JPS647219Y2 - - Google Patents

Description

[Detailed description of the invention] The invention is applicable to, for example, a power steering pump,
This invention relates to a rotation drive device for automobile auxiliary parts such as a water pump or a cooler compressor.

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

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 can be sped up using the above-mentioned pulleys, etc.
Alternatively, the auxiliary parts themselves are made larger to obtain high output.

However, auxiliary parts need to receive sufficient rotational input from the engine to drive the auxiliary part itself, but as the rotational speed increases, efficiency decreases above a certain number of rotations. Considering this, it is not necessarily required that the input rotational speed to the auxiliary parts be proportional to the engine rotational speed. In order to save energy and reduce the size and weight of auxiliary parts, when the engine is in the high-speed rotation range, the input rotation from the engine to the auxiliary parts should be decelerated to drive the auxiliary parts. is required.

In order to meet such requests, the applicant of this case,
When the input shaft is rotating at a low speed, the output shaft is driven to rotate at the same rotational speed as the input shaft by activating the spring clutch mechanism, while the input shaft attempts to rotate at a high speed higher than a certain set value. In this case, by driving the planetary gear mechanism without activating the spring clutch mechanism with the solenoid, the output shaft is rotated at a speed lower than that of the input shaft, thereby making it suitable for auxiliary parts. This patent application proposes a rotational drive device for automobile auxiliary parts that can avoid the situation where the auxiliary parts rotate at high speeds when the rotational speed exceeds the rotation speed.
No. 161135 (see Japanese Patent Application Laid-open No. 59-50255).

Therefore, an outline of the rotary drive device proposed by the present applicant (hereinafter referred to as the previously proposed rotary drive device) will be explained based on FIGS. 1 to 4.

As shown in FIG. 1, an input shaft 1 that receives output rotational torque from an engine is integrally formed with a bracket 2 whose overall cross section is approximately U-shaped. On the surface, ring gear 4
is engraved. On the other hand, a sun gear 6 is rotatably attached to the output shaft 5 connected to the auxiliary parts, and between the ring gear 4 and the toothed part 7 carved on the outer peripheral surface of one end 6a of the sun gear 6. As shown in FIG.
...is placed. Each of these planetary gears 8, 8, . . . is rotatably supported by a plurality of pins 9, 9, . Each of these pins 9, 9...
is one side surface 10a of a carrier 10 formed to protrude in the outer radial direction at one end 5a of the output shaft 5 on the input shaft 1 side.
They are planted at equal intervals in the circumferential direction. In this way, between the input shaft 1 and the output shaft 5, the ring gear 4, the sun gear 6, and each planetary gear 8, 8...
A planetary gear mechanism 2 composed of ... and a carrier 10
1 is provided.

The input shaft 1 and the output shaft 5 are connected to a support case 11
between this support case 11 and the outer circumferential surface 12 of the other end 6b of the sun gear 6 described above. A one-way clutch 13 is interposed to prevent rotation in the clockwise direction. Therefore, the direction of rotation of the sun gear 6 is determined by the one-way clutch 13.

As shown in Fig. 3, an annular member 14 made of, for example, synthetic resin material is fitted at a diametrical distance to the outer periphery of the output shaft 5, so as to straddle an annular stopper portion 15 provided at the middle of the output shaft 5 and an annular projection 16 extending from the other end 6b of the sun gear 6 along the output shaft 5. A coil spring 17 is interposed and disposed between the annular member 14 and the annular stopper portion 15 and the annular projection 16. One end 17a of the coil spring 17 is embedded in the annular member 14 and fixed to the annular member 14, as shown in Fig. 3. The other end 17b of the coil spring 17 is wound around the outer periphery of the sun gear 6. The coil spring 17
is wound around the output shaft 5 in the direction opposite to the direction of rotation of the output shaft 5 (the direction opposite to the arrow P in FIG. 3). The coil spring 17 and the annular member 14 constitute a spring clutch mechanism 18.

At a position facing the outer peripheral surface 14a of the annular member 14, there is a solenoid 20 having a brake plunger 19 that presses the outer peripheral surface 14a and stops rotation of the annular member 14 by a frictional force with the outer peripheral surface 14a. is installed. The brake plunger 19 of the solenoid 20 is spaced apart from the outer circumferential surface 14a of the annular member 14 under normal conditions.At this time, the output shaft 5 and the sun gear 6 rotate together, and when the spring clutch mechanism 18 is released, Only the outer peripheral surface 14a of the annular member 14 is pressed against it.

Next, the operation of the rotary drive device having the above configuration will be explained.

Now, if the engine rotation speed is low, the third
As shown in the figure, the tip 19a of the brake plunger 19 of the solenoid 20 is separated from the outer peripheral surface 14a of the annular member 14. Then, the input shaft 1, which is rotating at low speed in response to the output rotational torque from the engine,
The rotation 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 connected to the ring gear 4.
However, the sun gear 6 tries to rotate in the direction opposite to the rotational direction of the input shaft 1 (direction of arrow P in FIG. 2) (direction of arrow R' in the same figure), but the sun gear 6
3 prevents rotation in the opposite direction, the planetary gears 8, 8 begin to rotate (revolution) in the direction of arrow P in FIG. 2 due to the reaction force. Therefore, the output shaft 5 begins to rotate via the pins 9, 9, . . . , on which the planetary gears 8, 8, .
As the output shaft 5 rotates, the coil spring 17 wraps around the outer peripheral surface 15a of the annular stopper portion 15 of the output shaft 5, and the output shaft 5 and the coil spring 17 begin to rotate together. On the other hand, the other end 17b of the coil spring 17 is connected to the sun gear 6.
Since the output shaft 5 and the sun gear 6 are frictionally engaged with the annular protrusion 16, the output shaft 5 and the sun gear 6 rotate together, and as a result, the planetary gears 8, 8, . Rotates integrally with sun gear 6 and output shaft 5. On the other hand, input shaft 1
Also, since the ring gear 4 provided at one end meshes with the planetary gears 8, 8, . . . , the input shaft 1 and the output shaft 5 rotate together.

On the other hand, when the engine is about to start rotating at a high speed higher than a certain set value, as shown in FIG.
a against the outer peripheral surface 14a of the annular member 14.
Then, the rotation of the annular member stops, and one end of the annular member stops rotating.
The coil spring 17 in which the coil spring 7a is embedded cannot be wound around the outer peripheral surface 15a of the annular stopper portion 15 of the output shaft 5. Therefore, the output shaft 5 no longer rotates the sun gear 6 integrally. On the other hand, the rotation of the input shaft 1 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 sun gear 6 attempts to rotate in the opposite direction (direction of arrow R' in the figure) to the rotation direction of the input shaft 1 (direction of arrow P in FIG. 2) with respect to ring gear 4. , one-way clutch 13 prevents its 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 planetary gears 8, 8...
... starts to mesh with the sun gear 6 and rotate (revolution) in the direction of arrow P in FIG. This planetary gear 8,
8... rotates the output shaft 5 via the pins 9, 9... and the carrier 10.
In this way, the rotation of the input shaft 1 is caused by the ring gear 4, the planetary gears 8, 8... and the planetary gears 8, 8...
...and the sun gear 6 mesh to reduce the output shaft 5.
This will be communicated to Therefore, the input rotational speed of the auxiliary equipment parts connected to the output shaft 5 can be reduced so as not to become unnecessarily high.

By the way, in the previously proposed rotary drive device described above, the solenoid 20 for stopping the rotation of the annular member 14 is fixed to the support case 11 at a position in the radial direction of the annular member 14. Brake plunger 19 provided at 20
When the spring clutch mechanism 18 is actuated, the plunger 19 is projected radially inward and the tip of the plunger 19 is pressed against the outer peripheral surface 14a of the annular member 14. Therefore, the annular member 14 becomes eccentric with respect to the output shaft 5 due to the pressure of the plunger 19, and as a result, the inner circumferential surface of the coil spring 17 hits the outer circumferential surface of the output shaft 5, increasing rotation loss.

In addition, in the previously proposed rotary drive device described above, the radius of the annular member 14 is R, the friction coefficient between the annular member 14 and the plunger 19 is μ, and the annular member 1
4, the braking torque T of the plunger 19 against the annular member 14 can be expressed as T=FμR.
Since the tip of the plunger 19 is pressed against the outer circumferential surface 14a of the annular member 14, sufficient braking torque T cannot be obtained. 1
9 had to be made sufficiently large. Therefore, there was a drawback that a large amount of power consumption was required to be supplied to the solenoid 20.

In view of the shortcomings of the existing proposals, the present invention is designed to avoid an increase in energy loss due to the pressure contact of the coil spring against the output shaft when the spring clutch mechanism is operated, and to maintain a predetermined pressing force of the solenoid plunger against the annular member. The object of the present invention is to provide a rotary drive device that can obtain a braking torque larger than that of previously proposed braking torques.

Hereinafter, embodiments of the present invention will be described based on the drawings. Components that are the same as those in the previous proposal are given the same reference numerals, and redundant explanation will be omitted.

FIG. 5 is a sectional view of a main part showing an embodiment of a rotational drive device for automobile auxiliary parts according to the present invention.

As shown in FIG. 5, a solenoid 20 having a brake plunger 19 for stopping rotation of the annular member 14 is fixed to the side of the support case 11 facing the end surface of the annular member 14. On the other hand, a radial protrusion 22 is formed on the inner circumferential surface 11a of the support case 11, and a friction member 23 is provided between the protrusion 22 and the plunger 19 so as to be unrotatable with respect to the annular member 14. It is being
In this embodiment, the friction member 23 is the annular member 1
It is integrally molded on the outer periphery of 4.

In such a configuration, when a power supply current is supplied to the solenoid 20, the brake plunger 19 provided thereon moves in the axial direction and engages the friction member 2.
3 to the protrusion 22 side. As a result, the friction member 23 is held between the protrusions 22 and the brake plunger 19 from both sides, and the annular member 14 is integrated with the support case 11 via the protrusions 22 and the friction member 23. Become. Then, the coil spring 17 whose one end 17a is embedded in the annular member 14 cannot be wound around the outer peripheral surface 15a of the annular stopper portion 15 of the output shaft 5. Therefore, the output shaft 5 cannot rotate the sun gear 6 integrally. on the other hand,
The rotation of the input shaft 1 is transmitted to each planetary gear 8, 8, .
This is transmitted to the output shaft 5 through the meshing and deceleration of the planetary gears 8, 8, . . . and the sun gear 6 with the planetary gears 8, 8, . Therefore, the input rotational speed of the auxiliary parts connected to the output shaft 5 can be reduced so as not to become unnecessarily high.

In this way, in this embodiment, the annular member 1
A solenoid 20 is fixed to the side of the support case 11 facing the end surface of the friction member 23, and a brake plunger 19 provided thereon presses the end surface 23a of the friction member 23 in the axial direction. Since the rotation of the annular member 14 is restrained, unlike the previously proposed case, the annular member 14 is eccentric with respect to the output shaft 5, and as a result, the coil spring 17 hits the output shaft 5 and generates a large amount of energy. There are no defects such as loss of width.

In addition, in this embodiment, the mounting radius of the solenoid 20 for pressing the annular member 14 is r,
If the coefficient of friction between the annular member 14 and the brake plunger 19 is μ, and the pressing force of the brake plunger 19 when pressing the annular member 14 is F, then the braking torque T of the brake plunger 19 against the annular member 14 is , T=2Fμr.
Here, since the effective radius R of the annular member 14 and the mounting radius r of the solenoid 20 are approximately the same, the first
Compared to the previously proposed case shown in FIGS. Therefore, a certain predetermined braking torque T can be obtained with approximately half the power supply current consumed in the case of the previous proposal.

Next, FIG. 6 shows another embodiment of the present invention. In this embodiment, a friction member 24 is attached to the outer periphery of the annular member 14 and the inner periphery of the support case 11 in a non-rotatable manner. One or more sheets (in this example, a total of 5 sheets) engaged so as to be movable only in the direction
It is composed of annular slide plates 25, 26... Each of these annular slide plates 25, 26...
Of these, the annular slide plate 25 on the annular member 14 side...
As shown in FIG. 7, on the inner circumferential surface of the annular member 4, there are circular protrusions 25a that are loosely fitted into a large number of axial guide grooves 27 formed on the outer circumferential surface 14a of the annular member 4. Annular slide plates 26 are provided at predetermined intervals in the circumferential direction, and are provided on the support case 11 side.
On the outer circumferential surface of the support case 11, protrusions 26a that are loosely fitted into a large number of axial guide grooves 28 formed on the inner circumferential surface 11a of the support case 11 are provided at predetermined intervals in the circumferential direction. It is being

Even with this configuration, the brake plunger 19 presses the axial end surface 24a of each of the annular slide plates 25, 26 . Since the friction member 24 is held between both sides by the plunger 19 and the rotation of the annular member 14 is restrained, the annular member 14 is eccentric with respect to the output shaft 5 when the spring clutch mechanism 18 is operated. Therefore, it is possible to prevent the coil spring 17 from coming into pressure contact with the output shaft 5 and causing frictional heat.

In addition, in this embodiment, the friction member 24 is constituted by one or more annular slide plates 25, 26..., so in this case, the number of annular slide plates 25, 26... If n is T=
It can be expressed in 2nFμr. Therefore, the annular slide plate 2
5, 26, . . ., the predetermined braking torque T can be obtained with a smaller pressing force F.

As is clear from the above explanation, the present invention provides a spring clutch between the output shaft (carrier) and the sun gear, and a brake section (an annular member to which the spring end of the spring clutch is fixed) for switching the spring clutch. The mechanism (including a solenoid for rotating and stopping) is controlled by an external electric signal, and the end face of the friction member (equipped on the annular member of the brake part) is controlled by a brake plunger and a protrusion provided on the support case. Since it is configured to be clamped in the axial direction from both sides, it has the following effects.

(a) The spring clutch installed between the output shaft and the sun gear requires a large capacity to transmit all the torque, but due to its characteristics, the spring clutch is small and can transmit a large capacity of torque, and the shaft part , the entire device can be downsized.

(b) Since the spring clutch is controlled by an external electric signal, it is possible to prevent hunting and stabilize the output rotation speed by providing hysteresis in the switching rotation speed from low speed to high speed and from high speed to low speed. .

(c) It is possible to prevent heat generation due to a half-closed clutch.

(d) The spring clutch can be turned on and off with just enough force to stop the annular member, that is, just enough braking force to prevent the spring from tangling with the output shaft.
Therefore, the power consumption for operating the solenoid to generate the braking force is extremely low, and since the end face of the friction member provided on the annular member is held in the axial direction from both sides, it is possible to It can be reduced to about half compared to the previous year. Note that if the friction member is of a multi-plate type, the power consumption will be further reduced.

(e) Since the cross section of the friction member is axially clamped from both sides, the annular member integrated with the friction member will not be eccentric with respect to the output shaft, and therefore the coil spring will be pressed against the output shaft. There is no possibility that frictional heat will be generated.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view of a main part of a rotary drive device for an already proposed automobile auxiliary component, Fig. 2 is a cross-sectional view taken along the - line in Fig. 1, and Fig. 3 is a - line sectional view in Fig. 1.
The line sectional view, FIG. 4, shows the state in which the brake plunger of the solenoid is pressed against the annular member.
Figure 5 is a cross-sectional view of the main part showing one embodiment of the present invention, Figure 6 is a cross-sectional view of the main part showing another embodiment of the present invention, and Fig. 7 is a support for the friction member. FIG. 3 is a perspective view of a main part showing a state before being accommodated and arranged in a space between a case and an annular member. 1...Input shaft, 2...Bracket, 4...Ring gear, 5...Output shaft, 6...Sun gear, 8,8
...Planetary gear, 9,9...Pin, 10...
Carrier, 11... Support case, 11a... Inner peripheral surface, 13... One-way clutch, 14... Annular member, 14a... Outer peripheral surface, 17... Coil spring, 17a... One end, 17b... Other end, 18...
... Spring clutch mechanism, 19 ... Brake plunger, 20 ... Solenoid, 21 ... Planetary gear mechanism, 22 ... Projection, 23, 24 ... Friction member, 23a, 24a ... Axial end surface, 25, 26
...An annular sliding plate.

Claims (1)

[Scope of Claim for Utility Model Registration] (1) An input shaft that receives the output rotation of an engine, a ring gear provided on a bracket integrated with this input shaft,
an output shaft connected to an auxiliary component; a sun gear rotatably provided on the output shaft; a plurality of planetary gears disposed between the sun gear and the ring gear and meshing with these gears; and the output shaft. a support case that rotatably supports the input shaft and the output shaft; and a support case that prevents the sun gear from rotating in the opposite direction relative to the ring gear. For this purpose, a one-way clutch is provided between the sun gear and the support case, an annular member is provided on the outer periphery of the output shaft, and the annular member is wound around the outer periphery of the output shaft.
and a coil spring having one end fixed to the annular member and the other end wound around the outer periphery of the sun gear, and a brake plunger for stopping rotation of the annular member fixed to the support case. The solenoid is fixed to a side of the support case facing the end surface of the annular member, and a radial protrusion is formed on the inner circumferential surface of the support case, and the protrusion A friction member is interposed between the annular member and the brake plunger so as not to be rotatable with respect to the annular member, and the end face of the friction member is pressed by the brake plunger, so that the protrusion and the brake plunger are pressed. 1. A rotational drive device for automobile auxiliary parts, characterized in that rotation of the annular member is restrained by sandwiching the friction member from both sides with a plunger. (2) The friction member is integrally molded on the outer peripheral surface of the annular member.
A rotary drive device for automobile auxiliary parts as described in 2. (3) The friction member includes one or more annular slide plates that are axially movably engaged with the outer peripheral surface of the annular member, and axially movable with the inner peripheral surface of the support case. 1. A rotational drive device for automobile auxiliary parts as claimed in claim 1, which comprises one or more annular slide plates engaged with.