JP3447857B2 - Power tool torque transmission mechanism - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a torque transmission mechanism provided in an electric tool such as an electric hammer or a hammer drill for transmitting rotation of a motor shaft to a bit side. 2. Description of the Related Art A conventional torque transmission mechanism is disclosed in
One disclosed in Japanese Patent Publication No. 0-23319 is known. In this method, a gear transmitted from the motor shaft is loosely fitted to a shaft supported between the motor shaft side and the bit side, and a pressing plate slidable in the axial direction is provided so as to be integrally rotatable with the shaft. The presser plate is urged toward the gear by two disc springs, and the gear and the presser plate are integrated by locking a ball provided on one side with an engagement hole formed on the other side to form a gear. Rotation can be transmitted to the shaft. Here, when the load on the shaft increases, the ball is disengaged from the engagement hole, and the gear has an overload clutch function that idles. Japanese Patent Application Laid-Open No. 2-116405 discloses that a cage is provided in a radial direction between a clutch gear which rotates while meshing with a motor shaft and is loosely fitted to a shaft and a cage integral with the shaft. A locking member that projects radially by a compression spring into the notch is provided, and a locking groove for locking the locking member is provided in the clutch gear. An invention that has a function as a load clutch is disclosed. In the above-mentioned conventional torque transmission mechanism, the former employs an inexpensive disc spring and sets its pressing force as a torque limit as it is. Due to the large amount of deflection against the load in the axial direction and the variance of the deflection, it is necessary to adjust the pressing force for each tool by providing an adjusting screw on the disc spring, which makes the assembling labor very troublesome. . In the latter case, it is easy to set the torque limit value by adopting a compression spring with little variation in characteristics. However, since it is necessary to provide a compression spring in each of a plurality of notches, this is also assembled. Problems such as labor and cost increase. SUMMARY OF THE INVENTION Accordingly, the present invention provides a low-cost, highly-reliable torque system that can easily set a stable torque limit even when an inexpensive disc spring is employed. obtained by the configurable transmission mechanism, its configuration, before
A cylindrical portion is provided on the rotating shaft side, and is provided around the cylindrical portion.
A sleeve consisting of a disc part with a radial connection recess
The gear is coaxially loosely fitted on the disk of the sleeve,
A clutch formed by a connecting recess of a leave and a recess of a gear.
While inserting the ball into the groove, the biasing means, Yu the cylindrical portion
Is fitted, a pressing member movable in the axial direction of a tapered portion cylindrical portion for urging the engagement direction between the ball and the contact with the recess, the member is suppressed provided the cylindrical portion to the ball side And a disc spring for pressing. An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a longitudinal sectional view of a hammer drill 1 in which a housing cap 4 is provided in an outer housing 2.
And an operating mechanism 3 supported by a crank housing 5 screwed to the housing cap 4, supported by the crank housing 5 and the gear housing 6,
A transmission mechanism 40 for transmitting rotation from the motor 9 to the operation mechanism 3 is configured respectively. Further, between the operating mechanism 3 and the transmission mechanism 40, a switching mechanism 6 capable of switching operation to three modes of a hitting mode, a neutral mode, and a hitting + rotation mode.
0 is interposed. First, the operation mechanism 3 will be described. In this embodiment, the bit 7 side is the front, the handle 8 side is the rear, the upper side in FIG. 1 is the upper side, and the lower side is the lower side. A motor shaft 9a of a motor 9 disposed vertically behind the hammer drill has a gear 11 integrated with a crankshaft 10 supported vertically in the rear of the crank housing 5.
The piston 14 is connected via a connecting rod 13 to a connecting pin 12 projecting eccentrically upward of the crankshaft 10 via a connecting rod 13.
Is converted into a reciprocating motion of the piston 14. Note that the crankshaft 10 is a hollow member having an upper opening as shown in a cross section, so that the weight is reduced. The piston 14 is provided inside a cylindrical cylinder 15. The cylinder 15 is made of aluminum, and its rear portion is gripped and fixed to the crank housing 5 and extends forward.
A slide sleeve 16 and a tool holder 17 are coaxially fitted to the front half, respectively. First, the tool holder 17
Is composed of a small-diameter portion 18 to which the bit 7 is attached and detached, a middle-diameter portion 19 that is supported by a ball bearing 4 a provided on the housing cap 4, and a large-diameter portion 20 that is externally fitted to the slide sleeve 16. The part 18 projects forward from the housing 2, where the chuck sleeve 80
The locking grooves 7a, 7a of the bit 7 are locked by the rollers 81, 81 pressed by the roller, the bit 7 is gripped so as to be able to rotate integrally, and the rear large-diameter portion 20 has the engaging projection 2 formed on the outer periphery.
The shaft 2 of the transmission mechanism 40
The tool holder 17 is in mesh with the engagement teeth 24 at the front end of the bevel gear 23 which is engaged with the metal 5 and is supported by the metal 22. Next, the slide sleeve 16 is a cylindrical body made of a synthetic resin which is loosely inserted between the large-diameter portion 20 of the tool holder 17 and the cylinder 15 so as to be slidable back and forth. The rear position is regulated by contacting the front end, and a washer 26 and a rubber 27 are disposed on the front side so as to be movable back and forth between the middle diameter portion 19 and the washer 26 and the like. You can move forward until you touch. On the other hand, a compression spring 29 is arranged behind the slide sleeve 16 and the bevel gear 23 to urge the slide sleeve 16 forward. An iron receiving ring 28 is interposed. In the cylinder 15, a piston 14 is provided.
A striker 31 is disposed movably forward and backward via an air chamber 30 to form a second air chamber 32 in front of the striker 31. A middle element 33 is provided in the middle diameter portion 19 of the tool holder 17.
Are also arranged to be able to move back and forth. Also cylinder 1
At the position of the air chamber 30, one refill hole 34 and six air holes 35, 35.
The air chamber 32 is also provided with six ventilation holes 36. First, the refill hole 34 on the side of the air chamber 30 is
The air hole 35 is provided only at the retracted position where the folded portion 16a of the slide sleeve 16 abuts against the tip of the cylinder 15, and the receiving ring 2 is simultaneously retracted.
8 (FIG. 2). Further slide sleeve 1
3, large slits 37, 37,... And small width slits 38, 38,... Are formed in the axial direction, respectively, as shown in FIG.
0, at the outer circumferential position of the ventilation hole 36 of the cylinder 15,
Six through holes 39, 39... And six auxiliary holes 39 a, 39 a in which the axial position from the front is shifted from the through hole 39.
.. are provided respectively, but the slide sleeve 16
The slits 37 and 38 of the tool holder 17 are provided with a through hole 39 and an auxiliary hole 39a so that the slide sleeve 16 can communicate with the vent hole 36 regardless of whether the slide sleeve 16 is in the forward or backward position.
The slit 37, even if the tool holder 17 rotates,
38 are provided so that they can communicate with each other. In the operating mechanism 3 configured as described above, the bit 7 is inserted from the tip of the tool holder 17 at the time of normal work, and when the abutted intermediate piece 33 is pushed in, the intermediate piece 33 retreats the washer 26 and the rubber 27. To contact the folded portion 16a of the slide sleeve 16
6 and the receiving ring 28 are retracted against the bias of the compression spring 29 (the position in FIG. 1). At this time, since the air hole 35 is closed by the receiving ring 28, when the piston 14 advances and retreats here, the air chamber 30 acts as an air spring, causing the striker 31 to interlock and project into the second air chamber 32. The rear end of the meson 33 is hit and the hitting action is transmitted to the bit 7. The second air chamber 32 communicates with the outside through the slits 37 and 38 of the slide sleeve 16 and the through-hole 39 or the auxiliary hole 39a of the large-diameter portion 20 of the tool holder 17, so that the slide sleeve 16 can be moved forward and backward. Even if the tool holder 17 rotates, there is no rebound of air here, and no loss of impact force occurs. In addition, washer 26, rubber 27
Is designed to buffer the reaction from the bit 7 at this time and to mitigate the rearward impact. And at the time of blank hit,
As shown in FIG. 4, the bit 7 moves forward until the rear end of the locking groove 7 a comes into contact with the rollers 81, 81, and at the same time, the washer 26 until the intermediate piece 33 comes into contact with the small diameter portion 18. The rubber 27 moves forward until it comes into contact with the middle diameter portion 19 by the bias of the compression spring 29. At this time, the slide sleeve 16 and the receiving ring 28 also advance to the positions shown in the figure, but the closed air holes 35 are opened, so that the function of the air spring of the air chamber 30 is lost, and The linkage of the striker 31 is cut off, and the striker 31 stops at a position where it comes into contact with the rear end of the advancing intermediate piece 33, so that the subsequent idle strike is prevented. Also at this time, since the second air chamber 32 communicates with the outside through the long slits 37, 38, the through hole 39 or the auxiliary hole 39a from the ventilation hole 36, the air here rebounds and the striker is hit. There is no risk of pushing back the piston 31 toward the piston 14. As described above, in the above-mentioned hammer drill 1, the cylinder 15 is connected to the tool holder 17 for transmitting rotation.
The cylinder 15 is made of a lightweight material such as aluminum by being provided with the operating mechanism 3 which is fixed to the housing separately from the housing and which performs opening / closing of the air hole 35 for preventing an idle hit by moving the slide sleeve 16 back and forth. It can be formed, and weight reduction and low cost can be achieved. In the above embodiment, the slide sleeve 16 and the receiving ring 28 are provided separately. However, they may be integrated, and a ventilation hole for exhausting the air in the second air chamber 32 to the outside of the tool holder 17. The number and shape of 36, slits 37 and 38, through hole 39, and auxiliary hole 39a can also be appropriately changed. Next, the transmission mechanism 40 will be described. FIG.
, The shaft 25 meshing with the bevel gear 23
The motor shaft 9a is driven by ball bearings 41 and 42.
In a substantially central portion thereof, movement in the axial direction is restricted by washers 43 and 44 integral with the shaft 25, and the cylindrical portion 46 and a disk portion 47 provided around the cylindrical portion 46 are provided.
Is loosely fitted rotatably.
As shown in FIG. 6, symmetric slide grooves 25a, 25a are formed in the axial direction of the shaft 25. In each of the slide grooves 25a, 25a, a change key 48, 48 through which the washer 44 is passed, is provided. Each of the change keys 48, 48 is vertically slidably inserted between the upper and lower washers 43, 44 by the protrusions 49, 49 projecting upward. Further sleeve 45
In the upper half of the inner peripheral surface of the cylindrical portion 46, four notches 5
0, 50... Are formed, and change keys 48, 4
8, the projections 49, 49 are engaged with the two symmetrical cut portions 50, 50, so that the sleeve 45 and the shaft 2 are not engaged.
When the change keys 48 and 48 are integrally rotated, the projections 49 and 49 separate from the cut portions 50 and 50 at the lower limit positions of the change keys 48 and 48, and the rotation of the sleeve 45 is not transmitted to the shaft 25. , 48 are operated by vertically moving the change link 61 by gripping a connecting ring 51 mounted below the change keys 48, 48 in a groove 62 a of a holder portion 62 of a change link 61 in a switching mechanism 60 described later. It moves up and down according to. On the other hand, a helical gear 52 meshing with the motor shaft 9a is loosely fitted coaxially with the disc portion 47 of the sleeve 45, and eight connecting recesses 4 are radially formed on the outer periphery of the disc portion 47.
7a, 47a are provided on the inner periphery of the helical gear 52 with eight connecting recesses 52a, 52a, respectively. The connecting recesses 47a, 52a are aligned with each other to form radial clutch grooves 53, 53,. Are formed, and balls 54, 54,... Are inserted into the respective clutch grooves 53, 53,. A retaining ring 55 having a tapered portion 55a whose thickness decreases toward the outer periphery is loosely fitted on the lower surface of the cylindrical portion 46. The retaining ring 55 is locked at its upper end by a clip 56. It is urged downward by two disc springs 57 and 58 loosely fitted to the cylindrical portion 46. Therefore, the tapered portion 55a of the restraining ring 55 which is normally urged downward urges the ball 54 in the radial direction of the clutch groove 53, and the connection recess 47a, 52a is connected by the ball 54 at this position. As a result, the helical gear 52 and the sleeve 45 rotate integrally. That is, the pressing force of the disc springs 57 and 58 converted in the radial direction of the ball 54 by the pressing ring 55 limits the torque to the shaft 25. In the transmission mechanism 40 configured as described above, the change link 61 is located at the upper side and the projection 49,
When the helical gear 52 is rotated by the rotation of the motor shaft 9a in a state where 49 is locked to the cut portions 50, 50 of the sleeve 45, the pressing ring 55 pressed by the urging of the disc springs 57, 58 at this time, Since the balls 54 in the clutch grooves 53 are urged in the radial direction, and the helical gear 52 and the disk portion 47 of the sleeve 45 are integrated, the sleeve 45 rotates together with the helical gear 52, and the notch 5
The shafts 25 rotate via the change keys 48, 48 by the projections 49, 49 locked at 0, 50, transmitting rotation to the bevel gear 23, and rotating the tool holder 17 as described above. During this rotation operation, rotation resistance is generated on the tool holder 17 side, and the disc spring 57,
When the torque exceeds the set torque value due to the pressing of the ball 58, each ball 54 in the clutch groove 53 moves toward the rotation center side while slidingly contacting the tapered portion 55 a against the pressing of the pressing ring 55 (FIG. 7). Then, the connecting recess 4 in each clutch groove 53
As the unification of 7a and 52a is released, the rotation from the helical gear 52 is not transmitted to the disk portion 47 of the sleeve 45, and functions as an overload clutch. In particular, as a characteristic of the disc spring, the change in the amount of deflection decreases as the load approaches the elastic limit, but in the hammer drill 1 having the transmission mechanism 40, the disc springs 57 and 58 are provided.
The pressing force in the axial direction due to the taper portion 55a of the restraining ring 55 and the ball 54 of the clutch groove 53 is reduced by the disc portion 47.
, The pressing force to the restraining ring 55 can be set within the range of the load in which the change in the amount of deflection of the disc spring is small, and a stable set torque value can be obtained. Further, since there is no unevenness for each tool, it is not necessary to provide a screw member for adjusting the pressing force, and the assembling work is not required. The number and shape of the disc springs and the clutch grooves are not limited to the above-described embodiments, but can be appropriately increased or decreased or the shape can be changed. Of course, the transmission mechanism can be applied to other electric tools other than the hammer drill. Next, the switching mechanism 60 will be described. FIG.
8 and 9, the change link 61 includes a holder 62 that holds the change keys 48, 48, and a link 63 that is perpendicular to the holder 62.
To the long hole 63a provided in the front-back direction at the tip of the link portion 63,
An eccentric pin 67 projecting from the switching knob 65 penetrates. The switching knob 65 is rotatable with a cylindrical through portion 66 pivotally supported by an insertion hole 64 formed by the housing 2 and the crank housing 5.
A retaining portion 66a is formed on the peripheral edge of the tip. The penetrating portion 66 integrally connects an end portion of the rectangular cylindrical operation portion 68 having one end opened outside the housing 2 from an opening thereof, and a stopper 69 is loosely inserted into the operation portion 68. This is urged in the protruding direction by a compression spring 71, and a pin 70 projecting orthogonally to the stopper 69 is inserted into an arcuate slit 72 provided in the housing 2 to pull out from the operating portion 68. Stop has been made.
The slit 72 is provided with cuts 73a, 73b, 73c toward the center of the arc at the front and rear (0 degree and 180 degrees) and at an intermediate position (90 degrees) therebetween.
At the time of rotation of the pin 5, the pin 70 is guided by the slit 72. At each cut position, the pin 70 is locked by the bias of the compression spring 71, and can be stopped at the position (every 90 degrees). ing. On the other hand, on the outer periphery of the large diameter portion 20 of the tool holder 17, sliding teeth 5 formed on the inner periphery of the crank housing 5 are provided.
A pinion 74a, 74a,... meshing with a is formed on the outer periphery, and a lock ring 74 that can move back and forth is externally fitted. The lock ring 74 is urged rearward by a compression spring 78 disposed between the lock ring 74 and a bearing retainer 77 that is press-fitted into the housing cap 4, and has a square cutout 76 in a chamfer 75 on a side thereof. The switching knob 65 penetrates the long hole 63a of the change link 61 here.
Eccentric pin 67 is locked. On the inner periphery of the rear end of the lock ring 74, engaging teeth 79, 79, ... meshing with the front half of the engaging projection 21 of the tool holder 17 are provided. Therefore, here, with the rotation of the switching knob 65 every 90 degrees, the eccentric pin 67 moves the position in FIG.
Is shifted to the lower left position at 90 degrees (the pin 70 is locked at the notch 73b) and to the lower right position at 180 degrees (the pin 70 is locked at the notch 73c). But
The change link 61 moves up and down in accordance with the vertical movement of the eccentric pin 67 to move the change keys 48 and 48 held by the holder 62 up and down, and the lock ring 74 moves back and forth in accordance with the forward and backward movement. Engaging projection 21
Will be engaged and disengaged. In the switching mechanism 60 configured as described above, three modes can be selected by the rotational position of the switching knob 65. That is, as shown in FIG. 10, first, in FIG. 10A at the 0-degree position, the eccentric pin 67 at the upper left restricts the lock ring 74 at the position away from the engagement protrusion 21 and the change link 61 at the upper limit position. Change key 48,
Forty-eight projections 49, 49 are inserted into notches 50, 5
Lock to zero. Therefore, as described above, in addition to the striking operation by the piston 14, the striking element 31, and the intermediate element 33, the rotation of the shaft 25 causes the bevel gear 2 to rotate.
3. The rotation + impact mode in which the tool holder 17 rotates. Next, when the switching knob 65 is rotated 90 degrees from here, the eccentric pin 67 only moves to the lower left of the cutout portion 76 to maintain the separated position of the lock ring 74 as shown in FIG. Since the link 61 is moved to the lower limit position and the projections 49, 49 of the change keys 48, 48 are disengaged from the notches 50, 50 of the sleeve 45, the rotation of the sleeve 45 is not transmitted to the shaft 25, and the striking operation is obtained. However, the tool holder 17 is in a neutral (idling state) in which free rotation is possible. When the switching knob 65 is further rotated to the 180-degree position from here, the eccentric pin 67 moves to the lower right as shown in FIG. 21 to lock the rotation of the tool holder 17. At this time, since the change link 61 remains at the lower limit position, the rotation is not transmitted from the sleeve 45 to the shaft 25, and the striking mode is such that only striking operation is obtained. Therefore, when it is necessary to determine the angle of the bit 7 with a rag or the like, the tool holder 17 is set free using the neutral position shown in FIG.
Is adjusted to a predetermined angle, and then the switching knob 65 is set to the striking mode shown in FIG.
Is fixed, which is very convenient for filing work and the like. As described above, according to the switching mechanism 60, the switching of the rotation transmission to the shaft 25 and the switching of the rotation lock of the tool holder 17 are performed by separate members and also at different locations. Designs suitable for different loads applied to the lock ring 45 and the lock ring 74 can be made, and durability can be maintained. Further, even if one of the parts is damaged, only the replacement is required, which leads to suppression of cost increase. In particular, the mode switching can be performed rationally by linking the rotation of the eccentric pin 67 by the operation of the switching knob 65 with the lock ring 74, the change link 61, and the change key 48 even with a separately separated member. And good operability is obtained. In the above embodiment, the lock ring 74 as the lock member is moved in the axial direction of the tool holder 17 and the change key 48 as the key member is moved in the cross direction thereof to perform rotation transmission and lock switching. Depending on the form of the transmission mechanism 40, a form in which both are moved in the axial direction and switched can be adopted. As described above, according to the present invention, the biasing force of the disc spring generated in the axial direction of the rotating shaft is converted into the pressing force in the radial direction of the ball by the restraining member, whereby the ball is stabilized. With the applied pressing force, the ball and the concave portion can be locked, and the setting of the torque limit can be easily performed without unevenness.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view of a hammer drill. FIG. 2 is an explanatory sectional view of a cylinder and a receiving ring at a position of an air chamber. FIG. 3 is an explanatory cross-sectional view of a cylinder, a slide sleeve, and a tool holder at a position of a second air chamber. FIG. 4 is an operation explanatory diagram at the time of idling. FIG. 5 is an explanatory diagram of a transmission mechanism. FIG. 6 is an explanatory diagram of a transmission mechanism. FIG. 7 is an explanatory diagram of a transmission mechanism. FIG. 8 is an explanatory diagram of a switching mechanism. FIG. 9 is an explanatory diagram of a switching mechanism. FIG. 10A is an operation explanatory view of a switching mechanism. (B) It is operation explanatory drawing of a switching mechanism. (C) It is operation explanatory drawing of a switching mechanism. [Description of References] 1. hammer drill, 2. housing, 3. operating mechanism, 5. crank housing, 6. gear housing, 7. bit, 9. motor, 10. crank shaft, 14 · · piston, 15 · · cylinder, 16 ·
・ Slide sleeve, 17 ・ ・ Tool holder, 21 ・ ・
Engaging projections, 23 bevel gears, 24 engaging teeth, 25
..Shafts, 30.Air chambers, 31.Blowers, 32
..The second air chamber, 33..meson, 40..transmission mechanism,
45 sleeve, 48 change key, 51 connecting ring, 52 helical gear, 53 clutch groove, 54 ball, 55 ring, 57, 58
..Plate spring, 60..switching mechanism, 61..change link, 65..switching knob, 67..eccentric pin, 74 ..
Lock ring.

Continuation of the front page (58) Field surveyed (Int.Cl. ⁷ , DB name) B25D 11/12 B25D 16/00

Claims (1)

(57) [Claim 1] A gear rotating by rotation transmission from a motor side, and a rotating shaft for loosely inserting the gear coaxially and transmitting rotation to a bit side, wherein the rotation Ball on the shaft side , gear
On the side, with its ball comprises a lockable recess, a torque transmission mechanism of the power tool provided with urging means for pressing the balls into the concave side, to the rotary shaft side, a cylindrical portion, Around the tube,
A sleeve comprising a disk portion having a radial connection recess
Is provided, and the gear is loosely fitted coaxially to the disk portion of the sleeve,
The clutch formed by the coupling recess of the sleeve and the recess of the gear
While inserting the ball into the switch groove, the biasing means, the cylindrical portion
Is loosely fitted, the ball abuts a ball-side and restrained member movable with a tapered portion in the axial direction of the cylindrical portion for urging the member suppressing provided to the cylindrical portion to the engagement direction of said recess A torque transmitting mechanism for an electric tool, comprising: a disc spring that presses against the power tool.