Automatic torque regulating system with enlarging function

An automatic torque regulating system includes a base, a plurality of positioning rods mounted on the base, a first disk mounted on the positioning rods, a second disk moved with the first disk, a hollow bushing sandwiched between the first disk and the second disk and pivotally connected a force input shaft and a force output shaft, a plurality of cams moved in concert with the first disk and the second disk and pressing a conic face of the force output shaft. Thus, when the first disk and the second disk are moved, the cams are moved axially relative to the force output shaft to change different contact points between the cams and the conic face of the force output shaft so as to regulate the torque automatically.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a gear system and, more particularly, to an automatic torque regulating system for a generator or an electric car.

2. Description of the Related Art

A conventional generator or electric car comprises a gear system having a force input shaft, a plurality of gears and a force output shaft. In operation, when the generator or electric car produces a load resistance due to an excessive voltage, the force output shaft stops rotating by the load resistance to stop rotation of the force input shaft. However, the gear system does not have a torque regulating function so that the generator or electric car is easily inoperative due to shortage of torque.

BRIEF SUMMARY OF THE INVENTION

The primary objective of the present invention is to provide an automatic torque regulating system with an enlarging function.

In accordance with the present invention, there is provided an automatic torque regulating system comprising a base, a force output shaft, a plurality of positioning rods, a plurality of spring abutments, a plurality of compression springs, a first disk, a second disk, a plurality of driving shafts, a plurality of driven shafts, a plurality of driving gears, a plurality of driven gears, a hollow bushing a plurality of cams, a plurality of swing arms, a plurality of first tension springs, a plurality of second tension springs, a plurality of swinging members, a force input shaft, a driven sleeve, a driving sleeve, and a main drive gear. The base includes a transverse plate and an upright plate. The upright plate has a center provided with a shaft hole, and the force output shaft extends through the shaft hole of the base. The upright plate has a surface provided with a plurality of screw holes, and the positioning rods are locked onto the screw holes of the base. The force output shaft is pivotally connected with the shaft hole of the base. The force output shaft is provided with a conic face. The force output shaft has a first end provided with a force output portion extending through the shaft hole of the base and a second end provided with a connecting portion. Each of the positioning rods has a first end provided with a first thread screwed into one of the screw holes of the base and a second end provided with a second thread locked onto the first disk. Each of the spring abutments is mounted on one of the positioning rods and rests on the first disk. Each of the compression springs is mounted on one of the positioning rods and is biased between one of the spring abutments and one of the positioning rods to push the first disk forward. The first disk is provided with a plurality of through holes aligning with the screw holes of the base, and the positioning rods extend through the through holes of the first disk. The first disk has a center provided with a first shaft hole for mounting the hollow bushing. The first disk is provided with a plurality of first pivot holes pivotally connected with the driving shafts. The first disk is provided with a plurality of arcuate openings allowing passage of the driven shafts. The second disk has a center provided with a second shaft hole for mounting the hollow bushing. The second disk is provided with a plurality of second pivot holes pivotally connected with the driving shafts. The second disk is provided with a plurality of arcuate slots allowing passage of the driven shafts. Each of the driving gears is mounted on one of the driving shafts. Each of the driven gears is locked on one of the driven shafts and meshes with one of the driving gears respectively. The hollow bushing is sandwiched between the first disk and the second disk. The hollow bushing has a front end pivotally connected with the force input shaft and a rear end pivotally connected with the connecting portion of the force output shaft. Each of the cams is locked onto one of the driven shafts and press the conic face of the force output shaft. Each of the cams has a side provided with a mounting seat. Each of the swing arms is pivotally connected with the mounting seat of one of the cams. The first tension springs are biased between the swing arms to force the cams to press the conic face of the force output shaft, so that the conic face of the force output shaft is sandwiched between the cams by the elastic force of the first tension springs. Each of the second tension springs is mounted between one of the driving shafts and one of the driven shafts, so that each of the driven gears is forced to mesh with one of the driving gears constantly by the elastic force of each of the second tension springs. Each of the swinging members is mounted between the first disk and the second disk. Each of the swinging members has a first side provided with a first pivot hole allowing passage of one of the driving shafts and a second side provided with a second pivot hole allowing passage of one of the driven shafts. The driven sleeve is secured on the force input shaft and is provided with two first abutting faces and two first guiding ramps. The driving sleeve is pivotally mounted on the force input shaft and is juxtaposed to the driven sleeve. The driving sleeve is provided with two second abutting faces aligning with the first abutting faces of the driven sleeve and two second guiding ramps aligning with the first guiding ramps of the driven sleeve. The main drive gear is mounted on the force input shaft and meshes with the driving gears.

According to the primary advantage of the present invention, the cams are moved axially relative to the force output shaft to change different contact points between the cams and the conic face of the force output shaft so as to regulate the torque automatically.

According to another advantage of the present invention, the cams are moved relative to the force output shaft to enlarge the torque, thereby preventing the generator or the electric car from being inoperative due to shortage of torque.

DETAILED DESCRIPTION OF THE INVENTION

Referring to the drawings and initially toFIGS. 1-12, an automatic torque regulating system in accordance with the preferred embodiment of the present invention comprises a base10, a force output shaft20, a plurality of positioning rods30, a plurality of spring abutments33, a plurality of compression springs “S”, a first disk40, a second disk50, a plurality of driving shafts “L1”, a plurality of driven shafts “L2”, a plurality of driving gears “G1”, a plurality of driven gears “G2”, a hollow bushing43, a plurality of cams46, a plurality of swing arms48, a plurality of first tension springs “S1”, a plurality of second tension springs “S2”, a plurality of swinging members60, a force input shaft70, a driven sleeve72, a driving sleeve76, and a main drive gear “G”.

The base10has a substantially L-shaped profile and includes a transverse plate11and an upright plate12. The upright plate12has a center provided with a shaft hole14, and the force output shaft20extends through the shaft hole14of the base10. The upright plate12has a surface provided with a plurality of screw holes15surrounding the shaft hole14, and the positioning rods30are locked onto the screw holes15of the base10. The base10further includes two triangular reinforcing plates13connected between the transverse plate11and the upright plate12.

The force output shaft20is pivotally connected with the shaft hole14of the base10by a bearing “B” and is retained by a snap ring “C”. The force output shaft20is provided with a conic face21having a diameter gradually decreased from a front end to a rear end thereof. The force output shaft20has a first end provided with a force output portion22extending through and protruding from the shaft hole14of the base10and a second end provided with a connecting portion23.

Each of the positioning rods30has a first end provided with a first thread31screwed into one of the screw holes15of the base10and a second end provided with a second thread32locked onto the first disk40by a nut “N” and a needle bearing “B1”. Each of the spring abutments33is mounted on one of the positioning rods30and rests on the first disk40. Each of the compression springs “S” is mounted on one of the positioning rods30and is biased between one of the spring abutments33and one of the positioning rods30to push the first disk40forward, so that the first disk40is moved forward or backward on the positioning rods30.

The first disk40is provided with a plurality of through holes41aligning with the screw holes15of the base10, and the positioning rods30extend through the through holes41of the first disk40. The first disk40has a center provided with a first shaft hole42for mounting the hollow bushing43. The first disk40is provided with a plurality of first pivot holes44pivotally connected with the driving shafts “L1” by a plurality of bolts “P” and a plurality of washers “Q”. The first disk40is provided with a plurality of arcuate openings45allowing passage of the driven shafts “L2”.

The second disk50has a center provided with a second shaft hole51for mounting the hollow bushing43. The second disk50is provided with a plurality of second pivot holes52pivotally connected with the driving shafts “L1”. The second disk50is provided with a plurality of arcuate slots53allowing passage of the driven shafts “L2”.

Each of the driving gears “G1” is mounted on one of the driving shafts “L1” by a plurality of bearings “B”. Each of the driven gears “G2” is mounted on one of the driven shafts “L2” by a washer “Q”, a bearing “B” and a snap ring “C”. Each of the driven gears “G2” is locked on one of the driven shafts “L2” by a plurality of bolts “P”. Each of the driven gears “G2” meshes with one of the driving gears “G1” respectively.

The hollow bushing43is sandwiched between the first disk40and the second disk50so that the first disk40, the hollow bushing43and the second disk50are moved forward and backward simultaneously. The hollow bushing43has a front end pivotally connected with the force input shaft70by a plurality of bearings “B”, and the force input shaft70is locked on the front end of the hollow bushing43by a bolt “P” and a washer “Q”. The hollow bushing43has a rear end pivotally connected with the connecting portion23of the force output shaft20by a bearing “B”.

The cams46are mounted on the driven shafts “L2” and press the conic face21of the force output shaft20. Each of the cams46has a conic face resting on the conic face21of the force output shaft20. The conic face of each of the cams46has a diameter gradually increased from a front end to a rear end thereof and has a gradient equal to that of the conic face21of the force output shaft20. Each of the cams46is locked onto one of the driven shafts “L2” by a bearing “B” and a bolt “P” so that each of the cams46is moved forward and backward with one of the driven shafts “L2”. Each of the cams46has a side provided with a mounting seat47by a plurality of bolts “P”. Each of the swing arms48is pivotally connected with the mounting seat47of one of the cams46by a bearing “B” and a snap ring “C”. Each of the swing arms48has two ends each provided with a pivot hole49for mounting a pivot rod “R”. The first tension springs “S1” are biased between the swing arms48to force the cams46to press the conic face21of the force output shaft20, so that the conic face21of the force output shaft20is sandwiched between the cams46by the elastic force of the first tension springs “S1”. Each of the first tension springs “S1” has two ends each hooked onto the respective pivot rod “R” of one of the swing arms48. Each of the second tension springs “S2” is mounted between one of the driving shafts “L1” and one of the driven shafts “L2”, so that each of the driven gears “G2” is forced to mesh with one of the driving gears “G1” constantly by the elastic force of each of the second tension springs “S2”.

Each of the swinging members60is mounted between the first disk40and the second disk50. Each of the swinging members60has a first side provided with a first pivot hole61allowing passage of one of the driving shafts “L1” and a second side provided with a second pivot hole62allowing passage of one of the driven shafts “L2”. The second side of each of the swinging members60has a first end received in one of the arcuate openings45of the first disk40and a second end received in one of the arcuate slots53of the second disk50. In such a manner, when the cams46are moved forward or backward relative to the force output shaft20to change different contact points between the cams46and the conic face21of the force output shaft20, each of the driving shafts “L1” functions as a fulcrum, and each of the swinging members60drives one of the driven shafts “L2” to pivot about one of the driving shafts “L1” and to swing inward (as shown inFIG. 16) or outward (as shown inFIG. 10) in one of the arcuate openings45of the first disk40and one of the arcuate slots53of the second disk50, so that the driven gears “G2” also swing in concert with the driven shafts “L2”.

Each of the driving shafts “L1” in turn extends through one of the driving gears “G1”, one of the second pivot holes52of the second disk50, the first pivot hole61of one of the swinging members60and one of the first pivot holes44of the first disk40. Each of the driven shafts “L2in turn extends through one of the driven gears “G2”, one of the arcuate slots53of the second disk50, the second pivot hole62of one of the swinging members60, one of the arcuate openings45of the first disk40and one of the cams46.

The force input shaft70is provided with an elongate channel71extending longitudinally. The driven sleeve72is secured on the elongate channel71of the force input shaft70by a bolt “P”. The driven sleeve72has an exterior provided with two claws73. The driven sleeve72is provided with two first abutting faces74and two first guiding ramps75between the two claws73. The driving sleeve76is pivotally mounted on the force input shaft70by a needle bearing “B1” and is juxtaposed to the driven sleeve72. The driving sleeve76is provided with two second abutting faces77aligning with the first abutting faces74of the driven sleeve72and two second guiding ramps78aligning with the first guiding ramps75of the driven sleeve72. The main drive gear “G” is mounted on the force input shaft70and meshes with the driving gears “G1” to drive and rotate the driving gears “G1”.

In practice, each of the cams46is locked onto one of the driven shafts “L2”, and each of the driven gears “G2” is locked on one of the driven shafts “L2”, so that when the driven gears “G2” are rotated, the driven shafts “L2” and the cams46are also rotated in concert with the driven gears “G2”. Thus, when the main drive gear “G” is rotated by the force input shaft70, the main drive gear “G” drives and rotates the driving gears “G1” which drive and rotate the driven gears “G2” which drive and rotate the cams46which drive and rotate the force output shaft20. At this time, when the cams46are moved forward or backward relative to the force output shaft20to change different contact points between the cams46and the conic face21of the force output shaft20, the cams46are biased by the elastic force of the first tension springs “S1” and are kept in constant contact with the conic face21of the force output shaft20, while each of the driven gears “G2” is biased by the elastic force of each of the second tension springs “S2” and is kept in constant contact with one of the driving gears “G1”.

In operation, referring toFIGS. 7-12with reference toFIGS. 1-6, the driving sleeve76is connected with a motor80, and the force output portion22of the force output shaft20is connected with a generator90. The generator90includes a large gear92and a small gear91. When the generator90is operated under the normal load, the first disk40and the second disk50are pushed and moved forward to a determined position by the elastic force of the compression springs “S”, so that the driven sleeve72is moved forward and engages the driving sleeve76as shown inFIG. 12. In such a manner, the motor80applies a power to rotate the driving sleeve76which rotates the driven sleeve72which rotates the force input shaft70which rotates the main drive gear “G” which rotates the driving gears “G1” which rotate the driven gears “G2” which rotate the driven shafts “L2” which rotate the cams46which rotate the force output shaft20which drives the small gear91and the large gear92of the generator90so as to achieve the purpose of generating electricity.

On the contrary, referring toFIGS. 13-17with reference toFIGS. 1-6, when the generator90produces a load resistance due to an excessive voltage, the force output shaft20stops rotating by the resistance to stop rotation of the force input shaft70. At this time, the driving sleeve76is rotated by the motor80successively, and the driven sleeve72is pushed backward by a taper fit between the first guiding ramps75of the driven sleeve72and the second guiding ramps78of the driving sleeve76as shown inFIG. 13, so that the first disk40and the second disk50are pushed and moved backward as shown inFIG. 17, and the cams46are moved axially relative to the force output shaft20from the position as shown inFIG. 8to the position as shown inFIG. 14, to change different contact points between the cams46and the conic face21of the force output shaft20. At the same time, when the cams46are moved backward relative to the force output shaft20to change different contact points between the cams46and the conic face21of the force output shaft20, the cams46are biased by the elastic force of the first tension springs “S1” and are kept in constant contact with the conic face21of the force output shaft20, while each of the driven gears “G2” is biased by the elastic force of each of the second tension springs “S2” and is kept in constant contact with one of the driving gears “G1”. In such a manner, the cams46are moved backward on the force output shaft20to enlarge the torque, so that the force output shaft20is rotated in concert with the cams46simultaneously to drive the small gear91and the large gear92of the generator90. Thus, the cams46are moved forward or backward relative to the force output shaft20to change different contact points between the cams46and the conic face21of the force output shaft20, so as to regulate the torque automatically, thereby preventing the generator90from being inoperative due to shortage of torque.

In the preferred embodiment of the present invention, the conic face21of the force output shaft20has a diameter gradually decreased from a front end to a rear end thereof, while the conic face of each of the cams46has a diameter gradually increased from a front end to a rear end thereof and has a gradient equal to that of the conic face21of the force output shaft20. In such a manner, when each of the cams46is located at the front position of the force output shaft20, each of the cams46applies a smaller torque, and when each of the cams46is located at the rear position of the force output shaft20, each of the cams46applies a larger torque. Thus, when the cams46are moved backward relative to the force output shaft20, the torque is enlarged, and when the cams46are moved forward relative to the force output shaft20, the torque is reduced. Therefore, the cams46are moved forward or backward relative to the force output shaft20to change different contact points between the cams46and the conic face21of the force output shaft20, so as to regulate the torque automatically.

Referring toFIG. 18, the force output portion22of the force output shaft20is connected with an electric car100. The electric car100includes a belt wheel101and a belt102. Thus, the force output portion22of the force output shaft20uses the belt wheel101and the belt102to transmit the power of the motor80to the electric car100.

Accordingly, the cams46are moved axially relative to the force output shaft20to change different contact points between the cams46and the conic face21of the force output shaft20, so as to regulate the torque automatically. In addition, the cams46are moved relative to the force output shaft20to enlarge the torque, thereby preventing the generator90or the electric car100from being inoperative due to shortage of torque.