JPS5938420B2 - Engine auxiliary drive system - Google Patents

Description

[Detailed Description of the Invention] This invention provides an engine water pump, a cooling fan,
It relates to devices that drive auxiliary equipment such as generators and compressors for air conditioners.

In the conventional engine accessory 1 drive device, a drive pulley is directly connected to the end of the engine crankshaft, and driven pulleys of various accessories are driven from this pulley via a belt, a cogged belt, etc.

Therefore, the various auxiliary machines rotate in proportion to the engine rotation speed, and the rotation speed of the auxiliary machines becomes insufficient, especially when the engine rotates at low speed.

For this, set the drive and driven pulley ratios to dog,
It is also possible to configure the auxiliary equipment to rotate at an increased speed even when the engine rotates at low speed, but in this configuration, when the engine rotates at high speed, the auxiliary equipment ζ over-rotates, resulting in a decrease in the durability of the auxiliary equipment. This poses a problem in that it causes an increase in auxiliary equipment operating noise and an increase in engine power loss.

In order to solve this problem, a conventional drive device has been developed in which a planetary gear device is installed between the engine crankshaft and the drive pulley, and the rotation speed of the drive pulley is controlled by the differential movement of this device. Proposed.

For example, in JP-A-53-12329 shown in FIG. 1, a planetary gear unit 4,
A brake device 5 and a one-way clutch 6 are provided, and a sun gear γ is connected to a brake drum 8 and a carrier 9.
is connected to the input shaft 2, the ring gear 10 is connected to the drive pulley 3, and the one-way clutch 6 is interposed between the input shaft 2 and the drive pulley 3.

A brake band 11 is disposed on the brake drum 8 and operates to brake the rotation when the engine speed is below a predetermined number.

In this conventional device, the engine rotation speed is a predetermined number (for example, 1
500 rpm) or less, brake band 11
Since the brake drum 8 is fixed and the sun gear 7 is fixed, the speed 1. Take it out to drive pulley 3.

Furthermore, when the engine speed exceeds the predetermined number, the brake drum 11 is freed and the sun gear γ is freed, so that the input shaft 20 rotations are directly transmitted to the drive pulley by the action of the funway clutch 60.

Therefore, in this device, the rotation speed characteristic of the drive pulley is
It is represented by a broken solid line A in the figure.

The chain line B represents the characteristic when the drive pulley 3 is directly connected to the crankshaft 1.

However, in such a device, a one-way clutch 6 is interposed between the input shaft 2 and the first drive pulley 3, and when the sun gear 7 is released, the one-way clutch 6 directly transfers 20 rotations of the input shaft to the drive pulley. 3. Therefore, if the torque acting on the drive pulley 3 when this one-way clutch is activated is Tout, the torque acting on the input shaft 2 is Taut, and in the end, the load capacity Tone 1 of the one-way clutch 6 is equal to the above-mentioned Taut. Become.

Therefore, this type of one-way clutch must have a load capacity sufficient to withstand the torque T out described above, but a normal one-way clutch has a shape and weight that are proportional to its load capacity. Therefore, in the above-mentioned configuration, there is a problem that the one-way clutch becomes large and heavy due to the high load capacity, and as a result, the entire device also becomes large and heavy.

This invention was made by focusing on such conventional problems, and it connects the input shaft to a carrier and the output shaft to a ring gear, and brakes the sun gear to increase the output rotation speed above a predetermined engine rotation speed. The purpose of this invention is to solve the above problem by interposing a one-way clutch between the ring gear and the sun gear in a configuration designed to reduce speed.

The present invention will be explained below based on the drawings.

FIG. 3 is a diagram showing an embodiment of the Q invention.

In the figure, 1 connects the input shaft 2 to the key 12 and bolt 13.
14 is a fixed wall forming a part of the engine; 15 is a rotating sleeve rotatably supported by a bearing 16 around the input shaft 2; 3 is this rotating sleeve 15; This is a drive pulley supported by a bearing 17 around the periphery of the drive pulley.

A driven pulley 18 is connected to the drive pulley 3 via a belt 19, and is connected to an auxiliary machine (not shown).

The planetary gear device 20 has a sun gear 21 integrally formed with the rotating sleeve 15, and a ring gear 22.
is formed integrally with the drive pulley 3, and further a carrier 24 supporting a planetary gear 23 meshing with the sun gear 21 and ring gear 22 is formed integrally with the input shaft 2.

Further, a flange 25 is formed on the outer periphery of the rotating sleeve 15, and the inner side of an annular leaf spring 26 is attached thereto, and a similarly annular friction plate 27 is secured to this leaf spring 26 with screws 28.

This friction plate 27 is arranged opposite to the electromagnetic solenoid 29 fixed to the fixed wall 14, and when the solenoid 29 is excited, it is attracted from the free state position to the electromagnetic solenoid 29 side, and is pressed against the friction surface 30 of the electromagnetic solenoid 29. The rotation of the rotating sleeve is braked by 150 rotations.

A one-way clutch 32 is interposed between the sleeve 15 and the drive pulley 3, in other words, between the sun gear 21 and the ring gear 22.

In the figure, 33 is an oil seal, 34 is a planetary gear 23
35 is a pin shaft that supports the carrier 24, 35 is a disk) I
A timing gear for driving the J computer, and 36 a front cover.

Although the electromagnetic solenoid 230 control circuit is not shown, the electromagnetic solenoid 230
The configuration is such that power is supplied to the

Next, the action will be explained.

When the engine is started and crankshaft 1 rotates,
Along with this, the carrier 24 rotates.

Then, the engine rotation speed is a predetermined value, for example, 1500 rpm.
When the rotational speed is less than m, the electromagnetic solenoid 29 is excited, so the friction plate 27 is attracted to the friction surface 30 against the leaf spring 26, and the rotation of the sun gear 210 is braked and fixed.

Therefore, a differential movement occurs between the ring gear 22 and the carrier 24, and the ring gear 22, ie, the first drive pulley 3, is rotated at a higher speed than the carrier 24, ie, the input shaft 2.

The speed increasing ratio is (ZR + ZS)/ZR (where ZR and ZS are the numbers of teeth of the ring gear and sun gear, respectively).

Note that the speed increasing ratio is between 1 and 2.

On the other hand, when the engine speed exceeds the predetermined value, the electromagnetic solenoid 29 becomes de-energized and the sun gear 21 becomes free.

Therefore, differential motion in the planetary gear device 20 is no longer performed, and the one-way clutch 32 interposed between the input shaft 2 and the sun gear 21 causes the sun gear 21 to rotate integrally with the input shaft 2, and furthermore, the ring gear 22, that is, the driving The boo 93 is rotated integrally with the input shaft.

As a result of the above, the engine rotation speed and drive pulley rotation speed characteristics in this embodiment can be made similar to the conventional characteristics shown in Fig. 2, but in this embodiment, the device can be further miniaturized for the following reasons. can be achieved.

That is, in this example, the torque Tou acting on the input shaft (carrier) when the one-way clutch 32 is activated is
t, the torque TR acting on the ring gear and the torque Ts acting on the sun gear 21 are as follows from the relationship of the speed increasing ratio.

Here, since the one-way clutch 32Ω load capacity TOf1e2 interposed between the ring gear 22 and the sun gear 21 is equal to the torque T8 of the sun gear, it becomes R, and since 1+->1, it becomes S.

Therefore, the load capacity T o of the one-way clutch 32
ne2 can now be made smaller than the carrier torque 'l'out, making it possible to use a one-way clutch that is smaller and lighter than the one-way clutch 6 of the conventional device shown in FIG. Accordingly, the entire device can be made smaller and lighter.

In addition, when carrying out this invention, if the rotation ratio of the driving pulley 3 and the driven pulley 18 is configured to be reduced, the speed will increase in the engine low speed range as shown by the chain double-dashed line C in FIG. In the high engine speed range, the amount decreases and each auxiliary device can operate.

In addition, as shown by the broken line in the same figure, the engine speed is reduced only in the high rotation range to prevent the auxiliary equipment from over-speeding, and the durability of the auxiliary equipment is improved, reducing noise caused by the auxiliary equipment drive. Loss of engine output can be suppressed.

As explained above, according to the present invention, the input shaft is connected to the carrier, the drive pulley is connected to the ring gear, and the sun gear is connected to the friction plate to be free or fixed, and the ring gear and sun gear are connected to each other. Since a one-way clutch is inserted between the two, sufficient auxiliary rotation speed can be obtained in the low engine speed range, while preventing overspeed of the complement and generation of noise in the high engine speed range. Furthermore, the load capacity of the one-way clutch can be reduced, making it possible to use a small and lightweight one-way clutch, thereby achieving the effect that the entire device can be made smaller and lighter.

[Brief explanation of the drawing]

Figure 1 is a sectional view of the conventional device, Figure 2 is an output rotation characteristic diagram,
FIG. 3 is a sectional view of an embodiment of the present invention, and FIG. 4 is an auxiliary machine rotation characteristic diagram. 1...Crankshaft, 2...Input shaft, 3
... Drive pulley, 15 ... Sleeve,
20... Planetary gear device, 21... Sun gear, 22...-Ring gear, 23...
Planetary gear, 24...Carrier, 26...
...Plate spring, 27...Friction plate, 29...
...Electromagnetic solenoid t32...One-way clutch.

Claims (1)

[Scope of Claims] 1. A carrier of a planetary gear device is integrally provided on an input shaft connected to the crankshaft of an engine, while a ring gear is provided on an output member such as a 1 drive pulley for driving an auxiliary machine, and a ring gear is provided on an output member such as a drive pulley, and a ring gear is further provided on a sun gear. is configured so that the sun gear can be in a free state or in a state fixed to a fixed part of the device by connecting friction plates, and a one-way clutch is interposed between the ring gear and the sun gear, and the engine speed is below a predetermined value. 1. An engine auxiliary drive device characterized in that a sun gear is set in a fixed state when the engine speed is a predetermined value or more, and the sun gear is set in a free state when the engine speed is equal to or higher than a predetermined value. 2 The friction plate is supported by a spring, and the friction plate is normally kept in a free state by the force of the spring, but when the electromagnetic solenoid provided in the fixed part of the device is energized, the friction plate is attracted to the electromagnetic solenoid against the force of the spring. 2. The engine auxiliary drive device according to claim 1, wherein the sun gear is fixed by rotating the sun gear.