JPS5950255A - Rotational drive device for automotive auxiliary part - Google Patents

Abstract

PURPOSE:To prevent such occurence as high speed rotation in excess of the rotational speed suitable for auxiliary parts by providing a planetary gear mechanism between an input shaft and output shaft, and transmitting the rotational torque from the input shaft to the output shaft through the planetary gear in a reduced speed. CONSTITUTION:When the tip of the braking plunger 19 of a solenoid 20 is separated from an outer circumference 14a under low speed input condition, a coil spring 17 is wound around the outer circumference of an annular stopper 15, and an input shaft 1 and output shaft 5 rotate in unison. On the other hand, when the tip of the plunger 19 is forced to contact the outer circumference 14a, the coil spring 17 cannot be wound around the outer circumference of the output shaft. Because of this, the output shaft 5 does not rotate in union with a sun gear 6, but the planetary gear revolves due to the reaction of a one way clutch 13. Thus, the rotational speed of the input shaft is reduced and transmitted to the output shaft 5, preventing the input rotation to auxiliary parts from becoming unnecessarily high.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotational drive device for automobile auxiliary parts such as a power steering pump, a water pump, or a cooler combination.

Automotive auxiliary parts are driven by the output rotation of an engine via a pulley.

By the way, such auxiliary parts are required to have a certain level of output even in the low rotation range of the engine, so they must be increased in speed due to the above-mentioned boom, or the parts themselves must be made larger or larger. etc., and output k 't8'
tI' has been completed.

However, the auxiliary parts need to receive sufficient rotational input from the engine to drive the auxiliary parts themselves.
Considering that as the rotation speed increases, the efficiency decreases above a certain rotation speed, the input rotation speed to the auxiliary parts should not necessarily be proportional to the rotation speed of the post-washing machine. isn't it. Energy saving, small shaft for auxiliary parts IJj-
In order to achieve this, it is required that the input rotation from the engine to the auxiliary parts be decelerated to drive the auxiliary parts. be.

It was proposed.

In order to accomplish this purpose, the present invention operates a spring clutch mechanism to drive the output shaft to rotate at the same rotational speed as the human-powered shaft when the human-powered shaft is rotating at a low speed. On the other hand, when the input shaft is to rotate at a high speed higher than a certain set value, the solenoid does not activate the spring clutch mechanism and the planetary gear mechanism is fully driven. The output shaft has a metal rotation drive field.

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below based on the drawings.

FIG. 1 is a side view of the rotary drive device for auxiliary parts for motor vehicle υ according to the present invention, and FIG.
Kji im+ IZI, Figure 3 is Figure 1 K Okel l
it-11 [This is a thin sectional view.

As shown in FIG. 1, a bracket 2 whose overall cross section is approximately U-shaped is integrally formed on a human power shaft 1 that receives output rotational torque from an engine. 1ii
Su/Gugya 4 is engraved on the inner peripheral surface on the ia side. On the other hand, a sun gear 6 is rotatably attached to an output shaft 5 connected to an auxiliary component.
As shown in FIG. 2, a plurality of planetary gears 8, which are meshed with the toothed portion 7 and the ring gear 4, are provided between the toothed portion 7 carved on the outer circumferential surface of the one end 6a and the recling gear 4 described in iiJ.
8... are arranged. Each of these planetary gears 8, 8, . . . is rotatably supported by the pins 9, 9, . . . of the M plane. Each of these bins 9, 9, . a, they are planted at equal intervals in the circumferential direction. In this way, between the input shaft 1 and the output shaft 5, there is provided a planetary gear 21 that is composed of a ring gear 4, a sun gear 6, planetary gears 8, 8, . . . , and a key rear 10. .

The human power 11+1 and the output shaft 5 are rotatably supported by a support case 11, and between the support case 11 and the outer ring 12 of the other end 6b of the sun gear 6, there is a ring gear of the sun gear 6. A one-way clutch 13 is interposed therebetween to prevent rotation in the opposite direction to 4 (in this example, 8g2 in the 101st direction in the figure). Therefore, the direction of rotation of the sun gear 6 is determined by the one-way clutch 13.

In addition, at the external station position of the output shaft 5, as shown in FIG.
For example, an annular member 14 molded from a synthetic resin material or the like includes an annular stopper portion 15 provided in the middle of the output shaft 5 and an annular projection extending along the output shaft 5 from the other end 6b of the sun gear 6 described in HIJ. It is fitted with a certain gap b in the diametrical direction so as to straddle the portion 16. A coil spring 17 is interposed in the gap between the annular member 14, the annular stopper portion 15, and the annular protrusion 16. One end 17a of the coil spring 17 is embedded within the annular member 14 and fixed to the annular member 14, as shown in FIG.

However, the other end 17b of the coil spring 17 is locked to the sun gear 6. In addition, this coil spring 1
7 is in the direction opposite to the rotational force direction (third direction) with respect to the output shaft 5.
It is wound in a direction opposite to the arrow P in the figure). The coil spring 17 and the annular member 14 constitute a spring clutch mechanism 11.

At a position facing the outer circumferential surface 14a of the annular member 14, there is a brake plunger 19 that suppresses the outer circumferential surface 14ai and completely stops the rotation of the loam-like portion @14 by the frictional force with the outer circumferential surface 14a. A solenoid is provided. Brake plunger 19 of this solenoid 20
1p is separated from the outer circumferential surface 14a of the annular part 14 in normal times, and only when driving the spring clutch mechanism 18, is moved to the outer circumferential surface 1III14a of the loam part old 14;
L a It is growing so that it can be used.

Next, create a configuration like the one above! The operation of the present invention will be explained.

1. When the rotational speed of the engine is low, as shown in FIG. 3, the tip 19a of the brake plunger 19 of the solenoid is kept away from the outer peripheral surface 14a of the member 14. Then, the rotation of the input shaft 1, which is rotating at low speed in response to the output rotational torque from the engine, is controlled by each planetary gear 8, 8.
It is transmitted to... At this time, each planetary gear 8, 8.
Due to the rotation (rotation) of the input shaft 1, the rotation direction of the input shaft 1 relative to the sun gear 6ii and the ring gear 4 (direction of arrow P in Fig. 2)
and the opposite direction (in the figure, the one-way controller 13 prevents rotation in the opposite direction, so the reaction force causes the planetary gears 8, 8 to rotate (revolution) in the direction of the arrow P in Figure 2). For this reason, planetary gears 8, 8...
The pins 9, 9... and the pins 9, 9... are pivotally supported.
Output l111II5 through the implanted carrier 10
begins to rotate. As the output shaft 5 rotates, the coil spring 17 is wound around the outer peripheral surface 15a of the four-shaped stopper portion 13 of the output shaft 5, and the output shaft 5 and the coil spring 17 rotate together. start. On the other hand, since the other end 17b of the coil spring 17 is locked to the annular protrusion 16, the output shaft 5 and the sun gear 6 rotate together, and as a result, the output shaft 5 and the sun gear 6 are engaged with each other. Planetary gear 8°9...
rotates integrally with the sun gear 6 and output shaft 5 without rotating. On the other hand, since the ring gear 4 provided at one end of the input shaft 1 meshes with the planetary gear 8.8, the human power shaft 1 and the output shaft 5 will finally rotate together. be.

On the other hand, if the engine is about to start rotating at a heavy speed that exceeds the dazzling value, as shown in FIG. 19ak Outer peripheral surface 1 of loam-like member 14
4 Press against a. Then, one end 17 on the ring 14
The coil spring J7 with the part a buried therein cannot be wound around the outer part 15a of the annular stopper part 15 of the output shaft 5. Therefore, the output shaft 5 no longer rotates the sangya 6 integrally. On the other hand, the rotation of the input shaft 1 is transmitted to each planetary gear 8.8... At this time, due to the rotation (rotation) of each planetary gear 8°8..., the sun gear 6 is rotated by the ring gear 4 in a direction opposite to the rotational direction of the input shaft 1 (direction of arrow P in FIG. 2) (in the same figure). However, the one-way clutch 13 stops the rotation in the opposite direction. Therefore, due to the reaction force of the one-way clutch 13 trying to stop the rotation of the sun gear 6, the bridle/tarikya 8, 8.・・・
is meshed with sun gear 6 and rotates in the direction of arrow P in Fig. 2 (
revolution). The revolution of the planetary gears 8, 8... is caused by the Mil Br2 pins 9, 9... and the carrier 10.
The output shaft 5 will be rotated through this. In this way, the rotation of the human-powered shaft is done by ring gear 4 and planetary gear 8°8...
・And due to the meshing and deceleration of the planetary gears 8, 8, . . . and the sun gear 6, the power is transmitted to the output shaft 5.

Therefore, this output reduction 151/C can be reduced so as not to cause the rotational speed of the connected auxiliary parts to reach the manual rotational speed.

Note that if the low-speed rotation time of the human-powered shaft 1 is relatively longer than the high-speed rotation time, as in the case of this loss/M example, the spring clutch mechanism 18 Solenoid 20 i 0 N only when moving
If the solenoid 20 is turned off at other times, that is, when the input shaft 1 is rotating at a low speed, the loss of energization to the solenoid can be prevented.

As is clear from the above description, the present invention provides a planetary gear mechanism between the input shaft and the output 1i+, and uses this planetary gear mechanism ttq to reduce the rotational torque from the human power shaft and transmit it to the output shaft. Therefore, even when the gradual opening for driving the input shaft is about to rotate at a heavy speed, this high-speed rotational torque can be transmitted to the auxiliary parts connected to the output shaft at a reduced speed.

Therefore, it is possible to prevent the situation where the sleeve part is rotated at a full commercial speed above the rotational speed JW suitable for the @a part. Therefore, it is possible to achieve proper operation of the auxiliary parts and to prevent a decrease in efficiency, and in addition, it is possible to save energy and energy, and it is also possible to downsize the auxiliary parts as a whole.

Further, in the present invention, since a solenoid for controlling the driving operation of the spring clutch Tsukisa is provided on the output shaft side, the point at which the rotational speed of the output shaft is decelerated can be arbitrarily selected by operating the solenoid.

[Brief explanation of the drawing]

FIG. 1 shows an embodiment of the present invention with a gold boss 9! ? slI sectional view, Fig. 2 is a cross-sectional view taken along the line ■-■ in Fig. 1, Fig. 3 is a sectional view taken along the line III-III in Fig. 1, and Fig. 4 shows a solenoid brake plunger attached to the annular member. m-III in FIG. 1 showing the pressed state? It is a tn sectional view. 1...Input shaft, 2...Bracket, 4...Ring gear, 5...Output shaft, 6...'V-ngya, 8,8
...planetary gear, 9,9...bin, 10...
Carrier, 11... Support case, j: 3... One-way clutch, 14... Annular part restraint, J7... Coil spring, 17a... One end, 17b... Other end, 1
8... Spring clutch mechanism, 19... Brake plunger, 20... Solenoid, 21... Planetary gear mechanism. 3C Figure 3n Figure 4

Claims (1)

[Claims] An input shaft that receives the output rotation of the engine, a ring gear provided on a bracket integrated with this input shaft, an output shaft connected to auxiliary parts, a sun gear rotatably provided on this output shaft, and this sun gear and r2i+ Nr2! a plurality of planetary gears disposed between the J gear and meshing with the gears; and a carrier provided on the output shaft;
A pin for rotatably supporting each of the planetary gears, a support case for fully rotatably supporting the input shaft and the output shaft, and a support case for preventing the sun gear from rotating in a direction opposite to the ring gear. a one-way clutch disposed between the one-way clutch, an annular member disposed on the outer periphery of the output shaft; One end is solid 1
a coil spring whose other end is fixed to the sun gear; and a brake plunger which presses the outer circumferential direction of the annular member to stop the rotation of the annular member. Rotary drive devices for automotive auxiliary parts that are particularly important.