JPS6344981B2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention provides a method for providing a
When transmitting the rotation of the input shaft to the output shaft, it smoothly reduces the impact force applied to the shaft system depending on the size of the load.
The present invention relates to a shock absorber that efficiently transmits rotation.

[Conventional technology]

Conventional examples of such shock absorbers include a friction clutch that uses friction caused by contact between friction surfaces to intermittent rotational motion, and a torque converter that is a fluid coupling that transmits rotational motion through fluid.

[Problem to be solved by the invention]

However, in the friction clutch described above, rotation is transmitted by coupling the input shaft and output shaft by intermittent friction surfaces and by a buffering function by friction. It is necessary to intermittent operation of both shafts at the appropriate timing, and since there is slippage in the contact between friction surfaces, there is energy loss in rotation transmission, and there is a risk that the reliability of rotation transmission will be impaired due to wear during long-term use. There is a problem. Additionally, torque converters using fluid have problems in that they have energy loss and are large and complex in structure.

The present invention solves the problems of the prior art, simplifies the rotation transmission mechanism, eliminates the need for intermittent operation of both shafts during rotation transmission, and provides a buffer that alleviates the impact force applied to the shaft system. It is an object of the present invention to provide a shock absorber that dramatically increases the effectiveness and can smoothly, reliably, and efficiently transmit rotation regardless of the rotational speed of the input shaft and the magnitude of the load applied to the output shaft.

[Means to solve the problem]

In order to solve the above problems, the present invention takes the following measures. That is, "three sets of planetary gear devices A each consisting of a sun gear, a planetary gear, and an internal gear,
The sun gear A of the planetary gear set A is fixed to the input shaft, and the sun gear C of the planetary gear set C is removably connected to the input shaft, and the internal gear A of the planetary gear set A is connected to the input shaft. The sun gear B of the planetary gear device B and the internal gear C of the planetary gear device C, which are loosely fitted on the outer peripheral surface of the input shaft, are integrated, and the carrier B of the planetary gear device B and the carrier C of the planetary gear device C are integrated. A pair of pawls 3 are arranged at an interval of 180° and protrude from the circumferential outer surface of the internal gear B of the planetary gear set B, and the carrier A of the planetary gear set A is cylindrical so as to surround the entire planetary gear set. One end is fixed to the output shaft, and a cylindrical housing chamber is formed on the outer circumferential surface of the intermediate portion to accommodate the pawl and spring formed on the internal gear B of the planetary gear device B. The housing chamber of the carrier A of the planetary gear device A is divided into two chambers, left and right, by a pair of pawls formed on the internal gear B. The springs are divided and connected into a plurality of pieces in each compartment, and both ends of the springs are connected to the internal gear B. A plurality of pins housed in opposition to a pair of claws and attached to both ends of the spring and the connecting end are formed on both side walls of the housing chamber of carrier A at a central angle of several tens of degrees around the axis of the input shaft. It is characterized by having each arcuate groove protrude outward from both ends.

[Effect]

First, the sun gear C of the planetary gear set C and the input shaft are connected via a clutch. Since carrier A, which is connected to the load via the output shaft, is stationary at the beginning of operation, the rotation of the input shaft is caused by internal gear B of planetary gear unit B via planetary gear units A and B.
Rotation in the same direction is applied at a reduced speed, while rotation in the opposite direction to the rotation of the input shaft is applied at a reduced speed to the internal gear B via the planetary gear device C. Therefore, as the input shaft rotates, the internal gear B rotates at a predetermined speed in the same direction as the input shaft due to the difference in rotation applied from both directions, and a pair of symmetrically protruding parts on the outer peripheral surface of the internal gear B rotate in the same direction as the input shaft. The pawl compresses a plurality of springs which are divided and connected in a cylindrical housing chamber in the carrier A of the planetary gear set A. The pins attached to the connecting ends of the springs, which are connected in multiple pieces, are connected to arc-shaped grooves formed at a predetermined center angle on both side walls of the cylindrical storage chamber of carrier A, depending on the load. Since it protrudes outward from both ends, when the spring is compressed through the pair of pawls due to the rotation of internal gear B, the pin on the pawl side slides within the arc-shaped groove, and the spring is compressed accordingly and the load is reduced. The rotational force for driving is stored in the spring. Internal gear B
When the compression of the spring reaches a predetermined angle according to the load, the rotational force accumulated in the spring causes the carrier A, which is connected to the spring through the engagement of the pin and the arcuate groove, to rotate in the same direction as the input shaft. As a result, the output shaft also begins to rotate in the same direction as the input shaft. As the output shaft rotates with the rotation of the carrier A, the deceleration effect by the planetary gear system is gradually reduced, and the output shaft rotates at the same rotational speed as the input shaft.

〔Example〕

An example of implementing the present invention will be described with reference to the attached drawings. 1 is an input shaft, 2 is an output shaft, and three sets of planetary gear devices A, B, and C are arranged between these two shafts. Each of the planetary gear sets A, B, and C consists of a sun gear, a planet gear, a carrier thereof, and an internal gear. A sun gear A of a planetary gear set A is fixed to the input shaft 1, and a sun gear C of a planetary gear set C is removably coupled to the input shaft 1 via a clutch 5. The internal gear A meshes with the planetary gear A of the planetary gear set A, and the sun gear B of the planetary gear set B is loosely fitted to the input shaft 1.
and the internal gear C meshing with the planetary gear C of the planetary gear device C are integrally connected, and the carrier B of the planetary gear B and the carrier C of the planetary gear C are also integrally connected. A pair of pawls 3, 3 are formed protruding from the circumferential outer surface of the internal gear B of the planetary gear device B with an interval of 180° between them. Planetary gear A
The carrier A is formed into a cylindrical shape so as to surround the entire planetary gear set, and one end of the carrier A is fixed to the output shaft 2, and a pair of pawls formed on the internal gear B are attached to the outer peripheral surface of the intermediate part. A cylindrical housing chamber 6 for accommodating the springs 3 and 4 is formed in a protruding manner. The inside of the accommodation chamber 6 of this carrier A is divided into two left and right chambers by the presence of a pair of claws 3, 3 of an internal gear B, and in each chamber, a spring 4 divided into three pieces is connected inside. Gear B claws 3, 3
It is housed in a state facing the A hinge 8 having pins 7 is attached to both ends of the split-connected spring 4 and each connection end, and these pins 7 are housed inside both side walls of the storage chamber 6 of the carrier A. The end of the spring 4, which is connected in three parts, corresponds to the divided part where it is in contact with the pawls 3, 3 of the internal gear B, and the central angle is approximately 100 cm with respect to the axis of the input shaft 1.
A pair of left and right arc-shaped grooves 9 are formed at an angle of 40 degrees and project outward from both ends thereof. Further, a guide roller 10 that rotates in contact with the inner wall surface of the ceiling of the storage chamber 6 is disposed on the pin 7, and thereby the spring 4
is supported. The number of teeth of each gear of the planetary gear devices A, B, and C is set as follows.

A B C 30 30 20 30 30 32 90 90 84 Next, the operation of the device according to the above embodiment will be explained. In order to transmit the rotation of the input shaft 1 to the output shaft 2, the sun gear C is first coupled to the input shaft 1 via the clutch 5. Since the carrier A is fixed to the output shaft 2 and is loaded with a load, the carrier A is in a stationary state at the beginning of startup. Therefore, when the sun gear A rotates once clockwise via the input shaft 1, the internal gear A rotates counterclockwise via the planetary gear A by 30/90=1/3. Since sun gear B and internal gear C are integrated with internal gear A, both sun gear B and internal gear C also rotate 1/3 in the counterclockwise direction. Since the carrier B of the planetary gear B and the carrier C of the planetary gear C meshing with the sun gear C coupled to the input shaft 1 are integrally coupled, the internal gear B is connected to the sun gear B.
The counterclockwise rotation of the planetary gear C rotates clockwise via the planetary gear B, while the carrier C of the planetary gear C rotates counterclockwise under the influence of the counterclockwise direction of the internal gear C and is integrated with the carrier C. Since the carrier B of the planetary gear B also rotates counterclockwise, the clockwise rotation of the internal gear B is thereby reduced. Therefore, the rotation angle of internal gear B is the rotation angle by sun gear B and internal gear B.
It is determined by integrating the rotation direction of the carrier B and the rotation of the carrier B acting in the opposite direction. The rotation of the carrier C is the rotation of the internal gear C and the sun gear C.
The rotation angle of carrier C and therefore carrier B is determined by the rotation of (120° x 84/84 + 20) - (360° x 20/84 + 20) ≒ 27.7
degree, and carrier B rotates 27.7 degrees counterclockwise.

Therefore, the rotation angle of internal gear B is (120° x 30/90) - (27.7° x 30 + 90/30 x 30/90)
≒3.07°, and the internal gear B rotates 3.07° in the same direction every time the input shaft 1 rotates clockwise (360°). As the internal gear B rotates, the spring 4 is compressed via the pair of claws 3, 3 according to the applied load. Since pins attached to the ends of the springs 4 are slidably engaged with both ends of the arcuate grooves 9 formed on both side walls of the storage chamber 6 of the carrier A, the pair of claws 3, 3 presses the spring 4, the pin on the claw side slides in the arcuate groove 9, and the spring 4 is pressed accordingly.
is compressed. Since the compression angle of the spring 4 with respect to the maximum load (the center angle of the arcuate groove 9 on the side wall of the storage chamber 6) is set to approximately 40° as described above, when the spring 4 is compressed to the maximum by the internal gear B ( (When the load is the maximum set load) The input shaft is relative to the output shaft.
This means that there is a margin of 40° ÷ 3.07° ≒ 13 rotations (range of buffering effect).

As the input shaft rotates, the spring 4 is compressed by the internal gear B according to the applied load, and as a result, rotational force for driving the load is accumulated in the spring 4, and the compression angle of the spring 4 changes according to the applied load. When a predetermined angle corresponding to the angle is reached, the accumulated rotational force causes the spring 4 to
Meanwhile, a carrier A connected through engagement between a pin 7 and an arcuate groove 9 rotates in the same direction as the input shaft 1, and an output shaft 2 coupled to this carrier A rotates in the same direction as the input shaft 1.
also rotates in the same direction as the input shaft 1. As the spring is compressed, resistance also appears in the rotation of the planetary gear A, and as the carrier A rotates, the deceleration effect of the planetary gear device on the input rotation for exerting the buffering function is gradually reduced, and the output shaft 2 becomes the input shaft 1. It rotates at the same rotational speed.

Note that the reaction force from the spring 4 compressed by the internal gear B is received by the sun gear C of the planetary gear device C coupled to the input shaft 1, so that the spring 4 does not move backward during operation. Then, when the sun gear C is removed from the input shaft 1 via the clutch 5, the sun gear C is reversed by a predetermined angle, and the spring and speed reduction mechanism return to their initial states. Note that the compression angle of the spring may be approximately 60°. In the figure, 11 is a spring that presses the clutch 5 toward the sun gear C, and 12 is an on/off operation part for the clutch 5, which is connected to an arm that engages the clutch 5 and is connected to the outer cover. It consists of an operating lever that is attached. FIG. 4 is an explanatory diagram in which arrows indicate the rotation direction and rotation angle of each planetary gear device as the input shaft 1 rotates. For convenience, each gear is rotated 90 degrees to the front side from the state shown in FIG. 1. The situation is as follows.

〔Effect of the invention〕

As described above, the present invention includes a reduction mechanism using three sets of planetary gear devices between an input shaft and an output shaft, and a rotational force compressed by a predetermined angle according to the load by this reduction mechanism to drive the load. A shock absorber is constructed that smoothly and efficiently transmits the rotation of the input shaft to the output shaft by organically combining the rotational force accumulation mechanism with a spring that accumulates rotational force, thereby solving the problems of the above-mentioned conventional technology. and has the following effects.

Firstly, there is no need for complicated intermittent operation of input/output shafts, which requires proper timing as with conventional friction clutches, and there is no wear part such as friction surfaces, resulting in excellent durability and rotation transmission. It can be done reliably. Second, since rotation is mechanically transmitted using a planetary gear system and a spring, there is no energy loss associated with slipping on the friction surface of conventional friction clutches or via fluid in torque converters, and rotation transmission is much easier than conventional friction clutches. It can be done more efficiently. Thirdly, the range of the buffering effect (the allowable preceding rotational speed of the input shaft until the rotation of the output shaft) is dramatically increased by combining the speed reduction mechanism with the planetary gear system and the load rotational force accumulation mechanism with the spring. be able to. For example, as shown in the above example, the input shaft can be rotated approximately 13 times per minute in response to the maximum set load.
Even if a 780 rpm prime mover is directly input, the output shaft is approximately 1
It can remain stopped for seconds, and in reality, the output shaft also begins to rotate during this time, so the operating time is further extended, and the range of the buffering effect is extremely large. Therefore, regardless of the rotational speed of the input shaft and the load applied to the output shaft, rotation transmission can be carried out smoothly, reliably, and efficiently. It can be effectively used for AC motors that have many changes in load and speed, and for AC motors that initially have low torque. Fourth, the overall structure is extremely simple compared to torque converters and the like.

[Brief explanation of drawings]

The drawings show a shock absorber according to an example of implementing the present invention. Fig. 1 is a side view showing the overall structure in principle, and Fig. 2 shows the left half of Fig. 1 as a carrier A.
3 is a side view with the upper half in section, and FIG. 4 is a cross-sectional view of the input shaft and the gears in the planetary gear device. FIG. 3 is an explanatory diagram showing a relationship between a rotation direction and a rotation angle. 1...Input shaft, 2...Output shaft, 3...Claw, 4...
...Spring, 5...Clutch, 6...Containment chamber, 7...
Pin, 9...Arc-shaped groove, A, B, C...Planetary gear device.

Claims (1)

[Claims] 1 It has three planetary gear sets A, B, and C each consisting of a sun gear, a planet gear, and an internal gear, and fixes the sun gear A of the planetary gear set A to the input shaft, and also fixes the sun gear A of the planetary gear set C to the input shaft. A sun gear B of a planetary gear system B and an internal gear C of a planetary gear system C are connected to each other removably through a clutch, and are loosely fitted to the internal gear A of the planetary gear system A and the outer peripheral surface of the input shaft.
and the carrier B of the planetary gear system B.
A pair of pawls 3 are arranged at an interval of 180° and protrude from the circumferential outer surface of the internal gear B of the planetary gear device B, and the carrier A of the planetary gear device A is integrated with the carrier C of the planetary gear device C. has a cylindrical shape so as to surround the entire planetary gear set, and has one end fixed to the output shaft, and has a cylindrical shape for accommodating the pawl and spring formed on the internal gear B of the planetary gear set B on the outer peripheral surface of the intermediate part. The housing chamber of the carrier A of the planetary gear set A is divided into two chambers on the left and right by a pair of pawls formed on the internal gear B of the planetary gear set B. A spring is housed with its both ends facing a pair of pawls of an internal gear B,
The pins attached to both ends of the spring and the connecting end are connected to the outside from both ends of multiple arc-shaped grooves formed at an angle of several tens of degrees around the axis of the input shaft on both side walls of the accommodation chamber of carrier A. A shock absorbing device using a planetary gear device and a spring, characterized in that it is made to protrude.