JP6746141B2 - Mainspring type variable speed drive - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a mainspring type variable speed drive device that can be used mainly as a power source for a work cart, a belt conveyor, etc.

Conventionally, there is a mainspring drive device that can be used as a power source for a work trolley (for example, Patent Document 1).

WO2017/047370A1

However, the mainspring drive device described in Patent Document 1 has a problem that it takes time and effort to adjust the number of rotations (rotation speed) of the output shaft per unit time during use.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a spring type variable speed drive device capable of easily adjusting the number of rotations (the number of rotations) of the output shaft per unit time.

In order to solve the above problems, the present invention provides
A casing,
An output shaft that penetrates the casing and is attached to the casing so as to be relatively rotatable,
A one-way clutch externally fitted to the output shaft in the casing,
A mainspring that is housed in the casing, has a radially inner end fixed to an outer ring of the one-way clutch, and is tightened when the output shaft rotates in the torque transmission direction of the one-way clutch,
A damper holding part which is fixed to the casing integrally with the casing while being separated from the casing in the central axis direction of the output shaft on the outside of the casing,
A rotating shaft disposed between the damper holding portion and the casing in a central axis direction of the output shaft is detachably held by the damper holding portion, and the rotating shaft is centered on the central axis of the rotating shaft. A rotary damper that exerts braking force against the torque to rotate,
A mainspring type variable speed drive device having a torque transmission mechanism which is arranged between the damper holding portion and the casing in a central axis direction of the output shaft and which transmits a torque of the output shaft to the rotary shaft.

According to the present invention, it is possible to provide a mainspring type variable speed drive device capable of easily adjusting the number of rotations (the number of rotations) of the output shaft per unit time.

FIG. 1 is a perspective view of a mainspring type variable speed drive device according to an embodiment of the present application as viewed from a rotation speed adjustment mechanism side. FIG. 2 is a perspective view of the mainspring type variable speed drive device according to the embodiment of the present application as seen from the mainspring type drive device side. FIG. 3 is a side view of the mainspring type variable speed drive device according to the embodiment of the present application as seen from a direction perpendicular to the central axis. FIG. 4 is a side view of the mainspring type variable speed drive device according to the embodiment of the present application as viewed from the rotation speed adjusting mechanism side in the central axis direction. FIG. 5 is a cross-sectional view taken along the line AA shown in FIG. 4 of the mainspring type variable speed drive device according to the embodiment of the present application. FIG. 6 is a cross-sectional view taken along the line AB of FIG. 4 of the mainspring variable speed drive device according to the embodiment of the present application. FIG. 7 is a side view of the mainspring type variable speed drive device according to the embodiment of the present application as seen from the mainspring type drive device side in the central axis direction. FIG. 8 is a side view of the mainspring type variable drive device according to the embodiment of the present application viewed from the mainspring type drive device side in the central axis direction with a part of the casing removed. FIG. 9 is an enlarged cross-sectional view of the mainspring drive device according to the embodiment of the present application.

Hereinafter, embodiments of the present application will be described with reference to the drawings. FIG. 1 is a perspective view of a mainspring type variable speed drive device 1000 according to an embodiment of the present application as viewed from a rotation speed adjustment mechanism 100 side. FIG. 2 is a perspective view of the mainspring variable speed drive device 1000 according to the embodiment of the present application as seen from the mainspring drive device 200 side.

As shown in FIG. 2, the mainspring variable speed drive device 1000 according to the present embodiment includes a rotation speed adjustment mechanism 100 and a mainspring drive device 200. In the mainspring type variable speed drive device 1000, the rotation speed of the output shaft 203 of the mainspring drive device 200 can be adjusted by the rotation speed adjustment mechanism 100.

FIG. 3 is a side view of the mainspring type variable speed drive device 1000 according to the embodiment of the present application as seen from a direction perpendicular to the central axis. FIG. 4 is a side view of the mainspring type variable speed drive device 1000 according to the embodiment of the present application as viewed from the rotation speed adjusting mechanism 100 side in the central axis direction. FIG. 5 is a cross-sectional view of the mainspring variable speed drive device 1000 according to the embodiment of the present application, taken along the line AA shown in FIG. FIG. 6 is a sectional view taken along the line AB of FIG. 4 of the mainspring variable speed drive apparatus 1000 according to the embodiment of the present application.

As shown in FIG. 5, the mainspring drive device 200 has a casing 201, a mainspring 202, and an output shaft 203. The mainspring 202 is housed in the casing 201. The output shaft 203 has an axially intermediate portion arranged in the casing 201. Key grooves are formed at both ends of the output shaft 203 along the central axis direction of the output shaft 203, and the keys 205a and 205b are fitted in the key grooves. The movement of the output shaft 203 in the direction of the central axis of the output shaft 203 is restricted by the first gear 101 a fitted and fixed to the output shaft 203 and the set collar 204. By rotating the output shaft 203 in a predetermined direction, the mainspring 202 is elastically deformed and energy for generating a driving force can be stored. When the output shaft 203 is released with the mainspring 202 wound up, the mainspring 202 elastically returns and the output shaft 203 rotates. Details of the mainspring drive device 200 will be described later.

The rotation speed adjustment mechanism 100 includes a torque transmission mechanism 101, a damper holder 102, a first rotary damper 103, and a second rotary damper 104. The torque of the output shaft 203 is transmitted to the first and second rotary dampers 103 and 104 by the torque transmission mechanism 101. The first and second rotary dampers 103 and 104 serve as resistance against the torque of the output shaft 203, and play a role of reducing the rotation speed and the torque of the output shaft 203.

The torque transmission mechanism 101 has a first gear 101a, a second gear 101b, and a third gear 101c. The first gear 101a is externally fitted and fixed to the output shaft 203 between the damper holder 102 and the mainspring drive device 200. The second gear 101b is externally fitted and fixed to the rotary shaft 103a of the first rotary damper 103, and meshes with the first gear 101a. The third gear 101c is externally fitted and fixed to the rotary shaft 104a of the second rotary damper 104, and meshes with the first gear 101a. The torque transmission mechanism 101 is not limited to a gear and may be any one that transmits torque from the output shaft 203 to the rotary shafts 103a and 104a of the rotary dampers 103 and 104.

As shown in FIG. 1, the damper holder 102 is made of a circular plate member. The damper holding part 102 is fixed to the casing 201 of the mainspring drive device 200 by four columns 110 arranged at substantially equal intervals in the circumferential direction. As shown in FIG. 3, the damper holder 102 is axially separated from the mainspring drive unit 200, and the torque transmission mechanism 101 is arranged between the damper holder 102 and the mainspring drive unit 200.

As shown in FIG. 4, the damper holding portion 102 is provided with an output shaft hole portion 102a formed in the central portion, a holding hole portion 102b, and a screw hole portion 102c. The output shaft hole 102a is formed in a circular shape penetrating the center of the damper holding portion 102. As shown in FIG. 5, the output shaft hole portion 102a allows the cylindrical portion of the first gear 101a and the output shaft 203 to pass therethrough. As shown in FIG. 4, four holding holes 102b are formed around the output shaft hole 102a at a substantially radial distance from the output shaft hole 102a at a predetermined distance in the circumferential direction. There is. First and second rotary dampers 103 and 104 are inserted into the holding hole portion 102b. Two screw holes 102c are provided adjacent to each holding hole 102b. The first and second rotary dampers 103 and 104 are fixed to the damper holding portion 102 by a screw 112 that passes through a screw hole portion 102c. The damper holder 102 may have any structure as long as it can detachably hold the rotary damper, and may have only one rotary damper.

As the first and second rotary dampers 103 and 104, commercially available ones can be used. The first and second rotary dampers 103 and 104 have rotating shafts 103a and 104a, and exert a braking force with respect to the torque that rotates the rotating shafts 103a and 104a about the central axis of the rotating shafts 103a and 104a. .. Although two rotary dampers 103 and 104 are arranged in this embodiment, the user can select the number of rotary dampers from 0 to 4. By increasing the number of rotary dampers, the rotation speed and torque of the output shaft 203 can be reduced. Further, the rotational speed of the output shaft 203 can be finely adjusted by using a plurality of rotary dampers having different braking forces in combination.

According to the present embodiment described above, it is possible to provide the mainspring type variable speed drive device 1000 capable of easily adjusting the number of revolutions (the number of revolutions) of the output shaft 203 per unit time. It is also conceivable to use a gear reducer to reduce the rotation speed of the output shaft 203. However, unlike the electric motor or the like, in the mainspring movable speed change drive device 1000, when the mainspring 202 elastically returns and all the stored energy is released, the output shaft 203 is not energized. Therefore, the use of the gear reducer reduces the number of times the driven object is rotated. For example, when the wheels of the work carriage are driven by using the gear reducer, the traveling distance becomes shorter according to the gear ratio of the gear reducer. Therefore, in the present embodiment, the rotary dampers 103 and 104 are used so that the number of times the driven object is rotated is not reduced.

FIG. 7 is a side view of the mainspring drive device 200 according to the present embodiment as viewed in the central axis direction. FIG. 8 is a side view of the mainspring drive device 200 as viewed in the central axis direction with a part of the casing 201 according to the present embodiment removed.

As shown in FIG. 8, a mainspring (spring) 202 is housed inside the casing 201 around the output shaft 203. The casing 201 has a peripheral wall 201b that surrounds the mainspring 202 radially outside the mainspring 202.

The outer end of the mainspring 202 in the radial direction is bent outward in the radial direction, forms a convex portion 202a protruding outward in the radial direction, and is folded inward. Eight recesses 201c, which are recessed in an arc shape toward the outer side in the radial direction, are formed on the inner side in the radial direction of the peripheral wall 201b at substantially equal intervals in the circumferential direction. The radially outer portion of the convex portion 202a is fitted into and engaged with the concave portion 201c. The convex portion 202a may be formed by deforming the end portion of the mainspring 202 as described above, but a member formed separately from the mainspring 202 may be attached.

FIG. 9 is a cross-sectional view taken along the line CC of FIG. 7 of the mainspring drive device 200 according to this embodiment.

The radially inner end of the mainspring 202 is fixed to a cylindrical bush 210 through which the output shaft 203 is passed. The casing 201 is integrally formed with annular portions 201f and 201g that surround both axial ends of the bush 210 from the outside in the radial direction. The annular portions 201f and 201g limit the movement of the bush 210 in the radial direction. Note that the annular portions 201f and 201g are sufficient as long as they limit the radial movement of the bush 210, and may have a shape other than the annular shape. For example, the annular portions 201f and 201g can be replaced with C-shaped portions. Further, the portion that restricts the radial movement of the bush 210 may be formed separately from the casing 201.

By providing the annular portions 201f and 201g, the through hole through which the output shaft 203 is passed can be maintained even when the output shaft 203 is removed. If the annular portions 201f and 201g are not provided, if the output shaft 203 is detached from the mainspring drive device 200, the bush 210 is supported only by the mainspring 202, and therefore the bush 210 is elastically deformed so that the bush 210 is not supported. It is displaced, and it becomes difficult to insert the output shaft 203. By providing the annular portions 201f and 201g, the position of the bush 210 is maintained even if the output shaft 203 is removed from the mainspring drive device 200, so that the output shaft 203 can be easily attached.

Annular transparent plates 218 and 219 are arranged on the outer sides of the annular portions 201f and 201g in the radial direction, respectively. The transparent plates 218 and 219 prevent the entry of fingers, foreign matter, etc. into the mainspring drive device 200 while allowing the inside of the mainspring drive device 200 to be observed through the opening 201d of the casing 201. The transparent plates 218 and 219 can be formed of plastic, glass, or the like.

A first needle bearing 211, a one-way clutch 212, and a second needle bearing 213 are interposed between the bush 210 and the output shaft 203. The outer needles of the first needle bearing 211, the one-way clutch 212, and the second needle bearing 213 are internally fitted and fixed to the bush 210. The one-way clutch 212 transmits torque to the bush 210 when the output shaft 203 rotates in the direction in which the mainspring 202 is tightened (torque transmission direction), and idles when the output shaft 203 rotates in the opposite direction. It is located in.

The output shaft 203 is rotatably attached to the casing 201 by a first rolling bearing 214 and a second rolling bearing 215 each having an outer ring fixed to the casing 201. A first sleeve 216 is interposed between the first rolling bearing 214 and the output shaft 203, and a second sleeve 217 is interposed between the second rolling bearing 215 and the output shaft 203. The first and second sleeves 216 and 217 respectively have flanges 216 a and 217 a that are radially expanded and are located between the first and second rolling bearings 214 and 215 and the bush 210.

With the above configuration, the mainspring drive device 200 according to the present embodiment elastically deforms the mainspring 202 by the rotation of the output shaft 203, temporarily stores energy in the mainspring 202, and outputs the energy as torque of the output shaft 203. can do.

Further, in the mainspring drive device 200 according to the present embodiment, since the one-way clutch 212 is interposed between the bush 210 fixed to the inner end of the mainspring 202 and the output shaft 203, the output shaft 203 has the mainspring. The mainspring 202 will not be damaged even when it is rotated in the direction opposite to the direction in which the winding 202 is tightened. Further, for example, when the mainspring drive device 200 drives the work carriage, the work carriage can continue to run due to inertia even after all the energy stored in the mainspring 202 is output.

Further, even when the mainspring 202 is excessively wound, the convex portion 202a is disengaged from the concave portion 201c by the convex portion 202a formed on the outer end of the mainspring 202 and the concave portion 201c formed on the peripheral wall 201b. Therefore, the mainspring 202 can be prevented from being damaged.

Specifically, when the mainspring 202 is tightened, the outer diameter of the mainspring 202 becomes smaller, and a gap is formed between the convex portion 202a and the portion of the mainspring 202 radially inside the convex portion 202a. When the mainspring 202 is wound up to a predetermined number of rotations (winding amount) and the convex portion 202a is pulled by a predetermined force, the convex portion 202a slides on the inclined surface of the concave portion 201c and moves radially inward to form the concave portion. The engagement with 201c is released, and the fixing of the mainspring 202 in the rotational direction is released. After that, the convex portion 202a moves in the circumferential direction by the bias of the mainspring 202, engages with the concave portion 201c located next in the circumferential direction, and limits the rotation of the mainspring 202 again. After that, when the output shaft 203 continues to rotate in the tightening direction, the same movement is repeated.

As shown in FIGS. 7 and 8, the mainspring drive device 200 extends substantially parallel to the central axis direction of the output shaft 203 on the outer diameter side of the peripheral wall 201b forming a part of the casing 201 and penetrates the peripheral wall 201b. Eight T-shaped grooves 201e thus formed are formed. The peripheral wall 201b has a substantially quadrangular outer shape when viewed from the front surface or the back surface, and two T-grooves 201e are formed at each of four corners thereof. In other words, one T-shaped groove 201e is formed near each end of one side of the peripheral wall 201b having a substantially quadrangular outer shape. This allows the user to attach the mainspring drive device 200 to the frame or the like of the work carriage in a relatively free manner by using the T-slot nut and the bolt. The user can select the number and type of fixtures such as T-slot nuts and bolts, and the position of the fixtures. Further, by forming the peripheral wall 201b into the above shape, the casing 201 can be easily mass-produced by extrusion molding.

100 rotation speed adjustment mechanism 101 torque transmission mechanism 101a first gear 101b second gear 101c third gear 102 damper holder 102a output shaft hole 102b holding hole 102c screw hole 103 first rotary damper 103a rotation Shaft 104 Second rotary damper 104a Rotation shaft 110 Strut 112 Screw 200 Spring drive device 201 Casing 201b Peripheral wall 201c Recess 201d Opening 201e T groove 201f, 201g Annular portion 202 Spring 202a Convex 203 Output shaft 204 Set collar 205a, 205b key 210 bush 211 first needle bearing 212 one-way clutch 213 second needle bearing 214 first rolling bearing 215 second rolling bearing 216 first sleeve 216a flange 217 second sleeve 217a flange 218, 219 transparent Plate 1000 Spring type variable speed drive

Claims (3)

A casing,
An output shaft that penetrates the casing and is attached to the casing so as to be relatively rotatable,
A one-way clutch externally fitted to the output shaft in the casing,
A mainspring that is housed in the casing, has a radially inner end fixed to an outer ring of the one-way clutch, and is tightened when the output shaft rotates in the torque transmission direction of the one-way clutch,
A damper holding part which is fixed to the casing integrally with the casing while being separated from the casing in the central axis direction of the output shaft on the outside of the casing,
A rotating shaft disposed between the damper holding portion and the casing in a central axis direction of the output shaft is detachably held by the damper holding portion, and the rotating shaft is centered on the central axis of the rotating shaft. A rotary damper that exerts braking force against the torque to rotate,
A power spring type variable speed drive device having a torque transmission mechanism which is arranged between the damper holding portion and the casing in a central axis direction of the output shaft and which transmits a torque of the output shaft to the rotary shaft. The torque transmission mechanism is
A first gear fitted onto the output shaft;
The mainspring type variable speed drive device according to claim 1, further comprising a second gear that is externally fitted to the rotation shaft and meshes with the first gear. The damper holder is
Consisting of plate-shaped members arranged substantially perpendicular to the central axis direction of the output shaft,
The mainspring type variable speed drive device according to claim 1 or 2, further comprising a plurality of holding holes into which the rotary dampers are inserted.

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