JP2011189428A - Torque driver - Google Patents

Abstract

An object of the present invention is to reduce the number of components while supporting high torque, making assembly easy and inexpensive, and setting a plurality of torque states.
A jacket, a cam barrel, a bit drive shaft, a fixed clutch member that rotates integrally with the bit drive shaft, a movable clutch member that rotates, a spring seat, a spring seat, and a movable seat. A spring 9 that applies torque to the displacement of the movable clutch member 7 to the non-engagement position with respect to the fixed clutch member 6 according to the distance of the clutch member 7, and is a passive extending radially from the movable clutch member 7 and the spring seat 8. When the shafts 14 and 15 are constrained in the rotation direction by the rotation-preventing groove 13 of the outer jacket 1, the cam windows 11 and 12 of the cam cylinder 3 are moved during relative rotation with the cam cylinder 3 with the bit drive shaft 5 of the outer jacket 1. The torque is adjusted by the spring 9 by moving in the circumferential direction and changing the distance between the movable clutch member 7 and the spring seat 8 into a plurality of distances.
[Selection] Figure 1

Description

  The present invention relates to a torque driver, and more particularly, to a torque driver having at least a torque limit function in which a clutch operates when a predetermined torque value is reached and screw fastening is impossible.

  Most of these torque drivers change the torque value continuously by screw operation, but in order to change it stepwise such as 1.5 times or 2 times, the operation amount is large and inconvenient to use.

  On the other hand, in Patent Document 1 below, among the toggle balls composed of three balls that are in triangular contact with each other so as to exert a toggle function in the axial direction, one receiving ball in the center in the axial direction is provided. A ball holding ring that can be slid in the axial direction, received from the outside, and a rotating shaft that fits at a fixed position inside the ball holding ring and has a circumferential cam in contact with two passive balls on both axial sides of the three balls And rotating the rotating shaft with respect to the ball holding ring and the outer jacket, thereby changing the amount of radial cam thrust to the outer side of the toggle ball and expanding the toggle ball in the axial direction. A technology is disclosed in which the region is repeatedly expanded and contracted, and the torque value by the spring is linearly changed at a certain angle by the expansion and contraction at this time. It is a suitable opening and closing operation of the air tool.

  Patent Document 2 below discloses a torque limit function for high torque, in which the torque value of the spring when the clutch is disengaged changes when the amount of clutch engagement is adjusted by the relative rotation of the fixed and movable cam pair. An electric screwdriver that exhibits the above is disclosed.

JP 63-107572 A Japanese Patent Publication No. 8-5016 Japanese National Patent Publication No. 10-502730

  However, the technique described in Patent Document 1 is not suitable for a torque driver that requires a high torque such as 1.6 and 3 Newton meters (N · m) in addition to the fine parts, many parts, and difficulty in assembling.

  In addition, the device described in Patent Document 2 adjusts the torque value by a continuous shift of the fixed and movable cam pair due to the relative rotation between the pressure contact slopes. Each requires a dedicated mechanism that stabilizes the position. Including this mechanism, the overall number of parts is large and the assembly is expensive.

  An object of the present invention is to provide a torque driver capable of setting a plurality of torque states with a small number of parts, easy assembly, and low cost while accommodating high torque in view of the above-mentioned problems. To do.

  In order to solve the above-described problems, a torque driver according to the present invention includes a mantle, a cam cylinder that is inserted into the mantle so as to be rotated from one end side of the mantle, is prevented from being detached, and is mounted. In this cam cylinder, a bit drive shaft that is inserted in the axial direction from the rear end opposite to the front end having the bit holder and supported so as to be received and rotated at a predetermined position, and can rotate integrally with the bit drive shaft The fixed clutch member fitted in this way and received at a fixed position from the back portion and the fixed clutch member fitted so that it can rotate on the bit drive shaft, the mutual teeth mesh with each other by relative rotation with the fixed clutch member, and the rotation of the outer mantle becomes the bit drive shaft. A movable clutch member that can move in the axial direction between an engaging position for transmission and a non-engaging position that disengages, and a movable clutch member that is rotatably fitted to the bit drive shaft and faces the movable clutch member Mounted around the bit drive shaft between the sleeve and the spring seat and the movable clutch member, and fixed according to the distance between the spring seat and the movable clutch member, the movable clutch member is moved from the engaged position to the non-engaged position. And a movable clutch member and a spring seat extending in a radial direction from the outer periphery, and provided with cam windows for distance adjustment provided in two axial directions on the cam cylinder. It has a passive shaft that penetrates individually and engages with an axial detent groove that is open at least on the insertion side of the cam cylinder on the inner surface of the outer jacket so as to be able to advance and retract in the axial direction. The movable clutch member having the above and the spring seat are prevented from rotating with respect to the outer jacket, and each cam window of the cam cylinder is provided with the movable clutch member of the outer jacket and the cam cylinder with the spring seat. By relative rotation with Depending on the circumferential displacement of the engaging position of the shaft, by varying the movable clutch member and the distance of the spring seats on the plurality is characterized by having a cam surface for the torque adjustment.

  In such a configuration, when the outer jacket is rotated, the movable clutch member that rotates around the outer jacket and the engagement between the movable clutch member and the fixed clutch member are used to respond to the distance between the movable clutch member and the spring seat. The torque is transmitted to the fixed clutch member and the bit drive shaft in which the rotation is prevented within a torque value corresponding to the degree of compression of the spring between them. As a result, the bit mounted on the bit drive shaft can be screwed and unscrewed. On the other hand, when the rotation of the mantle exceeds the torque value, the movable clutch member is engaged with the fixed clutch member against the spring against the rotational resistance of the fixed clutch member due to the rotational load generated on the bit drive shaft. It retreats to the non-engagement position where the mesh is disengaged from the engagement position. As a result, the mantle runs idle with respect to the bit drive shaft and exhibits a torque limit function.

  Further, each cam according to the circumferential displacement of the position of engagement of the cam cylinder with the passive shaft with respect to each cam window by the relative rotation operation from the outside with the movable clutch member of the outer jacket and the cam cylinder with the spring seat. By changing the distance between the movable clutch member and the spring seat between the cam surfaces of the windows, the torque value by the spring can be switched to a plurality.

  In addition, since the anti-rotation groove on the outer jacket is open to the insertion side of the cam cylinder, the bit drive shaft is equipped with a fixed, movable clutch member, spring, and spring seat, and the intermediate assembly combined with the cam cylinder is movable By aligning the passive shaft of the clutch member and the spring seat with the non-rotating groove, the passive shaft can be inserted into the outer jacket while being inserted into the non-rotating groove, and the above functions can be achieved simply by retaining at the insertion position. To do.

  In the above description, the plurality of torque adjustments may include a function lock state that disables a torque limit function between the fixed and movable clutch members.

  In such a configuration, in addition to the above, it is possible to perform screw tightening and unscrewing without a torque limit function by torque adjustment.

  In the above, the cam cylinder may further have a notch that opens at the insertion side end portion at least in the circumferential direction of the cam window on the insertion side to the mantle.

  In such a configuration, in addition to the above, the intermediate assembly further releases the corresponding passive shaft from the restraint by the cam window on the insertion side, so that the spring does not work between the spring seat and the movable clutch member. In the combined state, the passive shaft that has been released while being inserted into the jacket is accompanied by compression of the spring due to the approach between the spring seat and the movable clutch member, and the corresponding cam window is notched through the notch. The passive shaft can be moved to the torque setting portion of the cam window by simply rotating the cam tube with respect to the outer sleeve by relative rotation with the cam barrel with the bit drive shaft of the outer sleeve.

  According to the torque driver of the present invention, the rotation of the mantle is movable, the meshed holding by the spring with the fixed clutch member is transmitted to the bit drive shaft within the torque value corresponding to the degree of compression of the spring, and when the torque value is exceeded, Although the engagement between the fixed clutch members is disengaged and the outer shell rotates freely with respect to the bit drive shaft, the torque limit function can be exerted. In particular, the spring for each cam window of the cam cylinder is operated by the relative rotation operation from the outside of the outer jacket and the cam cylinder. The engagement position of the seat and the movable clutch member with the passive shaft is moved to different torque setting portions in the circumferential direction of the cam surface of each cam window, and the torque value can be easily switched to a plurality of values. In addition, the bit drive shaft is equipped with a fixed, movable clutch member, spring, and spring seat, assembled in an intermediate assembly combined with a cam cylinder, and the movable clutch member and the passive shaft of the spring seat are used as a detent groove in the outer jacket. By simply aligning, inserting into this, inserting it into the outer jacket, and retaining it at this insertion position, it can be easily assembled to exhibit the above functions.

It is the side view which looked at the half part of the torque driver which concerns on embodiment of this invention in cross section, and the side view of a bit. FIG. 4 is a side view showing a mantle of the torque driver, a side view of the half section as seen from a cross section, and an end view as seen from the cam cylinder insertion side. It is each side view which looked at the cam cylinder of the torque driver from three directions. It is the perspective view which exploded and looked at the same torque driver.

  The torque driver according to the embodiment of the present invention will be described with reference to FIGS. The following description is a specific example of the present invention and does not limit the matters described in the claims.

  As shown in FIG. 1 (a), a torque driver 100 of the present embodiment shown in the figure is inserted into a mantle 1 so that it can be rotated from the one end side of the mantle 1 so that it can be rotated. A cam cylinder 3 that is secured by a retaining ring 2 or the like, and a known bit mounting portion 4 for mounting the bit 51 shown in FIG. The bit drive shaft 5 is inserted in the axial direction from the rear end side opposite to the front end and received at a predetermined position. Specifically, the bit drive shaft 5 is supported by the thrust bearing surface 3b facing the opposite insertion side so as to be rotatable. And a fixed clutch which is fitted to the bit drive shaft 5 so as to be integrally rotated by fitting the square shaft 5a and the square hole 6a, and is received at a fixed position from the back by a spacer 20 with a double nut 10 or the like. Can rotate to member 6 and bit drive shaft 5 The teeth 6b and 7b are engaged with each other by the relative rotation with the fixed clutch member 6, and the rotation of the outer cannula 1 is transmitted to the bit drive shaft 5 and retracted to the left in FIG. A movable clutch member 7 that can move in the axial direction between the disengagement position where the meshing is disengaged, a spring seat 8 that is fitted so as to be able to rotate on the bit drive shaft 5 and faces the movable clutch member 7, and this spring seat 8 and the movable clutch member 7 are mounted around the bit drive shaft 5 and fixed according to the distance between the spring seat 8 and the movable clutch member 7, and the movable clutch members 6 and 7 are moved from the engaged position to the non-engaged position. And a spring 9 for applying a torque necessary for displacement.

  Further, the movable clutch member 7 and the spring seat 8 extend in the radial direction from the outer periphery, individually penetrate the cam windows 11 and 12 for distance adjustment provided in two axial directions in the cam cylinder 3, and Passive shafts 14 and 15 are engaged on the inner surface so as to be able to advance and retreat in an axial direction in an axial rotation-preventing groove 13 opened at least on the insertion side of the cam cylinder 3. Each of the passive shafts 14 and 15 is engaged with the rotation-preventing groove 13 so that the movable clutch member 7 and the spring seat 8 having these are prevented from rotating with respect to the outer jacket 1, The cam windows 11 and 12 are movable according to the circumferential displacement of the engagement position with the passive shafts 14 and 15 due to relative rotation of the outer jacket 1 with the cam cylinder 3 with the movable clutch member 7 and the spring seat 8. Cam surfaces 11a and 12a for adjusting the torque by changing the distance between the clutch member 7 and the spring seat 8 to a plurality are provided.

  As a result, when the outer jacket 1 is rotated, the distance between the movable clutch member 7 and the spring seat 8 through the movable clutch member 7 and the engagement between the movable clutch member 7 and the fixed clutch member 6 is provided. Accordingly, the torque is transmitted to the fixed clutch member 6 and the bit drive shaft 5 in which the rotation is prevented within a torque value corresponding to the compression degree of the spring between them. As a result, the bit 51 attached to the bit drive shaft 5 can be screwed and unscrewed. On the other hand, when the rotation of the outer jacket 1 exceeds the torque value, the movable clutch member 7 resists the spring 9 against the rotational resistance on the fixed clutch member 6 side due to the rotational load generated on the bit drive shaft 5, and the fixed clutch member. 6 is retracted from the engaged position engaged with 6 to the disengaged position where the engagement is released. As a result, the mantle 1 becomes idle with respect to the bit drive shaft 5 and exhibits a torque limit function.

  Further, the camshaft 3 with the movable clutch member 7 and the spring seat 8 of the outer jacket 1 is engaged with the passive shafts 14 and 15 with respect to the cam windows 11 and 12 of the cam barrel 3 by external relative rotation operation. The torque value by the spring 9 can be switched to a plurality of values by changing the distance between the movable clutch member 7 and the spring seat 8 between the cam surfaces 11a and 12a of the cam windows 11 and 12 in accordance with the circumferential displacement of the position.

  More specifically, the thrust receiving surface 3 b of the cam cylinder 3 is formed with a bearing 3 c that receives the bit drive shaft 5 in the radial direction, and the movable clutch member 7 and the spring that are held on the inner periphery of the cam shaft 3. The seat 8 also serves as a bearing for receiving the bit drive shaft 5 in the radial direction, and the fixed clutch member 6 is also received by the inner periphery of the cam cylinder 3 to rotate integrally with the bit section coaxial 5. I am doing. Further, as shown in FIGS. 1 (a), 2 (b) and 2 (c), the anti-rotation groove 13 of the outer jacket is opened to the insertion side of the cam cylinder 3, so that it is fixed to the bit drive shaft 5. The intermediate assembly 52 equipped with the movable clutch members 6, 7, the spring 9, and the spring seat 8 and combined with the cam cylinder 3 is arranged in the circumferential direction with the passive shafts 14, 15 of the movable clutch member 7 and the spring seat 8. If they are aligned with each other, the passive shafts 14 and 15 can be inserted into the outer sheath 1 while being inserted into the anti-rotation groove 13, and the above-described functions can be exhibited only by retaining at the insertion position.

  Accordingly, the rotation of the outer jacket 1 is fixed, the meshing and holding of the movable clutch members 6 and 7 by the spring 9 is transmitted to the bit drive shaft 5 within a torque value commensurate with the degree of compression of the spring 9, and is fixed when the torque value is exceeded. The engagement between the movable clutch members 6 and 7 is disengaged, and the torque limit function is achieved in which the outer jacket 1 rotates idly with respect to the bit drive shaft 5. FIG. 3 shows the positions of engagement of the spring seat 8 and the movable clutch member 7 with the passive shafts 14 and 15 with respect to the cam windows 11 and 12 of the cylinder 3 in the circumferential direction of the cam surfaces 11a and 12a of the cam windows 11 and 12, respectively. The torque values can be easily switched to a plurality by moving in the circumferential direction between the plurality of torque setting units 11a1 to 11a3 and 12a1 to 12a3. For this switching, operation portions 53 and 54 made of an elastic friction member are mounted on the outer periphery of the rear portion of the outer sleeve 1 and the outer periphery of the tip portion exposed from the outer sleeve 1 of the cam cylinder 3. Note that the outer periphery of the outer sleeve 1, the cam barrel 3, and the bit mounting portion 4 is made of an insulating material including the operation portions 53 and 54 in order to insulate during the electric rotation operation.

  In addition, the bit drive shaft 5 is provided with fixed and movable clutch members 6 and 7, a spring 9 and a spring seat 8, and is assembled to the intermediate assembly 52 combined with the cam cylinder 3, so that the movable clutch member 7 and the spring seat 8 are assembled. The passive shafts 14 and 15 are aligned with the anti-rotation groove 13 of the outer cannula 1 and inserted into the outer cannula 1 while being inserted into the groove. The above functions can be exhibited. Specifically, the C-type retaining ring 2 is elastically fitted in an annular groove 21 formed at the rear end of the cam cylinder 3, and the C-type retaining ring 2 is placed on the inner periphery of the outer end of the outer sleeve 1. Make contact. At this time, the spring acting between the cam surface 12a of the cam window 12 of the cam cylinder 3 that is prevented from being detached by the outer sheath 1 and the double nut 10 that receives the fixed clutch member 6 from the back in the cam cylinder 3 or the like. The repulsive force of 9 stabilizes the intermediate assembly in a functional state.

  Here, the plurality of torque adjustments include a function lock state in which the torque limit function between the fixed and movable clutch members 6 and 7 is disabled, and screw tightening and unscrewing without the torque limit function can be performed by torque adjustment. . In the illustrated example, the torque setting units 11a3 and 12a3 in FIG. 3 correspond to the lock position, the torque setting units 11a2 and 12a2 correspond to the torque value 3N · m setting position, and the torque setting units 11a1 and 12a1 have a torque value of 1.6N. -Supports m set value. In order to display this stepwise setting state externally, an index 55 is provided on the flange 3a provided to face the end surface on the front end side of the mantle 1 of the cam barrel 3, as shown in FIGS. A torque setting state display portion 56 that is provided by striking and facing the index 55 at each torque setting position of the jacket 1 relative to the cam cylinder 3 is provided.

  The cam tube 3 has a notch 57 that opens at least the cam window 11 on the insertion side to the mantle 1 at the end portion on the side opposite to the insertion side, as shown in FIGS. 3B and 3C. It is assumed that As a result, the intermediate assembly 52 releases the corresponding passive shaft 14 from the restraint by the cam window 11 on the insertion side to the mantle 1, and the spring 9 does not move between the spring seat 8 and the movable clutch member 7. In the rough combined state, the passive shaft 14 released in the middle of being inserted into the jacket 1 is compressed with the spring 9 due to the approach between the spring seat 8 and the movable clutch member 7, and the corresponding cam window 11 and through the notch 57, the passive shafts 14 and 15 are moved to the torque setting portions 11a1 to 11a3 and 11a1 to 11a3 of the cam windows 11 and 12 by relative rotation with the cam cylinder 3 with the bit drive shaft 5 of the mantle 1. Be made. The passive shafts 14 and 15 are provided at two locations on the diameter line of the movable clutch member 7 and the spring seat 8 so that the setting state of the torque value is stabilized, and the corresponding cam windows 11 and 12 are also arranged in the circumferential direction of the cam cylinder 3. It is provided in the place.

  Here, since the cam window 12 does not have the notch 57 like the cam window 11, it is necessary to assemble the spring seat 8 before passing the drive shaft 5 when assembling to the intermediate assembly 52. For this purpose, a loading / unloading port 12b extending in the axial direction from the torque setting portion 12a3 of the cam window 12 is provided. With this insertion / removal port 12b, the spring seat 8 can be taken in / out with respect to the cam cylinder 3 with a change in direction with respect to the cam surface 12a, the spring seat 8 is assembled before the torque drive shaft 5 is inserted, and the torque drive shaft 5 is removed. The subsequent spring seat 8 can be removed. In the illustrated example, the notch 57 corresponds to the torque setting portions 11a1 and 12a1 that minimize the set torque value, and the reaction force by the spring 9 when the intermediate assembly 52 is inserted into the outer mantle 1 to prevent it from coming off. As a result, the assembling work becomes easy, and after the assembling, the setting torque can be switched so as to increase in order, and it can be switched back again, eliminating the operation that greatly changes the setting step of the torque value, making the switching operation easier. . The notch 57 makes it impossible to provide the torque setting portion 11a1 that should be provided on the cam surface 11a, but there is no problem. This is because the spring force of the spring 9 causes the bit drive shaft 5 to thrust the thrust receiving surface 3b via the double nut 10 in an environment in which the cam cylinder 3 is prevented from being detached from the outer sleeve 1 at the end of insertion of the intermediate assembly 52 into the outer sleeve 1. The bit drive shaft 5 is stabilized in the cam barrel 3 by the action of being pressed against the cam cylinder 3, and the spring 9 is fixed around the stable bit drive shaft 5 by the double nut 10 and fixed and movable clutch members 6 and 7. This is because the initial torque value setting position is stabilized with respect to the spring seat 8 whose position is restricted by the cam surface 12a. In order to prevent the cam cylinder 3 from being removed by the C-type retaining ring 2 or the like, an opening 57 for operation as shown in FIGS. The lid 58 made of metal is attached so as to be detachable. In the illustrated example, a torque driver to be manually turned is shown, and the outer jacket 1 is so-called a tool body, but an electric torque driver can be configured by connecting the outer jacket 1 to an electric mechanism.

DESCRIPTION OF SYMBOLS 1 Outer jacket 2 C type retaining ring 3 Cam cylinder 4 Bit mounting part 5 Bit drive shaft 6 Fixed clutch member 7 Movable clutch member 8 Spring seat 9 Spring 10 Double nuts 11 and 12 Cam window 11a, 12a Cam surface 13 Anti-rotation groove 14 , 15 Passive shaft 53, 54 Operation unit

Claims (3)

  The outer sleeve, and a cam cylinder inserted into the outer jacket so as to be able to rotate while leaving a part from the one end side thereof, are prevented from being detached, and the tip having the bit bit holder in the cam cylinder is opposite. A bit driving shaft that is inserted in the axial direction from the rear end side and supported so as to be able to receive and rotate, and a fixed clutch member that is fitted so as to be able to rotate integrally with this bit driving shaft and is received at a fixed position from the back, Between the engagement position where the teeth are engaged with each other by rotation relative to the fixed clutch member so as to be able to rotate on the bit drive shaft and the rotation of the mantle is transmitted to the bit drive shaft, and between the non-engagement position where the engagement is released A movable clutch member that can move in the axial direction, a spring seat that is rotatably fitted to the bit drive shaft and faces the movable clutch member, and a bit drive shaft between the spring seat and the movable clutch member. And a spring that applies a torque necessary to displace the movable clutch member from the engaged position to the non-engaged position. The member and the spring seat extend in the radial direction from the outer periphery, individually penetrate the distance adjusting cam windows provided in two axial directions in the cam cylinder, and are opened at least on the cam cylinder insertion side on the inner surface of the outer jacket. Each of the passive shafts engages with the non-rotating groove so that the movable clutch member and the spring seat are covered with the outer sleeve by engaging with the non-rotating groove. Each cam window of the cam barrel is subject to circumferential displacement of the engagement position with the passive shaft due to relative rotation with the movable clutch member of the outer jacket and the cam barrel with the spring seat. Depending on the movable clutch member and The distance of the spring Zama plurality varied torque driver, characterized in that it has a cam surface for the torque adjustment.   The torque driver according to claim 1, wherein the plurality of torque adjustments include a function lock state that disables a torque limit function between the fixed and movable clutch members.   The torque driver according to any one of claims 1 and 2, wherein the cam cylinder has a notch that opens at least a part of a cam window on the insertion side to the mantle 1 in the circumferential direction at an end portion on the insertion side.

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