JPH08225027A - Auxiliary machine driving device - Google Patents

Abstract

PURPOSE: To improve the transmitting efficiency of the motive power, by providing the first gear connected to an input shaft side which is rotated by the driving force of an engine, and the second gear connected to the output shaft of an auxiliary machine side, and providing a planetary gear type differential mechanism whose change gear ratio is converted by the rotational frequency control of the third gear. CONSTITUTION: An auxiliary machine driving device 1 used for driving a supercharger 3 has a planetary type differential mechanism 7, and it is composed of an internal bear 41, a pinion gear 43, and the like. And it has a chain transmitting mechanism 9 and its sprocket 105 is held on an input shaft 5 as well as welded to the internal gear 41. And a sprocket 107 is fixed to a parallel shaft 113, and a hydraulic motor 11 is connected to the right side part of the parallel shaft 113 penetrating a casing 25. And by regulating the torque and converting the rotating direction of the hydraulic motor 11, the rotation of the internal gear 41 is controlled, and the change gear ratio of the differential mechanism 7 is made regulatable.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an accessory drive system for transmitting a driving force of an engine to an accessory of a vehicle.

[0002]

2. Description of the Related Art Japanese Unexamined Patent Publication No. 4-219552 discloses a "transmission" as shown in FIG.
The publication discloses a "capacity control device for a positive displacement rotary compressor" as shown in FIG.

A transmission 201 of FIG. 8 has an input shaft 203,
Planetary gear type speed increasing mechanism 205, low speed side output shaft 20
7, high speed side output shaft 209, one-way clutch 211,
The electromagnetic clutch 213, the output side pulley 215, etc. are provided. The internal gear 217 of the speed increasing mechanism 205 is fixed to the housing 219, each output shaft 207, 209 constitutes a carrier of the pinion gear 221, and the sun gear 223.
Is formed on the high speed side output shaft 209. The electromagnetic clutch 213 is arranged between the high speed side output shaft 209 and the pulley 215, and the one-way clutch 211 is arranged between the low speed side output shaft 207 and the pulley 215.

The driving force input to the input shaft 203 is increased by the speed increasing mechanism 205 to rotate the high speed side output shaft 209 and rotate the low speed side output shaft 207 at the same speed as the input shaft 203.
The one-way clutch 211 is the high speed side output shaft 2 at this time.
09 and the relative rotation of the low speed side output shaft 207 are permitted.

When the electromagnetic clutch 213 is connected, the pulley 215 is connected to the high speed side output shaft 209 and rotates at high speed. When the electromagnetic clutch 213 is released, the driving force causes the pulley 215 to rotate at a constant speed via the one-way clutch 211.

Further, the displacement control device 225 of FIG. 9 generates a control pressure from the discharge gas pressure of the belt type continuously variable transmission 229 and the displacement type rotary compressor 227 for transmitting the rotation of the engine to the displacement type rotary compressor 227. The control pressure generating means 231 and the pressure medium converting means 233 for converting the pressure generated by the control pressure generating means 231 into the hydraulic pressure for shifting operation of the belt type continuously variable transmission 229 are provided.
The discharge gas pressure of the positive displacement rotary compressor 227 is utilized for the speed change operation of the belt-type continuously variable transmission 229 by means of 1 and the pressure medium conversion means 233.

[0007]

Since the transmission 201 does not rely on friction for power transmission, the power transmission efficiency is good. But,
The capacity of the auxiliary machine suddenly changes at the time of gear shifting, the durability of the auxiliary machine is impaired, and since the number of gears is only two, the rotational speed of the auxiliary machine cannot be finely adjusted according to the change of the engine rotational speed. For example, when the supercharger is driven, the supercharging pressure greatly changes as the gear shifts. Therefore, smooth supercharging is not performed around the engine speed at which the transmission 201 is shifted, and the behavior of the vehicle body changes. Becomes unstable.

On the other hand, since the capacity control device 225 is a continuously variable transmission by the belt type continuously variable transmission 229, there is no sudden change in the auxiliary function force due to the gear shift. However, each pool 235, 2
The speed range of the belt type continuously variable transmission 229 determined by the pitch diameter of 37 is limited to a narrow range. Therefore, if the capacity of each type of auxiliary machine is different, or if the capacity of the same type of auxiliary machine is different, the belt type continuously variable transmission characteristics are different. A continuously variable transmission and a capacity control device must be prepared. In addition to this, the belt type continuously variable transmission 229 that relies on friction for power transmission has a poor power transmission efficiency and cannot transmit a large amount of power due to the slip of the belt 239.

Therefore, an object of the present invention is to provide an accessory drive system having a wide range of stepless speed change characteristics and good power transmission efficiency.

[0010]

According to a first aspect of the present invention, there is provided an auxiliary machine driving device, wherein a first gear connected to an input shaft side which is rotated by a driving force of an engine and a second gear connected to an output shaft of the auxiliary machine side. And a third gear, and a motor for controlling the rotation speed of the third gear via a power transmission mechanism and a planetary gear type differential mechanism in which the gear ratio is changed by controlling the rotation speed of the third gear. It is characterized by having and.

The accessory drive system according to claim 2 is the accessory drive system according to claim 1 further comprising a clutch for locking the rotation of the third gear.

According to another aspect of the present invention, in the accessory drive system, the clutch is a multi-plate clutch, and an oil pump rotatably driven by the input shaft and a hydraulic actuator for connecting the multi-plate clutch by receiving operating hydraulic pressure from the oil pump. The auxiliary machine drive device according to claim 2, further comprising: a control valve for controlling the multi-plate clutch by controlling the hydraulic pressure.

The accessory drive system according to a fourth aspect of the present invention comprises a one-way clutch disposed between the third gear and the motor, the one-way clutch allowing the preceding rotation of the third gear with respect to the motor.
Two or three accessory drive devices.

[0014]

According to the accessory drive system of the first aspect, the first gear on the input side and the second gear on the output side are controlled by controlling the rotation speed of the third gear.
The speed of the third gear is changed by the motor connected to the third gear (rotation control gear) via the power transmission mechanism by using the speed changing function of the planetary gear type differential mechanism whose gear ratio changes with the gear. It is configured so that the gear shift operation is performed by changing the rotation direction.

Since the rotation speed of the third gear can be adjusted steplessly by the motor, it is possible to carry out continuously variable transmission similar to the belt type continuously variable transmission as in the conventional example shown in FIG. Therefore, the rotational speed of the auxiliary machine does not suddenly change due to the gear shift, the durability of the auxiliary machine can be prevented from being lowered, and the capacity of the auxiliary machine can be precisely adjusted in response to the change of the engine rotational speed. . or,
If the gear ratio of each gear is set in this way, a wide speed change range can be obtained. Therefore, one type of auxiliary machine drive device can be widely used for various auxiliary machines. Since it is not necessary to prepare an auxiliary drive device for each capacity, the cost is reduced as a whole.

Further, since the power transmission does not depend on friction, it is possible to transmit large power with good power transmission efficiency.

An accessory drive device according to a second aspect is the accessory drive device according to the first aspect, further comprising a clutch for locking the rotation of the third gear, and similar to the accessory drive device according to the first aspect. , The durability of the auxiliary machine is improved by the continuously variable transmission function, the capacity of the auxiliary machine can be precisely adjusted in response to changes in the engine speed, and a wide speed change range can be obtained, so that the type and capacity of the auxiliary machine can be changed. It is not necessary to prepare a separate accessory drive device, the cost is low, the power transmission efficiency is good, and large power can be transmitted.

Moreover, since the clutch for locking the rotation of the third gear is provided, the load on the motor is reduced to that extent and the durability is improved.

According to a third aspect of the present invention, there is provided an auxiliary equipment drive device according to the second aspect, wherein a multi-plate clutch is used as a clutch, and an oil pump driven by the input shaft and an operating hydraulic pressure from the oil pump are received. A hydraulic actuator for engaging the multi-disc clutch and a control valve for controlling the operating hydraulic pressure to engage and disengage the multi-disc clutch are provided, which is similar to the accessory drive system of claim 2. In addition, the durability of the auxiliary machine and the ability to adjust the capacity are improved, and a wide support capacity for various auxiliary machines is obtained, which is low cost,
Power transmission efficiency is good and large power can be transmitted.

Moreover, since the operating means and the control means of the multi-plate clutch are incorporated, such control can be performed within the unit of the accessory drive device, and the handling becomes easy.

The accessory drive system of claim 4 is the same as claim 1 or 2.
In the accessory drive device of the third or third aspect, a one-way clutch that allows the preceding rotation of the third gear with respect to the motor is arranged between the third gear and the motor.
As in the case of the accessory drive device of No. 3 or 3, the durability and capacity adjusting function of the accessory are improved, a wide corresponding ability is obtained for the accessory, the cost is low, the power transmission efficiency is good, and the large power is large. Can be transmitted.

In addition, when the drive of the motor is stopped in the structure of claim 1, and when the drive of the motor is stopped and the connection of the clutch is further released in the structure of claims 2 and 3, the auxiliary equipment side The rotation of the second gear is stopped by the drive resistance of the third gear, and the third gear rotates at a high speed in response to the driving force of the engine. This rotation drives the motor through the power transmission mechanism, and the motor side drives the driving force. If it does not have a recovery function, it will lead to a loss of power. However, even in such a case, in the accessory drive system according to claim 4, the one-way clutch operates from the third gear.
Since power transmission to the motor is cut off, power loss is prevented,
Fuel efficiency is improved.

[0023]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIGS. This embodiment has the features of claims 1, 2, and 3. The left and right directions are the left and right directions in FIGS. 1 and 2, and members and the like without reference numerals are not shown.

As shown in FIGS. 1 and 2, the auxiliary machine driving device 1 of this embodiment is used for driving a supercharger 3 (auxiliary machine).

The accessory drive system 1 includes an input shaft 5, a planetary gear type differential mechanism 7, a chain transmission mechanism 9 (power transmission mechanism), a hydraulic motor 11 (motor), and a multi-plate clutch. Thirteen
(Clutch), hydraulic actuator 15, oil pump 17, output shaft 19, control valve 21, controller 23 and the like.

As shown in FIG. 2, the input shaft 5 is the auxiliary device drive unit 1.
The casing 25 of the bearing 2 from the left end side,
It is supported inside the casing 25 via 7, 29. A seal 31 is provided between the input shaft 5 and the casing 25,
31 is arranged to prevent oil leakage. A sprocket 33 is spline-connected to the left end of the input shaft 5, and is prevented from falling off by a washer 35 and a nut 37. The sprocket 33 is connected to a sprocket on the crankshaft side via a chain 39 (FIG. 1) and is rotated by the driving force of the engine.

The planetary gear type differential mechanism 7 is composed of an internal gear 41, a pinion gear 43, pinion carriers 45, 47, a sun gear 49 and the like.

As shown in FIG. 3, three pinion gears 43 are arranged at equal intervals in the circumferential direction, and each pinion gear 43 is supported by a pinion shaft 53 by a bearing 51. Both ends of each pinion shaft 53 are supported by the left and right pinion carriers 45 and 47, and the left pinion carrier 45 is welded to the input shaft 5. Thus
The driving force of the engine is input from the pinion carriers 45 and 47 to the differential mechanism 7.

The sun gear 49 is spline-connected to the output shaft 19 and is prevented from falling off by the washer 55 and the nut 57. The output shaft 19 is supported on the casing 25 by bearings 59 and 61.

The supercharger 3 includes a speed increasing gear set 63,
Timing gear set 65, screw type air compressor 6
It is composed of 7 etc.

The speed increasing gear set 63 is composed of large-diameter and small-diameter speed increasing gears 69 and 71 meshing with each other, and the timing gear set 65 is composed of large-diameter and small-diameter timing gears 73 and 75 meshing with each other. . Further, the air compressor 67 includes a pair of screw rotors 77 and 79.

A large-diameter speed increasing gear 69 is integrally formed at the right end of the output shaft 19, and a small-diameter speed increasing gear 71 is keyed to a shaft 81 of a screw rotor 77 together with a small-diameter timing gear 75.
They are connected by 83 and are fixed by nuts 85. Further, the large-diameter timing gear 73 is provided with the shaft 87 of the screw rotor 79.
It is fixed by a nut 89 and a power lock mechanism 91.

Each shaft 81, 8 of the screw rotors 77, 79
A compressor casing 97 has a left end supported by a bearing 93 and a right end supported by a bearing 95. The seat 7 is mounted between both ends of the shafts 81 and 87 and the compressor casing 97. Le 99, 101
This prevents air leakage.

The rotation of the output shaft 19 is accelerated by the speed increasing gear set 63, and the air compressor 67 is rotationally driven through the timing gear set 65, and the driven air compressor 67 is driven.
Is the intake air sucked through the suction holes,
The pressure is fed in the axial direction between them, and the gas is discharged from the discharge holes 103 and supplied to the engine.

The chain transmission mechanism 9 is composed of a pair of sprockets 105 and 107 and a chain 109 connecting them as shown in FIGS. The sprocket 105 is welded to the internal gear 41 of the differential mechanism 7, and the roller bearing 11 is mounted on the input shaft 5.
It is supported through 1. The sprocket 107 is fixed to the parallel shaft 113. The parallel shaft 113 is supported by the casing 25 via bearings 115 and 117, and the hydraulic motor 11 is connected to the right end portion passing through the casing 25. A seal 119 is arranged between the parallel shaft 113 and the casing 25 to prevent oil leakage.

Thus, the hydraulic motor 11 is connected to the internal gear 41 of the differential mechanism 7 via the chain transmission mechanism 9. As will be described later, the rotation of the internal gear 41 can be controlled by adjusting the torque of the hydraulic motor 11 and switching the rotation direction, and the gear ratio of the differential mechanism 7 can be adjusted.

The multi-plate clutch 13 is arranged between the casing 25 and the internal gear 41. When the multi-plate clutch 13 is engaged, the rotation of the internal gear 41 is locked, and when the multi-plate clutch 13 is released, the internal gear 41 becomes rotatable by the torque of the hydraulic motor 11.

The hydraulic actuator 15 is a hydraulic cylinder 1.
21 and a piston 123, and a hydraulic cylinder 121
Is supported on the casing 25 via bearings 125 and 127. Stop plate 1 fixed to casing 25
Coil spring 13 between 29 and piston 123
1 is arranged.

The oil pump 17 is arranged between the input shaft 5 and the casing 25, and is driven by the rotation of the input shaft 5. The hydraulic pressure generated by the oil pump 17 is supplied to the hydraulic actuator 15 via the oil passage 133 of the casing 25 and the oil passage 135 of the hydraulic cylinder 121.

The control valve 21 is arranged so that the oil passage 133 can be opened and closed. When the oil passage 133 is opened, the hydraulic pressure is supplied to the hydraulic actuator 15, and the oil passage 13 is opened.
When 3 is closed, the supply of operating hydraulic pressure to the hydraulic actuator 15 is stopped.

When the working oil pressure is supplied to the hydraulic actuator 15, the piston 123 pushes and engages the multi-plate clutch 13, and when the working oil pressure supply is stopped, the coil spring 131 causes the piston 123 to move backward. The plate clutch 13 is released.

Further, as shown in FIG. 1, signals from an engine speed sensor, an accelerator pedal depression angle sensor, a manual switch in the driver's seat, etc. are input to the controller 23. The controller 23 controls the torque of the hydraulic motor 11 and switches the rotation direction based on these signals.
The rotation speed and the rotation direction of the internal gear 41 are controlled via the chain transmission mechanism 9, and the control valve 21 is opened / closed by the signal S to lock and unlock the internal gear 41.

Next, referring to FIGS. 5 and 6, the shifting state of the differential device 7 under the control of the controller 23 will be described.

FIG. 5 shows the sun gear 49 (the output shaft 19, the rotary shaft) corresponding to the locked state and the rotated state of the internal gear 41.
FIG. 7 is an operation state diagram showing a rotating state of a charger 3). 6 is a rotational speed diagram of the input shaft 5 and the output shaft 19 corresponding to FIG. 5, and the graph 137 shows the internal gear 4
1 is the characteristic when the rotation speed Ni is 0 rpm, and the rotation speeds Ni are -1000 rpm and -200 respectively at the upper left.
Graphs 139 and 141 at 0 rpm are drawn. or,
At the bottom right of the graph 137, the rotation speed Ni is 1000 r
Graph 14 of pm, 2000 rpm and 3000 rpm
3, 145 and 147 are drawn. Each of these graphs shows the change in the number of revolutions of the output shaft 19 with respect to the change in the number of revolutions of the input shaft 5 in a state where the number of revolutions Ni is fixed at each number of revolutions. A graph 149 shows a change in the rotation speed of the output shaft 19 when the rotation speed Ni is changed in accordance with the change in the rotation speed of the input shaft 5.

A pattern 1 shown in FIG. 5 is a case where the rotation of the internal gear 41 is locked by the torque of the hydraulic motor 11 with the multi-plate clutch 13 being released, and the differential mechanism 7 is provided with each gear. The engine speed is increased at a constant gear ratio that is determined by the gear ratio. This state corresponds to the graph 137 in FIG. 6, and the rotation speed of the output shaft 19 (supercharger 3) changes in proportion to the rotation speed fluctuation of the input shaft 5 (engine).

The pattern 2 is a case in which the internal gear 41 is rotated at a constant speed in the same direction as the input shaft 5 by the torque of the hydraulic motor 11 with the multi-plate clutch 13 disengaged. In the mechanism 7, the differential of each gear is locked, so that the output shaft 19 rotates in the same direction as the input shaft 5 at a constant speed.

The pattern 3 corresponds to the case where the internal gear 41 is rotated ahead of the input shaft 5 by the torque of the hydraulic motor 11 with the multi-plate clutch 13 released.
The output shaft 19 is decelerated by receiving in the opposite direction the speed increasing component of the differential mechanism 7 in which the internal gear 41 rotates ahead of the sun gear 49. Further, if the internal gear 41 is further accelerated in the same direction, the rotation of the output shaft 19 is stopped.

The states of patterns 2 and 3 are graph 1 in FIG.
Corresponding to the lower right range of 37, the engine output can be reduced by lowering the rotation speed of the supercharger 3 at the time of high speed rotation of the engine or partial load, and the fuel consumption can be improved.

The pattern 4 corresponds to the case where the internal gear 41 is rotated in the opposite direction to the input shaft 5 by the torque of the hydraulic motor 11 with the multi-plate clutch 13 being released, and the output shaft 19 is It rotates at a higher speed than the pattern 1 that locks the internal gear 41. This state is shown in FIG.
In the range corresponding to the upper left of the graph 137, the supercharger 3 can be rotated at a high speed when the engine is rotating at a low speed to increase the supercharged air and increase the engine output. Furthermore, in the rotation direction opposite to the input shaft 5, the internal gear 4
By controlling the number of revolutions of 1, the rotation of the supercharger 3 can be controlled as shown by a graph 149, for example, and a desired supercharging characteristic can be obtained.

The pattern 5 is a case where the internal gear 41 is locked by the multi-plate clutch 13 and the rotation of the hydraulic motor 11 is stopped, and like the pattern 1, the output shaft 1
9 is speeded up by a speed-up ratio specific to the differential mechanism 7. in this case,
Since the hydraulic motor 11 is stopped, the load on the hydraulic motor 11 is reduced, the durability is improved accordingly, and the output loss of the engine is reduced by the driving force of the hydraulic motor 11.

Thus, the accessory drive system 1 is constructed.

As described above, the accessory drive system 1 controls the rotation of the internal gear 41 by the hydraulic motor 11 so that the supercharger 3 has the characteristics shown in the graph 149.
The rotation of can be adjusted steplessly. In this way, continuously variable transmission equivalent to that of the belt type continuously variable transmission as in the conventional example of FIG. 9 is possible, and the rotation speed does not suddenly change in accordance with the shift, so
It is possible to prevent deterioration of the durability of the supercharger 3 and precisely adjust the rotation of the supercharger 3 in response to changes in the engine speed to obtain a desired supercharging characteristic. it can. In this way, smooth supercharging is performed over the entire range of the speed change speed, and the behavior of the vehicle body is stabilized.

By setting the gear ratio of the differential mechanism 7, a wide speed range can be obtained in addition to the control of the rotational speed and rotational direction of the hydraulic motor 11, so that the accessory drive device 1 can be widely used for various accessories. This is applicable, and unlike the conventional example, it is not necessary to prepare an individual accessory drive device for each type and capacity of the accessory, and the cost is reduced as a whole. In addition, the accessory drive device 1
Unlike the belt type continuously variable transmission, since the power transmission does not depend on friction, the power transmission efficiency is high and a large power can be transmitted.

Further, since the multi-plate clutch 13 for locking the internal gear 41 is provided, the load on the hydraulic motor 11 is reduced as described above, and the durability and fuel consumption of the hydraulic motor 11 are improved. To do.

In addition, the hydraulic actuator 15 for engaging the multi-plate clutch 13 and the oil pump 1 driven by the input shaft 5 to provide the hydraulic pressure to the hydraulic actuator 15.
7 and a control valve 21 for controlling this hydraulic pressure
By including the operation means and the control means of the multi-plate clutch 13, the accessory drive device 1 is unitized, the accessory drive device 1 can be controlled within the unit, and the handling becomes easier accordingly.

Next, a second embodiment of the present invention will be described with reference to FIG. The accessory drive device 151 of this embodiment has the features of claim 4. In the description below, members having the same functions as those of the first embodiment are designated by the same reference numerals,
A description of these functional members will be omitted.

As shown in FIG. 7, in the accessory drive device 151, the internal gear 41 is the one-way clutch 153.
It is connected to the sprocket 105 of the chain transmission mechanism 9 via. In this one-way clutch 153, the internal gear 41 has a sprocket 105 (hydraulic motor 1
1) It is arranged in a direction in which it can be rotated ahead of.

As in the first embodiment, the accessory drive device 151 is excellent in the durability of the accessory and the ability to adjust the capacity of the accessory, and has a wide adaptability to various accessories and the power transmission efficiency. It can transmit large power well.

When supercharging is unnecessary, the multi-plate clutch 1
3 is released to bring the internal gear 41 into a free rotation state, and the driving of the hydraulic motor 11 is stopped,
The supercharger 3 is stopped. At this time, the rotation of the internal gear 41 is cut off from the hydraulic motor 11 by the one-way clutch 153, the rotation of the internal gear 41 drives the hydraulic motor 11 unnecessarily, and the driving resistance of the hydraulic motor 11 is increased. It is possible to prevent the supercharger 3 from being unnecessarily driven by being engaged with the internal gear 41.

Therefore, loss of engine output is prevented,
Fuel efficiency is improved.

This accessory drive device 151 has a graph 137 in FIG. 6 and an output shaft 19 (supercharger) in the upper left range.
3) can be controlled.

In each of the embodiments, the driving force of the engine is input to the pinion carrier and the internal gear is used as the rotation control gear. However, in the present invention, in addition, for example, the driving force is changed from the internal gear. It may be configured to input and control the rotation of the pinion carrier (pinion gear).

The motor for controlling the rotation of the rotation control gear is not limited to the hydraulic motor, but may be, for example, an electric motor or another rotary driving force source.

The clutch is not limited to the multi-plate clutch, but may be another friction clutch or a dog clutch.

The power transmission mechanism is not limited to the chain transmission mechanism, but may be, for example, a belt transmission mechanism or a gear transmission mechanism.

Unlike the second embodiment, the one-way clutch is arranged not only between the third gear and the power transmission mechanism but also at any place between the third gear and the motor. May be.

Needless to say, the auxiliary equipment is not limited to the supercharger. Due to its wide rotation speed control range and precise rotation speed control function, the accessory drive device of the present invention can perform desired rotation speed control for auxiliary machines of different types and capacities and bring out the required capacity. it can.

[0068]

According to the first aspect of the present invention, the auxiliary equipment drive device utilizes the speed change function of the planetary gear type differential mechanism, and controls the rotation speed and rotation direction of the third gear (rotation control gear) by the motor. Then, the shift operation is performed.

Therefore, the rotation speed of the third gear can be adjusted steplessly via the motor, and a continuously variable transmission function equivalent to that of the belt type continuously variable transmission apparatus of the conventional example can be obtained. Therefore, the rotation speed does not suddenly change, the durability of the auxiliary machine is prevented from lowering, and the ability of the auxiliary machine can be precisely adjusted according to the change of the engine speed. In addition to the control of the number of rotations and the direction of rotation of the motor, a wide gear change range can be obtained by setting the gear ratio of the gears, so one accessory drive unit can be widely used for various accessories. Unlike the above, there is no need to prepare an individual accessory drive device for each type and capacity of the accessory, and the cost is reduced as a whole. Further, since the power transmission does not depend on friction, the power transmission efficiency is good and a large amount of power can be transmitted.

According to a second aspect of the present invention, there is provided an auxiliary equipment drive device according to the first aspect, further comprising a clutch for locking the rotation of the third gear. , The durability of the auxiliary machine is improved by the continuously variable transmission function, the capacity of the auxiliary machine can be precisely adjusted according to the change of the engine speed, and a wide speed change range can be obtained. It is not necessary to prepare a separate accessory drive device, the cost is low, the power transmission efficiency is good, and large power can be transmitted.

Moreover, since the clutch for stopping the rotation of the third gear is provided, the load on the motor is reduced to that extent and the durability is improved.

According to a third aspect of the present invention, there is provided an auxiliary equipment drive device according to the third aspect, which is the auxiliary equipment drive device according to the second aspect, wherein a multi-plate clutch is used as a clutch and the oil pump is driven by an input shaft. And a hydraulic actuator that receives the operating hydraulic pressure from the oil pump and engages the multiple disc clutch,
And a control valve for controlling the hydraulic pressure to engage and disengage the multi-disc clutch.
Similar to the accessory drive device of (1), the durability of the accessory and the ability to adjust the capacity are improved, a wide adaptability to various accessories is obtained, and the power transmission efficiency is good and a large power can be transmitted.

Moreover, since the operating means and the control means for the multi-plate clutch are incorporated in the unit, such control can be performed in the accessory drive device unit, and the handling is extremely easy.

The accessory drive system of claim 4 is the same as claim 1 or claim 2.
In the accessory drive device of the third or third aspect, a one-way clutch that allows the preceding rotation of the third gear with respect to the motor is arranged between the third gear and the motor.
Alternatively, similarly to the accessory drive device of No. 3, the durability and capacity adjusting function of the accessory are improved, a wide corresponding capability is obtained for the accessory, the power transmission efficiency is good, and large power can be transmitted.

Further, in the constitution of claim 1, when the driving of the motor is stopped, and in the constitutions of claims 2 and 3, the driving of the motor is stopped and the clutch is disengaged. Three
A large power loss caused by the motor being uselessly driven by the high speed rotation of the gear is prevented by the one-way clutch blocking the rotation from the third gear to the motor, and the fuel consumption is improved accordingly.

[Brief description of drawings]

FIG. 1 is a configuration diagram of a first embodiment of the present invention.

FIG. 2 is a sectional view showing a mechanism portion of the first embodiment.

FIG. 3 is a side view of a differential mechanism portion used in the first embodiment.

FIG. 4 is a view as viewed in the direction of the arrow A in FIG. 2;

FIG. 5 is an operation state diagram of the first embodiment.

FIG. 6 is an input rotational speed-output rotational speed diagram showing the operating state of FIG.

FIG. 7 is a sectional view showing a second embodiment of the present invention.

FIG. 8 is a sectional view of a conventional example.

FIG. 9 is a cross-sectional view of another conventional example.

[Explanation of symbols]

 1, 151 Auxiliary machine drive device 3 Supercharger (auxiliary machine) 5 Input shaft 7 Planetary gear type differential mechanism 9 Chain transmission mechanism (power transmission mechanism) 11 Hydraulic motor (motor) ) 13 multi-plate clutch (clutch) 15 hydraulic actuator 17 oil pump 19 output shaft 21 control valve 41 internal gear (third gear) 43 pinion gear (first gear) 49 sun gear (second gear) 153 one-way clutch

Claims (4)

[Claims] 1. A first gear connected to an input shaft side, which is rotated by a driving force of an engine, a second gear connected to an output shaft on an auxiliary machine side, and a third gear. An auxiliary machine drive device comprising: a planetary gear type differential mechanism whose speed ratio is changed by rotation speed control, and a motor for controlling the rotation speed of a third gear via a power transmission mechanism. 2. The accessory drive system according to claim 1, further comprising a clutch for locking the rotation of the third gear. 3. The clutch is a multi-plate clutch,
An oil pump that is rotationally driven by the input shaft, a hydraulic actuator that receives the operating hydraulic pressure from the oil pump and connects the multiple disc clutch, and a control valve that controls the operating hydraulic pressure to operate the multiple disc clutch. Claim 2 provided
Accessory drive device. 4. The accessory drive system according to claim 1, further comprising a one-way clutch disposed between the third gear and the motor, the one-way clutch allowing the preceding rotation of the third gear with respect to the motor.