and the released state can be reliably maintained during the rotation. An object of the present invention is to provide a rotation output device including a lock mechanism that can be compactly configured as a whole.

Means for solving the problem

[0018] A rotation output device according to the present invention is provided on a rotation input body for inputting a rotation driving force, and on the same axis as the rotation input body, and is driven from the rotation input body with a predetermined play angle. A rotation output body that receives a force and outputs a rotational force; a fixed member that is disposed on the outer periphery of the rotation output body and fixed in rotation; and rotates integrally with the rotation output body, and moves to a radially outward side. A movable lock plate that engages and fixes to the fixed member, a biasing body that biases the movable lock plate radially outward, and a counter-rotating force that applies a force in the reverse rotation direction to the movable lock plate. Providing means, and the anti-rotational force applying means is provided with a guiding portion for guiding the movement of the movement lock plate to the radially outward side, and the anti-rotational force applying means is provided on the rotation output body with respect to the fixed member. It comprises a reduced rotation transmission mechanism that decelerates rotation and transmits it to the moving lock plate, By rotating the rotary input body from the rotary input body side, the movable lock plate is guided inward and fixed to the radial inner side. A release mechanism that releases the engagement and fixation with the fixed member is provided, and the lock mechanism that guides the movable lock plate on the radially inner side to the radially outer side by the rotation of the rotation output physical force is fixed on the radially inner side. The guide portion that transmits the differential with the rotation output body generated by the deceleration rotation transmission mechanism to the movable lock plate that is released from the engagement and fixation with the member, and the differential is transmitted via the guide portion. It is comprised with the said urging | biasing body which urges | biases the transmitted said movement lock plate to the diameter outward side.

[0019] According to the configuration described above, the movement lock plate is automatically guided radially inward by the rotation from the rotation input body side for inputting the rotational driving force, and the engagement and fixation with the fixing member are released and released. It can be in a state.

In addition, the rotation output body generated by the reduction rotation transmission mechanism on the moving lock plate whose engagement with the fixing member is released on the radially inner side by rotation from the rotation output body. The urging body that urges the movable lock plate to which the differential is transmitted via the guide portion to the radially outward side moves the movable lock plate to the radially outward side. Thus, a locked state in which the fixing member is engaged and fixed can be obtained.

[0020] Further, a decelerating rotation transmission mechanism that applies a counter-rotation force applying unit that applies a force in a reverse rotation direction to the moving lock plate, and transmits the rotation output body to the moving lock plate by decelerating the rotation of the rotation output body with respect to the fixed member. And the guide portion transmits to the movable lock plate a differential with respect to the rotation output body generated by the reduced rotation transmission mechanism to the movable lock plate. It is given to the movable lock plate. Therefore, during rotation, the movable lock plate guided to the radially inner side by the release mechanism and released from the engagement with the fixing member can be reliably maintained in the radially inner released state.

In one embodiment of the present invention, the reduced-rotation transmission mechanism is fixed to the rotation output body in parallel with the fixed plate in a direction perpendicular to the axis fixed to the fixed member and parallel to the fixed plate. And a rolling element that rolls between the rotating plate and the fixed plate while being in contact with the opposing surfaces, and a rolling element holding plate that holds the rolling element in a rollable manner. The guide part is arranged on a rolling element holding plate.

[0022] The fixed plate and the rotating plate include a plate-like body formed in a substantially circular shape.

The rolling element includes a spherical ball or a roller. Holding the rolling element in a rollable manner includes holding the rolling element by loose fitting or a shaft support.

[0023] According to the above configuration, since the rolling element is sandwiched between the rotating plate and the fixed plate in the reduced rotation transmission mechanism, the rolling element transmitted with the rotation of the rotating plate rolls on the fixed plate. The rotor rotates relative to the rotating plate together with the rolling element holding plate. At this time, the rolling element holding plate transmitted from the rolling element rolling on the fixed plate rotates at half the rotational speed of the rotating plate. Therefore, when viewed from the rotating output body that rotates and fixes the rotating plate, the rolling element holding plate rotates at a speed that is half the direction opposite to the rotating direction of the rotating output body.

[0024] Therefore, the movement lock plate is transmitted with a differential with respect to the rotation output body generated by the reduction rotation transmission mechanism via the guide portion provided on the rolling element holding plate, and is It can be in a locked state in which it is reliably moved outward and engaged with and fixed to the fixing member.

[0025] In addition, due to the above-described operation of the reduction rotation transmission mechanism, the movement lock plate rotates in the direction opposite to the rotation direction with respect to the rotation output body via the guide provided on the rolling element holding plate during rotation of the rotation output body. Therefore, the movable lock plate, which has been released from engagement with the fixing member, can be more reliably maintained in the released state on the radially inner side.

In one embodiment of the present invention, a plurality of rolling elements are provided in the circumferential direction, and the plurality of rolling elements are held by a rolling element holding plate so as to rotate integrally. According to the above configuration, the plurality of rolling elements that have rolled on the fixed plate by the rotation of the rotating plate can transmit the rotation at half the rotational speed of the rotating plate to the rolling member holding plate. Therefore, the load on the rolling element that transmits the rotation of the rotating plate to the rolling element holding plate is reduced. In addition, since the rolling element is in contact with both the rotating plate and the fixed plate, the rotation of the rotating plate is transmitted. Therefore, by arranging a plurality of rolling elements, the number of contact points increases, and the rotating plate is reliably connected. Can transmit the rotation of

[0027] Further, according to one embodiment of the present invention, the rolling element is formed of a sphere.

According to the above configuration, the strength due to the shape of the rolling elements can be improved, and a durable reduced rotation transmission mechanism can be configured. [0028] In one embodiment of the present invention, the movable lock plate includes an engaging convex portion, the guiding portion is configured by a guiding groove with which the engaging convex portion is engaged, and the release mechanism is These are constituted by release grooves with which the engaging projections engage.

According to the above configuration, since the release mechanism and the guide portion are each formed by a groove, compared to the case where the release mechanism and the guide portion are configured by providing separate members.

A compact rotation output device can be configured.

[0029] In one embodiment of the present invention, an escape portion that allows relative rotation is formed between the movable lock plate and the rotation output body.

According to the above configuration, the rotation is not transmitted from the rotation output body because the escape portion is formed.

[0030] For this reason, the movement lock body can reliably prevent the rotation angle corresponding to the "escape portion" from rotating together with the rotation output body.

Therefore, it is possible to reliably prevent the movement lock body from rotating together with the rotation output body, and even when the rotation input body and the rotation output body rotate together without any play angle, the movement lock body does not rotate together. The function can be obtained without fail.

[0031] Further, in one embodiment of the present invention, the movable lock plate is provided with a guide holding plate fixed to the rotation output body and rotated integrally with the rotation output body, and a plurality of the movement lock plates provided in the circumferential direction. It is held on the guide holding plate so as to rotate integrally.

According to the above configuration, since the plurality of movable lock plates are engaged and fixed with the fixing member, the rigidity at the engagement portion is increased, the lock torque at the time of locking can be increased, and a reliable and stable lock function is achieved. Can be obtained.

[0032] Further, in one embodiment of the present invention, the plate thickness of the fixed portion of the guide holding plate to the rotation output body is set to be thicker than the plate thickness of other portions of the guide holding plate. . According to the above configuration, the pressure receiving area with the rotation output body can be increased by increasing the thickness of the guide holding plate at the fixing portion with the rotation output body.

[0033] For this reason, the guide holding plate can reliably receive the rotational torque against the rotational torque from the rotation output body, while making the guide holding plate itself thin. Therefore, it is possible to reliably receive the rotational torque from the rotary output body and increase the lock torque while the guide holding plate is compact.

[0034] Furthermore, the rotation output device of the present invention can be used in an apparatus that requires rotation output, in addition to being interposed in the output system of the electric tool.

Thereby, operation at the time of locking of an electric tool etc. can be performed very easily. The invention's effect

[0035] According to the present invention, after the rotation of the input shaft is stopped, the output shaft by the user is securely locked by the rotation of the output shaft, and the released state can be reliably maintained during the rotation. The entire lock mechanism can be configured compactly.

BEST MODE FOR CARRYING OUT THE INVENTION

[0036] An embodiment of the present invention will be described below in detail with reference to the drawings.

FIG. 1 shows a power tool that employs the rotation output device of the present invention. As shown in FIG. 1, the electric power tool includes a housing 1 having a handle portion la to be gripped by a user during use, a power cord 2 provided at a lower portion of the handle portion la, a spindle 3 provided in front of the housing 1, and its spin. A chuck 4 mounted on the cylinder 3 and a drill bit 5 supported by the chuck 4 are provided.

[0037] The housing 1 described above includes a main body case portion 11 and a gear case 12 mounted in front of the main body case portion 11. Inside the housing 1, a motor M that can select forward rotation and reverse rotation is selectable. And a rotational output device 10 (see FIG. 2) described later, and the rotational driving force of the motor M is transmitted to the spindle 3 through the rotational output device 10.

A switch handle 6 for inputting a drive signal of the motor M is provided above the front surface of the handle portion la of the housing 1.

[0038] In the present embodiment, a general power tool with a cord will be described. However, the present invention itself may be a battery-type hand-type power tool that is not a power tool with a limited power source. . In addition, the installation tool may be a screwdriver, a grinder or a router. Further, the drive source may be not only electric but also compressed air or hydraulic drive.

Next, the rotation output device 10 inside the electric tool will be described with reference to FIG. 2 and FIG.

The rotation output device 10 transmits the rotation output from the output shaft Ml of the motor M, and Lock mechanism 1 for locking and releasing the spindle 1 OA is provided inside the gear case 12.

[0040] Next, the lock mechanism section 10A has, as main components, an output gear 31 that receives a rotational driving force from the output shaft Ml of the motor described above, and the lock mechanism section 10A that is located on the outer edge portion into a gear case 12. Lock ring 33 to be fixed, two float gears 34 meshed with the inner gear of the lock ring 33, and two pieces fitted and fixed to the spindle 3 with the float gear 34 also sandwiching the force in the longitudinal direction of the shaft center Output ring 32 (32a, 32b), and is configured to auto-release spindle 3 in response to rotation from motor M side.

[0041] As shown in Fig. 2, the output shaft Ml is arranged so as to be in the direction of approximately 7 o'clock in the rear view with respect to the spindle 3 (lower left in Fig. 2), and the output shaft Ml is driven to rotate by the output gear. The outer gear of the input gear M2 for transmitting to 31 and the output gear 31 may be formed of either a helical gear or a spur gear.

[0042] The detailed structure of the lock mechanism 10A will be described with reference to FIGS. 4 and 5. FIG. Fig. 4 is an exploded explanatory view showing both the front and side of the chuck side force of each component of the lock mechanism in the rotation output device, and Fig. 5 is an exploded perspective view of each component of the lock mechanism in the rotation output device. 4 shows a side view taken along the cut surface of the broken line in the front view of FIG.

[0043] As shown in Fig. 4, the lock mechanism 10A described above includes, from the chuck side, the fixing plate 36, the retainer 37, the Maoka 38, the bearing plate 39, the Chucky law output ring 32b, the P-cuckling 3 3, It has 2 float gears 34, 2 coil springs 35, motor side output ring 32a, and output gear 31. Each element except 2 float gears 34, coil springs 35, and steel balls 3 8 Are formed in a ring shape and disposed on the same axis.

[0044] The spindle 3 is viewed from the side of the chuck 4 shown in FIG. 1 in front view, which is substantially inscribed in the chuck shaft mounting portion 3a and a circle having a diameter of about 1.5 times the diameter of the chuck shaft mounting portion 3a. A hexagonal hexagonal cut surface portion 3b, a shaft stop portion 3c having substantially the same diameter as the chuck shaft attachment portion 3a, and supported by a bearing 13 (Fig. 3) provided in the front inside of the gear case 12. A small judgment surface connecting portion 3d having a small judgment surface (a cross section having a straight portion with a diameter equal to or less than the circular center across the circular center) smaller than the chuck shaft fitting portion 3a; It is supported by a bearing (not shown) that is about half the diameter and is provided near the center of the gear case 12. The shaft stoppers 3e are arranged in this order.

[0045] As shown in FIG. 6, the output gear 31 has a diameter about three times as large as the small judgment surface connecting portion 3d and an appropriate thickness, and has a tooth 3 la having an appropriate tooth height on the outer peripheral portion. Spur gear formed. A shaft through hole 31b loosely fitted to the small judgment surface connecting portion 3d at the center of the output gear 31 as viewed from the front, and a latch provided at the center of the float gear 34 described later at a position facing the shaft through hole 31b. It has a pin insertion hole 31c for inserting a stop pin. The output gear 31 may be a helical gear.

In the front view of the output gear 31, the teeth of the spur gear are simplified and the teeth 31a are shown as circles.

[0046] The shaft through hole 31b has a zigzag shape in front view in which the small judgment surface connecting portion 3d is loosely fitted with a play angle a (see FIG. 6), and the upper surface and the bottom surface are formed by arcs protruding outward. It is. The pin insertion hole 31c has a substantially isosceles triangular shape in front view formed by continuously arranging circles having a slightly larger diameter than the locking pin of the float gear 34 in three directions, and about 1Z4 of the output gear 31. It is a groove having a depth, and is arranged in a convex shape on the radially outward side.

[0047] The center interval of the left and right radial inner arc portions formed on the bottom side of the substantially isosceles triangle is the above-mentioned play angle α + j8, which is a combination of the play angle α and the play angle β. The width corresponds to the movement of the locking pin.

In addition, when the locking pin is fitted to the outer diameter central arc portion which is the apex portion of the approximately isosceles triangle shape of the pin insertion hole 31c, the float gear 34 is engaged with the lock ring 33 and fixed to the outer diameter. When the locking pin is fitted to the left and right radial inner circular arc portions of the pin insertion hole 31c, the float gear 34 is fixed to the inner diameter of the lock ring 33 and released from being locked. It is in the release position.

Further, the pin insertion hole 31c may be formed as a hole penetrating the output gear 31.

[0048] The motor-side output ring 32a has a substantially oval shape having substantially the same diameter and an appropriate thickness as the circular recess 31a, and is formed by folding back to the chuck side in the vicinity of the center of the side straight portion. A fitting pin 32c, a shaft through hole 32d having the same shape as the cross section of the small judgment surface connecting portion 3d at the center, and a central pin through hole 32e at a position corresponding to the pin insertion hole 31c are provided.

The fitting latch 32c is fitted into a fitting hole 32f of a chuck side output ring 32b described later. [0049] Further, the central pin through hole 32e is provided with a circle having a slightly larger diameter than the locking pin of the float gear 34 in three directions, and both ends of the semicircle of the apex side circle and the bottom side 2 circles. This is a shape with circular arcs in three directions that are continuously formed by connecting straight lines in the inner and outer directions with a radius of about 1Z4 (see Fig. 7).

The center distance between the left and right radial inner arcs formed on the bottom side of the three-direction arcs is a width corresponding to twice the play angle β.

In addition, when the locking pin is fitted to the outer radial arc portion of the outer diameter of the three-way arcs of the central pin through hole 32e, the float gear 34 is engaged with the lock ring 33 and fixed to the outer diameter. When the locking pin is fitted to the left and right radial inner circular arc portions of the central pin through hole 32e at the rotation fixed position, the float gear 34 is within the diameter of the lock ring 33 and the engagement fixed release. In the unlocked position.

[0050] In addition, an appropriate width of the outer peripheral portion of the shaft through hole 32d is projected to the chuck side so as to be thicker than the other portions of the output ring 32. Specifically, the outer peripheral portion of the shaft through hole 32d is formed with a thickness of about 1.3 times the thickness of the other portions.

[0051] The float gear 34 has a substantially comb shape having four leg portions and a circular arc portion 34a projecting upward, and the circular arc portion 34a is slightly smaller than the tip circle of the inner gear of the lock ring 33 described later. A circular arc having a small diameter is provided at the center of the upper portion with three gears 34b meshing with the inner gear of the lock ring 33 at a symmetrical position.

[0052] Further, in the center of the bottom side of the float gear 34, the float gear 34 is located at a radially inner position (inner diameter fixed release position) where the engagement between the inner gear 33a and the gear 34b of the lock ring 33 is eliminated. In this case, the small judgment surface connecting portion 3d of the spindle 3 includes a loose fitting portion 34c that can be loosely fitted with a play angle oc, and the central leg 34d that forms the side portion of the loose fitting portion 34c is floated. Prepare for symmetry in both positions, approximately 1Z4 width outside the gear 34!

[0053] Further, outer leg portions 34e that are spaced apart from the central leg portion 34d at an appropriate distance are provided symmetrically at the width direction ends of the float gear 34 on both outer sides of the central leg portion 34d.

In addition, the bottom surface of the outer leg 34e is formed at substantially the same height as the arc end of the loosely fitting part 34c, and the central leg 34d is about twice as long and half as wide as the outer leg 34e. Have [0054] Further, the appropriate distance between the outer leg 34e and the central leg 34d is an interval that is slightly larger than the diameter in the width direction of a coil spring 35, which will be described later, and a spring in which the coil spring 35 is loosely fitted. A mounting portion 34f is formed.

[0055] Further, on the central axis in the width direction of the float gear 34, a lock having an appropriate diameter and length that penetrates and fixes the float gear 34 in the vicinity of the center between the arc portion 34a and the upper side of the loose fitting portion 34c. A pin 34 g is provided, and is fixed to protrude from the motor side and chuck side sides of the float gear 34 by about twice the wall thickness of the float gear 34.

The protruding length of the locking pin 34g is such that when the lock mechanism 10A is assembled, the pin insertion hole 31c of the output gear 31 disposed on the motor side of the float gear 34 and the float gear 34 are Form the length that the locking pin 34g is locked to the locking groove 37c of the retainer 37 arranged on the chuck side.

[0056] Further, in the vicinity of the center of the arc portion 34a and the upper side of the loosely fitting portion 34c, at an appropriate distance from the locking pin 34g, the locking pin 34g is protruded toward the chuck side with substantially the same diameter. The front is provided with a circular locking projection 34h symmetrically. The protruding length of the locking projection 34h from the front surface of the float gear 34 on the chuck side is formed to be approximately 1Z2 of the protruding length of the locking pin 34g from the front surface of the float gear 34 on the chuck side.

Note that the locking projection 34h is not formed integrally with the float gear 34 main body portion as in the present embodiment, which only needs to perform the same operation and action as the locking pin 34g, but is formed by fixing the pin to the float gear 34. May be.

[0057] The lock mechanism portion 10A includes two float gears 34 in the vertically symmetrical direction, and coil springs loosely fitted on the left and right spring mounting portions 34f of the two float gears 34 in the upward and downward symmetrical directions. It has 35!

The lock ring 33 has a ring shape having an outer shape slightly larger than the tip circle of the output gear 31, and includes an inner surface gear 33a that meshes with the float gear 34 on the inner peripheral surface.

Further, the lock ring 33 is provided with a fixed projection 33b having a circular shape in a front view that is projected by pressing toward the chuck side with a predetermined diameter at a three-direction position that divides the lock ring 33 substantially equally into three in the circumferential direction. To prevent interference with the motor output shaft Ml, the lock ring 33 has a lower left part (about 4 o'clock in front view) of the outer periphery of the lock ring 33. Yes. The fixed convex portion 33b is a convex portion for engaging and fixing the lock ring 33 to the gear case 12.

[0059] The chuck-side output ring 32b has a circular shape when viewed from the front and has an appropriate thickness and the same diameter as the arc portion of the motor-side output ring 32a. Like the motor-side output ring 32a, the chuck-side output ring 3d The shaft through hole 32d has the same shape as the cross section of the center, and the appropriate width of the outer peripheral part of the shaft through hole 32d is projected to the chuck side to make it thicker than the other part. As with the ring 32a, a central pin through hole 32e is provided.

[0060] In addition, lateral pin through holes 32g are provided symmetrically on the left and right sides of the central pin through hole 32e with the same interval as the interval between the locking pin 34g and the locking projection 34h. . The side pin through hole 32g has one of the left and right radially inner arcs on the bottom side of the three circles constituting the center pin through hole 32e, and the other side is the radially inner side. Is arranged in a slanted manner so that the outer diameter is radially outward, and is a deformed shape having circular arcs in three directions formed continuously, and the radially inner circular arc portion deformed radially outward is the chuck side output ring 32b. It is provided symmetrically so that it is on the vertical center line side.

[0061] Further, two fitting holes 32f to be fitted with the fitting clips 32c are provided at positions facing the two central pin through holes 32e at the center at positions facing the center.

The pin insertion hole 31c, the central pin through-hole 32e, and the pin through-hole 38e are arranged so as to be at the same position of the central force.

[0062] The bearing plate 39 has a circular shape in front view having a diameter approximately twice as large as that of the small determination surface coupling portion 3d and an appropriate thickness, and has the same shape as the cross section of the small determination surface coupling portion 3d. 39a is provided at the center, and the upper and lower edges are provided with a notch 39b having a rectangular shape in front view allowing passage of the locking pin 34g.

[0063] Further, a circular fitting recess having a small size in a rear view that fits with the shaft through hole 32d of the chuck side output ring 32b is formed on the outer edge portion of the shaft through hole 39a on the back surface (side surface of the motor M) of the bearing plate 39. 39c is provided on the outer surface of the shaft hole 39a on the surface (chuck side surface) of the bearing plate 39, and a substantially circular rolling groove 39d in which a steel ball 38 described later is loosely fitted is formed in the notch 39b. It has almost the entire circumference across it. [0064] The rolling groove 39d has a cross-sectional groove shape formed by an arc in which about 1Z6 of the outer circumference of the steel ball 38 having a circular cross section comes into surface contact and is loosely fitted. Further, the thickness of the bearing plate 39 itself is formed to be about four times the groove depth of the rolling groove 39d.

The steel balls 38 are steel balls having an appropriate diameter, and are provided with ten steel balls 38 so as to be loosely fitted in respective steel ball holding holes 37b of a retainer 37 described later.

[0065] The retainer 37 has a circular shape when viewed from the front and has substantially the same diameter as the bearing plate 39. The retainer 37 allows the small judgment surface connecting portion 3d of the spindle 3 to pass through the center, and even when the spindle 3 rotates. In order not to hinder, a circular through hole 37a having a diameter larger than the cross-sectional diameter of the small judgment surface connecting portion 3d is provided, and the upper and lower outer peripheral edge portions allow locking of the locking pin 34g in front view. A substantially V-shaped locking groove 37c is provided. Further, on the outer diameter side of the through-hole 37a, five steel ball holding holes 37b in which the steel balls 38 are loosely fitted are provided in the circumferential direction at five positions at equal intervals between the upper and lower locking grooves 37c and 37c. .

[0066] The fixing plate 36 has substantially the same outer diameter as the lock ring 33, has a convex shape in a hollow side view protruding toward the chuck side, and is attached to the side surface of the lock ring 33 on the chuck side. Are provided with mounting through-holes 36b through which the fixed convex portions 33b penetrate at positions corresponding to the fixed convex portions 33b, and are convex inwardly in the radial direction to prevent interference with the motor output shaft Ml. An arc-shaped notch 36c is provided.

[0067] Further, in the center in front view of the convex portion 36d protruding to the chuck side by the press carriage, the penetration of the small judgment surface connecting portion 3d of the spindle 3 is allowed and the spindle 3 is rotated. Is provided with a circular through hole 36f having a diameter larger than the cross-sectional diameter of the small judgment surface connecting portion 3d. Further, the inner side surface (side surface of the motor M) of the convex portion 36d is provided with a rolling groove 36e having a circular shape in rear view in which the steel ball 38 is loosely fitted on the outer peripheral side of the through hole 36f.

[0068] The cross-sectional groove shape of the rolling groove 36e is an arc in which about 1/6 of the outer circumference of the circular cross-section of the steel ball 38 is in surface contact and loosely fitted, and the convex portion 36d is pressed. Formed. In addition, the convex portion 36d is in a locked state in which the locking pin 34g is fitted in the radially outer central arc portion of the pin insertion hole 31c and the central pin through hole 32e so as not to interfere in the locked state in which the locking pin 34g moves radially outward. End force in the radially outward direction of the locking pin 34g From the length to the center of the spindle 3 It is formed with a slightly larger radius.

[0069] With the above configuration, as shown in FIG. 5, two vertically symmetrical float gears 34 are engaged with the inner side gear 33a of the lock ring 33, and the coil springs are contracted to the left and right spring mounting portions 34f. Fit 35 into the lock ring 33. In this state, the motor side locking pin 34g of the float gear 34 is passed through the central pin through hole 32e of the motor side output ring 32a, and the chuck side of the float gear 34 is inserted into the central pin through hole 32e of the chuck side output ring 32b. The locking pin 34g and the locking pin 34h are passed through the side pin through-hole 32g, and the lock ring 33 and the float gear 34 are sandwiched between the motor side output ring 32a and the chuck side output ring 32b. In this manner, the fitting hook 32c penetrating the rectangular through hole 37d and the fitting hole 32f are fitted and assembled.

[0070] The bearing plate 39 and the steel ball holder are held on the chuck side of the chuck side output ring 32b of the motor side output ring 32a, the chuck side output ring 32b, the mouth ring 33 and the chuck side output ring 32b of the float gear 34 thus assembled. A retainer 37 in which a steel ball 38 is loosely fitted is arranged in the hole 37b, the fixing projection 33b of the lock ring 33 is fixed to the mounting through hole 36b of the fixing plate 36, and the bearing plate 39 is fixed to the fixing plate 36. The retainer 37 in which the steel ball 38 is loosely fitted in the steel ball holding hole 37b is assembled in such a manner as to cover the chuck side force. At this time, as shown in FIG. 8, the locking pin 34g on the chuck side of the float gear 34 that penetrates the central pin through hole 32e and also the chuck side force of the chuck side output ring 32b protrudes from the notch portion of the bearing plate 39. 39b and the retaining groove 37c of the retainer 37, and the steel ball 38 is assembled so as to be loosely fitted into the rolling groove 39d of the bearing plate 39 and the rolling groove 36e of the fixed plate 36.

[0071] In this state, the output gear 31 is arranged on the same shaft on the motor side of the assembled motor-side output ring 32a, and the small judgment surface connecting portion 3d of the spindle 3 is connected to the shaft through hole 39a of the bearing plate 39. As shown in Fig. 9, the spindle 3 is inserted from the through hole 36f side so that it fits with the shaft through hole 32d of the output ring 32 and loosely fits with the shaft through hole 31b of the output gear 31. The lock mechanism part 10A can be assembled to.

At this time, as shown in the enlarged view of part a in FIG. 9, the steel ball 38 is composed of a rolling groove 36e of the fixed plate 36 fixed by the lock ring 33 and a bearing plate 39 fixed to the spindle 3 by rotation. Both the rolling grooves 39d are in surface contact with arcuate surfaces. Therefore, with spindle 3 and times When the rolling-fixed bearing plate 39 rotates, the steel ball 38 that rolls while being in surface contact with the rolling groove 36e of the fixed plate 36 is also in surface contact with the rolling groove 39d. While rotating on 39d, it rotates in the rotation direction of the spindle 3 and presses the rotation front side surface of the steel ball holding hole 37b in the rotation direction. At this time, the rotation speed of the retainer 37 becomes half the rotation speed of the bearing plate 39 and can rotate with a torque twice that of the bearing plate 39.

In other words, the retainer 37 rotates in the opposite direction relative to the bearing plate 39. Further, while the bearing plate 39 is rotating, the retainer 37 receives a rotational force in the direction opposite to the rotation with respect to the bearing plate 39. In addition, the retainer 37 absolutely rotates behind the bearing plate 39. In the following description of the present specification, the above effect is referred to as a delayed effect. As shown in FIG. 9, a mechanism comprising a fixed plate 36, a retainer 37, a steel ball 38, and a bearing plate 39, and applying a load in the reverse rotation direction to the float gear 34g is described in this specification. , Deceleration rotation transmission mechanism

[0074] Next, the operation of the lock mechanism section 10A will be described with reference to FIGS.

10, 13 and 15 show front views from the chuck side of the output gear 31 in each state, and FIGS. 11, 14 and 17 show 37 parts of the retainer assembled to the lock mechanism 10A in each state. The front view of the chuck side force is shown, and FIGS. 12 and 16 are front views from the chuck side of the float gear 34 portion assembled to the lock mechanism portion 10A in each state. 10, FIG. 13 and FIG. 15, the chuck side output ring 32b is indicated by a dotted line in order to show the positional relationship between the pin insertion hole 31c and the central pin through hole 32e of the output ring 32.

First, the locked state will be described. In the locked state, as shown in FIG. 10, the locking pin 34g on the motor side of the float gear 34 is fitted to the radially outer central arc portion of the pin insertion hole 31c, and as shown in FIG. The locking pin 34g on the chuck side is fitted to the outer central circular arc portion of the central pin through hole 32e. In this state, as shown in FIG. 12, the upper and lower float gears 34, 34 are urged radially outward by the coil spring 35, and the gear 34b of the float gear 34 is provided on the inner periphery of the lock ring 33. Mated with the internal gear 33a It is in the outer rotation fixed position.

Therefore, the output gear 31 and the output ring 32 rotate to the lock ring 33 via the locking pin 34g of the float gear 34 fixed to the lock ring 33 fixed to the gear case 12 (see FIG. 3). Since the shaft through hole 32d of the output ring 32 and the small judgment surface connecting part 3d of the spindle 3 are fitted with no play angle, the spindle 3 is fixed and rotated so that the user can replace the bit for exchanging bits. Even if the spindle is rotated, the spindle 3 does not rotate, and the user can safely replace the bit.

Next, a release operation for releasing the lock state of the lock mechanism portion 10A by driving the motor M will be described.

When the user operates the switch handle 6 to input a drive signal, the motor M (Fig. 1) rotates, and the rotational driving force of the motor M is output through the teeth 31a meshing with the input gear M2. Is transmitted to 31. In the following description, the rotation of the motor M is the rotational driving force that rotates the output gear 31 counterclockwise (counterclockwise) when viewed from the chuck side.

Here, as shown by the arrow in the locked state force shown in FIG. 10, a front view from the chuck side of the output gear 31 in a state where the output gear 31 rotates counterclockwise is shown in FIG. Fig. 14 shows a front view from the chuck side of the retainer 37 part assembled to 10 mm.

[0079] As the output gear 31 rotates left by a degrees, the locking pin 34g located in the outer central arc of the pin insertion hole 31c is rotated counterclockwise by the side surface behind the rotation of the pin insertion hole 31c. Pressed. The float gear 34 is engaged with the inner gear 33a of the lock ring 33. The float gear 34 cannot rotate counterclockwise, and the output gear rotates counterclockwise against the biasing force of the coil spring 35. It moves radially inward along the side of the 31 pin insertion hole 31c that is behind the rotation. In this state, the engagement between the gear 34b and the inner gear 33a is eliminated, and the output pin 32 engaging the locking pin 34g with the central pin through hole 32e and the output engaging with the pin insertion hole 3lc. The rotation of the gear 31 with respect to each lock ring 33 is released.

[0080] In this state, the rotation fixing of the output ring 32 is released, and the play angle between the small judgment surface connecting portion 3d of the spindle 3 and the shaft through hole 31b of the output gear 31 is digested, and the left of the output gear 31 continues. Due to the rotation, the rotation rear side surface of the small judgment surface coupling portion 3d is opposed to the upper side surface of the shaft through hole 31b. Therefore, the output ring 3 2 that is pressed in the rotation direction and fitted to the spindle 3 and the spindle 3 rotates counterclockwise.

However, since the float gear 34 is provided with the loose fitting portion 34c, the float gears 34 and 34 moved to the in-diameter fixed release position and the small judgment surface connecting portion 3d do not come into contact with each other. In this state, the side surface of the radially inner circular arc portion of the central pin through hole 32e is not in contact with the locking pin 34g, so that the rotation of the float gear 34 is not transmitted at this in-diameter rotation fixed position.

Subsequently, as indicated by an arrow in FIG. 13, the output gear 31 is further increased. Fig. 15 shows a front view of the chuck side force of the output gear 31 in this state, and the lock mechanism 10A is assembled to the left rotated state (from the closed state (a + j8) °). FIG. 16 showing a front view of the chuck side force of the float gear 34 portion and FIG. 17 showing a front view from the chuck side of the retainer 37 portion assembled to the lock mechanism portion 10A will be described.

[0083] As described above, the shaft through hole 31b of the output gear 31 that receives the rotational driving force of the motor M presses the rotation rear side surface of the small cross-section connecting portion 3d in the left rotation direction, and the small determination surface connecting portion 3d and The fitted output ring 32 rotates counterclockwise. However, as described above, since the rotational force is not transmitted to the locking pin 34g, the locking pin 34g is fitted into the radially inner circular arc portion of the rotated pin insertion hole 31c and the central pin through hole 32e. In this state, the float gear 34 is pressed in the rotation direction by the side surface of the radially inner circular arc portion behind the rotation of the pin insertion hole 31c and the central pin through hole 32e, so that the spindle 3, the output ring 32, and the output The gear 31 and the float gear 34 rotate integrally, and rotate in this state while the motor M is rotating.

[0084] In the above description, the force described in the case where the output gear 31 rotates << ° and the state where it further rotates j8 ° after that is actually a series of operations. Therefore, even when the lock mechanism 10A is in the locked state, the user can auto-release and rotate the lock mechanism 10A that has been locked simply by operating the switch handle 6. User convenience can be improved.

[0085] During rotation of the motor M, the locking pin 34g rotates integrally with the retainer 37 always applied with the rotational force in the reverse rotation direction due to the delay effect of the reduced rotation transmission mechanism. Therefore, the float gear 34g rotates integrally with the pin insertion hole 31c and the central pin through-hole 32e rotating in the reverse rotation direction on the side surface of the radially inner circular arc portion behind the rotation. It is rolling. Therefore, the pin insertion hole 31c and the central pin through hole 32e are prevented from being inadvertently locked due to the release of the radially inner radial partial force behind the rotation. Also, due to the rotational force in the reverse rotation direction due to the delay effect of the deceleration rotation transmission mechanism described above, after the motor M stops, the inertial force of the spindle 3 causes the spindle 3 to rotate in the direction of rotation so far with the shaft through hole 3 lb. Rotation by α (hereinafter referred to as inertial force rotation) is prevented. Also, for example, when a tool with a large inertial force such as a rotor is attached to the chuck, the inertial force of the spindle 3 after the motor Μ stops exceeds the rotational force in the reverse direction of the retainer 37, and the inertial force Even if rotation occurs, the inertia force of the inertial force rotation is reduced by the rotational force in the reverse direction of rotation by the retainer 37. And the impact generated at the loose fitting part between the shaft through hole and 3 lb can be reduced.

Next, the lock operation after the rotation of the motor M is stopped will be described.

As described above, when inertial force rotation does not occur after the motor is stopped, the float gear 34 is in the radially inward fixing release position on the radially inward side, and is stopped in the state shown in FIGS. 15, 16, and 17. In this state, since the gear 34b and the inner gear 33a are not meshed with each other, the spindle 3 is in a rotatable state.

[0087] In order to perform bit exchange or the like, the user is assumed to rotate the spindle 3 in either the right rotation or the left rotation in this state.

First, a case will be described in which the user rotates the spindle 3 counterclockwise by the motor M in the same direction as before.

[0088] When the spindle 3 rotates counterclockwise, the output ring 32 that is rotationally fixed to the spindle 3 rotates counterclockwise integrally with the spindle 3, and the float gear 34 has a locking pin 34g positioned in the center pin through hole 32e. Since it is pressed against the side surface behind the rotation, it rotates integrally with the spindle 3. However, since there is a play angle _{α in} front of the rotation between the shaft through hole 31b and the small judgment surface connecting portion 3d, the output gear 31 and the spindle 3 do not rotate integrally. Therefore, due to the urging force of the coil spring 35 in the radially outward direction, the locking pin 34g moves to the radially outer central arc portion along the rotation rear side surface of the pin insertion hole 31c, and the float gear 34 is fixed to the radially outer rotation. Move to position. Therefore, as described above, the gear 34b and the inner gear 33a are engaged (see FIG. 12), and the lock mechanism 1 OA is in the fixed state shown in FIGS.

[0089] Next, a case where the user rotates the spindle 3 to the right, which is the direction opposite to the direction in which the motor M has been rotated, will be described.

When the spindle 3 rotates to the right, the output ring 32 fixed to the spindle 3 rotates to the right integrally with the spindle 3, and the float gear 34 has a locking pin 34g positioned behind the center pin through hole 32e. Since it is pressed by the side, it rotates integrally with the spindle 3. Here, unlike the case of the left rotation, in the case of the right rotation, there is no play angle α in front of the rotation between the shaft through hole 31b of the output gear 31 and the small judgment surface coupling portion 3d of the spindle 3, so that the spindle 3 and the output gear 31 rotate together. However, when the spindle 3 rotates, the delay effect of the above-mentioned reduced-speed rotation transmission mechanism occurs in the retainer 37, and the float gear 34 rotates integrally with the spindle 3, but the float gear 34g is rotated via the locking groove 37c. A rotational force in the opposite direction of rotation is applied. Therefore, as shown in FIG. 17, the locking pin 34g that is locked to the central portion on the radially inner side of the locking groove 37c is moved forward of the locking groove 37c by the biasing force in the radially outward direction of the coil spring 35. The float gear 34 moves to the outside rotation fixed position by moving outward along the side surface. Therefore, as described above, the gear 34b and the inner gear 33a are engaged with each other (see FIG. 12), and the lock mechanism portion 10A is in the fixed state shown in FIGS.

[0090] Thereby, when the spindle M stops after the motor M stops, the user automatically turns the spindle 3 by rotating the spindle 3 in the same direction or in the opposite direction. Spindle 3 can be locked. Therefore, as described above, even when the user rotates the spindle 3 for exchanging the bit, the rotation of the spindle 3 is fixed, and the user can safely exchange the bit. .

[0091] According to the above configuration, the float gear 34 is automatically guided to the radially inner side by the rotation from the output gear 31 side to which the rotational driving force is input, and the engagement fixing with the lock ring 33 is released. The locking groove 37c is decelerated and rotated to the float gear 34 whose engagement with the lock ring 33 is released on the radially inner side by rotation from the spindle 3. The differential with the spindle 3 generated by the transmission mechanism is transmitted, and the coil spring 35 biases the float gear 34 to the radially outward side, thereby moving the float gear 34 to the radially outward side and locking it. The mechanism unit 10A can be locked. Further, since the differential with respect to the spindle 3 generated by the reduced rotation transmission mechanism is transmitted to the float gear 34, a force in the reverse rotation direction is always applied to the float gear 34 during rotation. Therefore, during rotation, the float gear 34 guided to the radially inward side by the pin insertion hole 31c and released from the engagement with the lock ring 33 can be held in the radially inward arc portion.

[0093] In addition, since the release mechanism for guiding the float gear 34g to the in-diameter fixed release position is formed by the pin insertion hole 31c, the rotary output device 10 is more compact than the case where another member is provided. Can be configured.

[0094] Further, the float gear 34 is formed with the loose fitting portion 34c to which the rotation is not transmitted from the spindle 3, so that the float gear 34 reliably rotates the rotation angle corresponding to the "free fitting portion 34c" with the spindle 3. Therefore, it is possible to reliably prevent the float gear 34 from co-rotating with the spindle 3. Even when the output gear 31 and the spindle 3 rotate together without a play angle α, the movable lock body can reliably obtain a function without rotating together.

[0095] Further, since the plurality of float gears 34 are fixedly engaged with the lock ring 33, the rigidity at the engaging portion is increased, the locking torque at the time of locking can be increased, and a reliable and stable locking function is obtained. be able to.

[0096] Further, by increasing the thickness of the output ring 32 at the fitting portion with the spindle 3, the pressure receiving area with the spindle 3 can be increased, and the rotational torque from the spindle 3 can be increased. On the other hand, while the output ring 32 itself is thinned, the output ring 32 can reliably receive the rotating torque. Therefore, while the output ring 32 is made compact, the rotational torque from the spindle 3 can be reliably received, and the lock torque can be increased.

Note that, as shown in FIG. 18, the fixing plate 36 in the present embodiment may be formed integrally with the lock ring 33. More specifically, when the lock ring 33 is formed, a portion corresponding to the convex portion 36d of the present embodiment may be formed by press working in the disk-shaped steel material force. In this way, the number of parts constituting the lock mechanism portion 10A can be reduced, and a part of the assembly process can be reduced.

Further, as shown in FIG. 19, the steel ball 38 loosely fitted in the steel ball holding hole 37b of the retainer 37 is A roller body 38 'may be used. In this case, the roller retainer 37 ′ is provided with a roller holding hole 37′b slightly larger than the outer surface of the roller body 38 ′ in the circumferential direction in the same manner as the steel ball holding hole 37b of the present embodiment. It is only necessary to support the rotation shaft 38'a. In this case, the plate thickness of the retainer 37 is formed thinner than the diameter of the roller rotating body 38′b.

Accordingly, since linear contact portions can be secured between the roller body 38 ′, the bearing plate 39, and the fixed plate 36, the rotation of the bearing plate 39 can be reliably transmitted to the roller retainer 37 ′. Further, the rolling groove 36e and the rolling groove 39d need not be provided in the fixed plate 36 and the bearing plate 39.

Next, another example shown in FIG. 20 will be described. In this embodiment, the pressing force of the bearing plate 39 against the steel ball 38 is increased so that the rolling of the steel ball occurs reliably. Note that the same components as those in FIG. 4 are denoted by the same reference numerals and description thereof is omitted.

[0101] In this embodiment, an annular wave washer 40 is interposed between the bearing plate 39 and the chuck-side output ring 32b. That is, the inner peripheral portion 40a of the annular wave washer 40 is fitted to the flange on the periphery of the shaft through hole 32d of the chuck side output ring 32b, so that it is set on the chuck side output ring 32b, and the bearing plate 39 and the chuck It is interposed between the side output ring 32b.

[0102] With such a configuration, the wave washer 40 exerts a force that expands in the axial direction, and the bearing plate 39 is constantly urged toward the steel ball 38 side.

Therefore, since the steel ball 38 biased by the bearing plate 39 is pressed against the fixed plate 36 side, the pressing force of the steel ball 38 against the rolling groove 36e of the fixed plate 36 and the rolling groove 39d of the bearing plate 39 increases. As a result, the rolling of the steel ball 38 occurs reliably.

[0103] Therefore, according to this embodiment, the function of the steel ball 38 is more exhibited than that of the above-described embodiment, so that the above-described effects can be reliably achieved.

[0104] As described above, in the correspondence between the configuration of the present invention and the above-described embodiment,

The rotation output device of the present invention corresponds to the rotation output device 10,

Similarly,

The rotary input body corresponds to the output gear 31. The play angle corresponds to the play angle α,

The rotating output body corresponds to spindle 3,

The fixing member corresponds to the lock ring 33,

The movement lock plate corresponds to the float gear 34,

The biasing body corresponds to the coil spring 35,

The guide part corresponds to the locking groove 37c,

The reduced speed rotation transmission mechanism corresponds to the fixed plate 36, retainer 37, steel ball 38 and bearing plate 39,

The release mechanism corresponds to the pin insertion hole 31c,

The fixing plate corresponds to the fixing plate 36,

The rotating plate corresponds to the bearing plate 39,

The rolling element corresponds to the steel ball 38,

The rolling element holding plate corresponds to the retainer 37,

The engaging projection corresponds to the locking pin 34g,

The guide groove corresponds to the locking groove 37c,

The release groove corresponds to the pin insertion hole 31c,

The escape portion corresponds to the loose fitting portion 34c,

The guide holding plate is compatible with the output ring 32,

The present invention is not limited to the configuration of the above-described embodiment.

Brief Description of Drawings

FIG. 1 is a side view of a power tool that employs a rotation output device.

FIG. 2 is a rear view of the rotation output device attached to the gear case.

FIG. 3 is a cross-sectional explanatory view of a gear case in a state where a rotation output device is mounted.

FIG. 4 is an explanatory diagram showing the front and side of each component of the lock mechanism in the rotation output device.

FIG. 5 is an exploded perspective view of each component of the lock mechanism in the rotation output device.

[Fig. 6] Front view of the output gear.

[Fig. 7] Front view of the output ring. FIG. 8 is an exploded perspective view of each component of the deceleration rotation transmission mechanism.

9] An explanatory diagram of the lock mechanism.

FIG. 10 is a front view of the chuck side force of the output gear in the locked state.

FIG. 11 is a front view from the chuck side of the retainer part assembled in the lock mechanism in the locked state.

FIG. 12 shows a front view from the chuck side of the float gear part assembled in the lock mechanism in the locked state.

[Fig. 13] «° Front view from the chuck side of the output gear in a left-turned state

FIG. 14 is a front view from the chuck side of the retainer part assembled in the lock mechanism with the output gear rotated to the left by α °.

[Fig.15] Front view of the chuck side force of the output gear when rotated further | 8 ° counterclockwise.

FIG. 16 is a front view of the chuck side force of the float gear portion assembled to the lock mechanism with the output gear further rotated to the left by β °.

FIG. 17 is a front view from the chuck side of the retainer part assembled in the lock mechanism with the output gear further rotated to the left by β °.

圆 18] Explanatory drawing about the fixing plate of another embodiment.

圆 19] Explanatory drawing about the retainer and steel ball of another embodiment.

FIG. 20 is an exploded explanatory view showing the front and side surfaces of each component of the lock mechanism in the rotation output device of another embodiment.

Explanation of symbols

3 Spin Donore

10 Rotation output device

31 Output gear

31c Pin insertion hole

32 output ring

33 Lock ring

34 Float gear

34c Free fitting part g Locking pin Coil spring Fixing plate Retainer c Locking groove

wrecking ball

Bearing plate Free angle

Claims

The scope of the claims

[1] A rotational input body for inputting rotational driving force;

A rotational output body that is disposed on the same axis as the rotational input body, and that outputs a rotational force upon receiving a driving force from the rotational input body with a predetermined play angle;

A fixing member disposed on the outer periphery of the rotation output body and fixed in rotation;

A movable lock plate that rotates integrally with the rotary output body, moves outward in the radial direction, and engages and fixes to the fixing member;

An urging body for urging the movable lock plate radially outward;

An anti-rotational force applying means that applies a force in the reverse rotation direction to the movement lock plate, and the anti-rotation force applying means includes a guide portion that guides the movement of the movement lock plate to the radially outward side,

The anti-rotational force applying means comprises a reduced rotation transmission mechanism that decelerates the rotation of the rotation output body relative to the fixed member and transmits it to the movable lock plate,

The rotation input body is provided with a release mechanism that, by rotation from the rotation input body side, guides the moving lock plate radially inward to release the engagement and fixation with the fixing member,

The movement of the locking mechanism that guides the movable locking plate on the radially inner side by the rotation from the rotating output body to the radially outer side is released from the engagement and fixation with the fixing member on the radially inner side. The guide portion that transmits the differential with the rotation output body generated by the deceleration rotation transmission mechanism to the lock plate, and the movable lock plate that is transmitted the differential through the guide portion to the radially outward side Consists of the biasing body to bias

Rotation output device.

[2] The deceleration rotation transmission mechanism is

A fixing plate in a direction perpendicular to the axis fixed to the fixing member;

A rotating plate parallel to the fixed plate and rotatably fixed to the rotary output body;

A rolling element that rolls between the rotating plate and the fixed plate while abutting against each opposing surface, and a rolling element holding plate that holds the rolling element in a rollable manner.

The guide part is arranged on the rolling element holding plate. The rotation output device according to claim 1.

[3] A plurality of the rolling elements are provided in the circumferential direction,

The plurality of rolling elements are held by a rolling element holding plate so as to rotate integrally.

The rotation output device according to claim 2.

[4] The rolling element is formed of a sphere.

The rotation output device according to claim 2 or 3.

[5] The moving lock plate includes an engaging convex portion,

The guide portion is configured by a guide groove with which the engagement convex portion is engaged,

The release mechanism is configured with a release groove with which the engagement convex portion engages.

The rotation output device according to any one of claims 1 to 4.

6. The rotation output device according to any one of claims 1 to 5, wherein an escape portion that allows relative rotation is formed between the movable lock plate and the rotation output body.

[7] A guide holding plate fixed to the rotation output body and rotating integrally with the rotation output body,

A plurality of the movement lock plates provided in the circumferential direction are held on the guide holding plate so as to rotate integrally.

The rotation output device according to any one of claims 1 to 6.

[8] The thickness of the guide holding plate fixed to the rotating output body is set to be thicker than the thickness of the other portions of the guide holding plate.

The rotation output device according to any one of claims 1 to 7.

[9] An electric tool comprising the output system and the rotation output device according to any one of claims 1 to 8.