JPH09324646A - Auxiliary equipment drive - Google Patents

Abstract

(57) [Abstract] [PROBLEMS] To detect a transmission torque and protect an engine and an auxiliary machine from an excessive load. SOLUTION: The pinion gear 55 on the engine side is arranged in a power transmission system that transmits the driving force of the engine to an auxiliary machine 3.
And the sun gear 61 on the auxiliary machine 3 side and the internal gear 53.
A planetary gear type differential mechanism 5 having a multi-plate clutch 7 arranged between the internal gear 53 and the casing 37, and a multi-plate clutch 7 arranged between the case 37 and the casing 37. And a controller 21 for receiving the detection signal of the load measuring device 9 and disengaging the multi-plate clutch 7 to disconnect the accessory 3 from the engine when the transmission torque becomes excessive. .

Description

Detailed Description of the Invention

[0001]

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

[0002]

2. Description of the Related Art A screw type supercharging mechanism 201 as shown in FIG. 7 is disclosed in Japanese Patent Laid-Open No. 3-279689.

This is a supercharger used in a vehicle. The driving force of the engine is input to the input pulley 203 from the crankshaft side via a belt transmission mechanism to increase the speed increasing gear set 20.
The speed is increased by 5, and the screw rotors 211 and 213 of the compressor 209 are rotated via the timing gear set 207. The driven compressor 209 pressurizes the intake air to supercharge the engine.

[0004]

As described above, the rotation speed of the supercharging mechanism 201 changes according to the engine rotation speed.
Therefore, if the engine speed rises extremely, the compressor 209 is heavily loaded, and each gear set 205, 2
07 gear damage and compressor 209
There is a possibility that contact between 1 and 213 or seizure may occur.

Further, when the engine speed extremely rises,
The horsepower consumed for driving the supercharging mechanism 201 increases, the fuel efficiency of the engine decreases, and the supercharging pressure becomes excessive, which imposes a heavy load on the engine.

Such a problem occurs not only in the compressor but also in all auxiliary machines.

[0007] Therefore, an object of the present invention is to provide an auxiliary machine drive device capable of protecting the engine and the auxiliary machine when the transmission torque becomes extremely large.

[0008]

According to a first aspect of the present invention, there is provided an auxiliary machine drive device arranged in a power transmission system for transmitting engine driving force to an auxiliary machine. The first gear on the engine side and the first gear on the auxiliary machine side. A planetary-gear type differential mechanism having two gears and a third gear, a clutch arranged between the third gear and the stationary member, and a transmission arranged between the clutch and the stationary member. A load measuring device for detecting torque and a controller for receiving a detection signal of the load measuring device are provided.

In the accessory drive system according to the first aspect, when the third gear is connected to the stationary member by the clutch to lock the rotation,
The drive force of the engine is transmitted to the auxiliary machine via the planetary gear type differential mechanism, and the load measuring device arranged between the clutch and the stationary member detects the transmission torque, so that the auxiliary machine is driven. However, the transmitted torque can be detected.

Therefore, if the change in the transmission torque is monitored by the controller, when the engine speed increases and the transmission torque becomes abnormally large, the necessary measures for reducing the load on the auxiliary machine and the engine are taken. Therefore, the auxiliary machine and the engine are protected from excessive loads, damage and seizure are prevented, and durability is improved.

According to a second aspect of the present invention, there is provided the auxiliary device driving device according to the first aspect, wherein the load measuring device is a stationary member.
The housing, the engaging portion integrally formed with the clutch member and penetrating into the housing, the damper disposed between one side of the engaging portion in the rotation direction and the housing, and the load detection. And a spring arranged between the other side in the rotation direction of the engaging part and the housing part, the torque is detected from the load detected by the load detector and the distance from the load detector to the rotation center. As a feature, the same effect as that of the first aspect can be obtained.

In addition to this, by disposing the damper and the spring between the engaging portion and the accommodating portion which constitute the load measuring device, the load detector is hypersensitive to the change in the peak property of the transmission torque. Such reactions are alleviated, and the transmitted torque can be detected stably.

The invention according to claim 3 is the auxiliary equipment drive device according to claim 1, wherein the load measuring device is a stationary member.
A housing portion provided in the sing, an engaging portion integrally provided with the clutch member and penetrating into the housing portion, a cam surface provided in the engaging portion, and a cam surface as the engaging portion rotates. The cam member that moves by the contact of the cam member, the switch that operates by the movement of the cam member, the damper that is arranged between one side of the engaging portion in the rotational direction and the accommodating portion, and the other side of the engaging portion in the rotational direction. It is characterized by comprising a spring arranged between it and the housing portion, and an effect equivalent to that of the constitution of claim 1 is obtained.

In addition to this, as in the second aspect, the damper and the spring are arranged between the engaging portion and the accommodating portion constituting the load measuring device, so that the peak of the transmission torque can be improved. The hypersensitive reaction of the load detector to the change is alleviated, and the transmission torque can be detected stably.

The invention according to claim 4 is the invention according to any one of claims 1 to 3, wherein when the transmission torque detected by the load measuring device exceeds a predetermined value, the clutch is engaged by the controller. Is opened, and an effect equivalent to that of the configuration according to any one of claims 1 to 3 is obtained.

In addition to this, when the engine speed increases and the transmission torque exceeds a predetermined value, the clutch is released, and the third
The gear idling disconnects the auxiliary machine from the engine, reducing the load on the engine.

Thus, the engine and the auxiliary machinery are protected from an excessive load, gear damage and seizure of the auxiliary machinery are prevented, and the fuel efficiency of the engine is improved.

The invention according to claim 5 is the invention according to any one of claims 1 to 4, wherein the auxiliary machine is a supercharger of the engine, and the intake air flows from the discharge side to the intake side. 5. The configuration according to claim 1, further comprising a returning bypass valve, wherein the controller adjusts the opening degree of the bypass valve according to the transmission torque detected by the load measuring device. Get the same effect as.

In addition to this, the controller adjusts the opening degree of the bypass valve in accordance with the transmission torque. Therefore, for example, when the engine speed extremely rises and the transmission torque exceeds a predetermined value, the bypass valve is operated. As a result, intake air returns from the discharge side to the intake side, and it is possible to prevent excessive supercharging pressure from being applied to the engine.

In this way, the supercharger and the engine are protected, and their durability and engine fuel consumption are improved.

A sixth aspect of the present invention is the invention according to any one of the first to fifth aspects, in which an oil pump driven by a power transmission system and an oil pressure of the oil pump are received. A hydraulic actuator for operating the clutch and a valve for connecting and disconnecting the hydraulic pressure are arranged inside the casing, and an effect equivalent to that of the configuration according to any one of claims 1 to 5 is provided. obtain.

In addition to this, since the oil pump for driving the hydraulic actuator for operating the clutch is configured to be driven by, for example, the power transmission system in the stage prior to the clutch, these oil pump and hydraulic actuator are connected. The auxiliary drive device is unitized into the auxiliary drive device, and the above-described control can be performed in the unit, and the auxiliary drive device can be easily attached and detached.

The invention according to claim 7 is the accessory drive system according to any one of claims 1 to 6, wherein the clutch is a friction clutch.
Through this, an effect equivalent to that of the configuration according to any one of claims 6 is obtained.

In addition to this, in the accessory drive system of the present invention, the clutch is operated intermittently while a large torque is applied. However, as in this claim, the clutch is a friction clutch such as a multi-disc clutch. With the configuration, the clutch can be smoothly engaged and disengaged with the torque applied,
The response of connecting and disconnecting the accessories is so fast.

[0025]

BEST MODE FOR CARRYING OUT THE INVENTION The first aspect of the present invention will be described with reference to FIGS.
An embodiment will be described. This embodiment corresponds to claims 1, 2,
It has the features of 4, 5, 6, and 7. 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 FIG. 1, the accessory drive device 1 of this embodiment is used to drive a supercharger 3 (auxiliary equipment).

As shown in FIGS. 1 and 2, the accessory drive system 1 includes a planetary gear type differential mechanism 5, a multi-plate clutch 7 (friction clutch), a load measuring device 9, a hydraulic actuator 11,
Oil pump 13, solenoid valve 15 (valve),
Chain transmission mechanism 17, motor 19, controller 21
Etc.

Further, the supercharger 3 is a screw.
Type air compressor 23, speed increasing gear set 25, timing gear set 27, intake duct 29, discharge duct 31, bypass duct 33 that connects the ducts 29 and 31, an electromagnetic bypass valve 35 (bypass) arranged in the bypass duct 33. Valve) etc.

An input shaft 39 penetrates into the casing 37 (stationary member) of the accessory drive system 1 from the left end side and is supported by the casing 37 via bearings 41 and 43. A seal 4 is provided between the input shaft 39 and the casing 37.
5, 45 are arranged to prevent oil leakage.

A sprocket 47 is spline-connected to the left end of the input shaft 37, and is prevented from falling off by a washer 49 and a nut 51. The sprocket 47 is connected to a sprocket on the crankshaft side via a chain and is rotationally driven by the driving force of the engine.

The planetary gear type differential mechanism 5 includes an internal gear 53 (third gear) and a pinion gear 55 (first gear).
Gear), pinion carriers 57, 59 and sun gear 61
(Second gear).

As shown in FIG. 3, three pinion gears 55 are arranged at equal intervals in the circumferential direction. Each pinion gear 55 is supported on a pinion shaft 65 by a bearing 63, and each pinion shaft 65 is supported at both ends by left and right pinion carriers 57, 59. The pinion carriers 57 and 59 are connected to each other, and the left pinion carrier 57 is welded to the input shaft 39.

Thus, the driving force of the engine is the input shaft 39.
Is input to the pinion carriers 57 and 59 of the differential mechanism 5.

The sun gear 61 is spline-connected to the output shaft 67, and is prevented from falling off by the washer 69 and the bolt 71. The output shaft 67 is supported on the casing 37 by bearings 73 and 75.

The speed-increasing gear set 25 of the supercharger 3 is composed of large-diameter and small-diameter speed-increasing gears 77 and 79 meshing with each other, and the timing gear set 27 has a large-diameter and small diameter meshing with each other. Timing gears 81 and 83. Further, as shown in FIG. 1, the air compressor 23 includes a pair of screw rotors 85 and 87.

The large-diameter speed increasing gear 77 is integrally formed at the right end of the output shaft 67, and the small-diameter speed increasing gear 79 is mounted on the shaft 89 of the screw rotor 85 together with the small-diameter timing gear 83.
They are connected by 91 and are fixed by nuts 93. Further, the large-diameter timing gear 81 is used for the shaft 95 of the screw rotor 87.
Further, the taper ring fixing mechanism 97 and the nut 99 are positioned and fixed in the rotational direction.

Each shaft 89, 9 of the screw rotors 85, 87
5 is bearing 101, 10 at the left end and the right end, respectively.
3 is supported by the compressor casing 105, and seals 107, 109 mounted between both ends of the shafts 89, 95 and the compressor casing 105 prevent air leakage and oil leakage. There is.

The rotation of the output shaft 67 is accelerated by the speed increasing gear set 25, and the screw rotors 85 and 87 are rotationally driven through the timing gear set 27 so as not to contact each other, and the driven air compressor 23 is The intake air sucked from the intake duct 29 is axially pumped between the rotors 85 and 87,
It is discharged from the discharge port 111 and supplied to the engine through the discharge duct 31.

The chain transmission mechanism 17 includes a pair of sprockets 113 and 115 and a chain 117 for connecting them.
It is composed of The sprocket 113 is welded to the internal gear 53 of the differential mechanism 5 and is supported on the input shaft 39 via a roller bearing 119. The sprocket 115 is fixed to the parallel shaft 121, and the parallel shaft 121 is connected to the motor 19 (hydraulic motor).
Motor, an electric motor or other source of rotational driving force).

As described above, the motor 19 is connected to the internal gear 53 of the differential mechanism 5 via the chain transmission mechanism 17. As will be described later, the motor 19 controls the rotation of the internal gear 53 by adjusting the torque or switching the rotation direction, and adjusts the gear ratio of the differential mechanism 5.

As shown in FIG. 3, the multi-plate clutch 7 has an outer clutch plate 127 engaged with a recess 125 formed on the inner periphery of the clutch hub 123 and a recess 129 formed on the outer periphery of the internal gear 53. The engaged clutch plates 131 are alternately arranged.

The casing 37 is provided with three accommodating portions 133 at equal intervals in the circumferential direction, and an engaging member 135 (engaging portion) penetrating into each accommodating portion 133 is provided on the outer periphery of the clutch hub 123.
Are welded.

A rubber damper is formed between the engaging member 135 and the side wall 137 of the accommodating portion 133 on one side in the rotation direction.
139 (damper) is arranged. Further, a coil spring 141 (spring) is arranged between the engaging member 135 and the side wall 137 on the other side of the engaging member 135 in the rotation direction.
The rubber damper-139 is pressed against the side wall 137 via the connector 5.

In one containing portion 133, a rubber damper
A load detector 143 (piezoelectric element, strain gauge, or the like) is arranged between the 139 and the side wall 137 to configure the load measuring device 9. The load detector 143 is the coil spring 14
The initial value is given by 1.

When the multi-plate clutch 7 is engaged, the rotation of the internal gear 53 is locked, and the rotation of the input shaft 39 is increased in speed by the differential mechanism 5 and transmitted to the speed increasing gear set 25. or,
When the multi-plate clutch 7 is released, the internal gear 53 is brought into a free rotation state, the supercharger 3 is separated from the engine by the differential mechanism 5, and the internal gear 53 is disconnected.
The null gear 53 becomes rotatable by the torque of the motor 19.

As shown in FIG. 2, the hydraulic actuator 11 comprises a hydraulic cylinder 145 and a piston 147, and the hydraulic cylinder 145 is supported by the casing 37 by bearings 149 and 149. Further, a return spring 153 is arranged between the retainer 151 fixed to the clutch hub 123 of the multi-plate clutch 7 and the piston 147.

The oil pump 13 is arranged between the input shaft 39 and the casing 37, and is driven by the rotation of the input shaft 39. The hydraulic pressure generated by the oil pump 13 is applied to the oil passage 155 of the casing 37 and the oil passage 15 of the hydraulic cylinder 145.
Is supplied to the hydraulic actuator 11 via 7 and 7.

The solenoid valve 15 is arranged so as to open and close the oil passage 155, opens the oil passage 155 to supply the working oil pressure to the hydraulic actuator 11, and closes the oil passage 155 to supply the working oil pressure. To stop.

When the working oil pressure is supplied to the hydraulic actuator 11, the piston 147 presses and engages the multi-plate clutch 7, and when the working oil pressure is stopped, the piston 147 is retracted by the return spring 153. The multi-plate clutch 7 is released.

A signal from the load measuring device 9 is input to the controller 21, and further signals from an engine speed sensor, an accelerator depression angle sensor, a manual switch on the driver's seat, and the like are input.

Further, the controller 21 is as follows.
Solenoid valve 1 based on the signal from load measuring device 9
5 sends an ON-OFF signal to the electromagnetic bypass valve 35
To the motor 19, and a rotation torque adjustment signal and a rotation direction switching signal to the motor 19.

An arrow 159 in FIG. 3 indicates the direction of torque when the vehicle travels forward. At this time, when the multi-plate clutch 7 is engaged, the clutch is passed through the internal gear 53 and the multi-plate clutch 7. Torque is applied to the engaging member 135 of the hub 123, and the load detector 143 causes the engaging member 135 to cause the rubber damper-139 and the side wall 137 of the housing portion 133.
It is pressed between and and the load at that time is detected.

The controller 21 detects the torque received by the load measuring device 9 from the load detected by the load measuring device 9 (load detector 143) and the distance between the load detecting device 143 and the rotation center 161 (FIG. 3). Further, the torque transmitted to the supercharger 3 is calculated from the detected torque. The upper limit transmission torque for the supercharger 3 is preset in the controller 21.

In the controller 21, when the engine speed greatly increases and the transmission torque exceeds the upper limit value, the solenoid valve 15 stops the hydraulic pressure supply to the hydraulic actuator 11 to release the multi-plate clutch 7. , Disconnect the supercharger 3 from the engine.

Therefore, even if the engine speed greatly increases, the supercharger 3 is not overloaded, so that the differential mechanism 5, the speed increasing gear set 25, and the timing gear set 2 are provided.
7, the gears are prevented from being damaged, and the air compressor 23 prevents the rotors 85 and 87 from contacting and seizing. In addition, the multi-plate clutch 7 includes clutch plates 127, 13
No. 1 slippage, heat generation, and seizure are prevented, and durability is improved.

Further, since the supercharger 3 is disconnected when the rotational speed is high, the load on the engine is reduced, the fuel consumption is improved, and the excessive boost pressure is not applied to prevent the engine from being damaged. It

In this way, the engine and the auxiliary machinery are protected when the transmission torque becomes abnormally large.

In the range where the transmission torque is below the upper limit value, the controller 21 adjusts the opening degree of the electromagnetic bypass valve 35 while engaging the multi-plate clutch 7 and driving the supercharger 3. , Control the boost pressure according to the change of the engine speed.

Further, the controller 21 disengages the multi-plate clutch 7 to allow the internal gear 53 to rotate freely, and adjusts the rotation torque of the motor 19 or switches the rotation direction. By doing so, the gear ratio of the differential mechanism 5 and the rotation speed of the supercharger 3 are controlled steplessly, and the rotation of the supercharger 3 corresponding to the change of the engine rotation speed. Finely adjust the number to get the desired supercharging characteristics.

Thus, the accessory drive system 1 is constructed.

As described above, the accessory drive system 1 can monitor the transmission torque of the supercharger 3 while driving the supercharger 3 with the controller, so that the engine speed increases. When the transmission torque becomes abnormally large, the supercharger 3 is disconnected and the engine and the supercharger are separated.
It protects the jar 3 from an excessive load, prevents breakage and seizure, and improves durability.

Further, as described above, the rubber damper is provided between the engaging member 135 and the accommodating portion 133 which constitute the load measuring device 9.
By arranging 139 and the coil spring 141, the hypersensitive reaction of the load detector 9 to the change of the peak property of the transmission torque is alleviated, and the transmission torque can be stably detected.

Further, since the oil pump 13, the hydraulic actuator 11, and the solenoid valve 15 are incorporated into the accessory drive device 1 to form a unit, the accessory drive device 1 can be easily handled by assembling or removing. It was

In addition to this, in the accessory drive system of the present invention, the clutch is operated intermittently while a large torque is applied. In the accessory drive system 1 of this embodiment, the clutch is a multi-plate clutch 7. As a result, the clutch can be smoothly engaged and disengaged while torque is applied.
The response of connecting and disconnecting the charger 3 is fast.

Next, another example of the load measuring device used in the accessory drive system of the present invention will be described with reference to FIGS. The load measuring device 163 has the features of claim 3. In the following description, members having the same functions as those of the first embodiment are designated by the same reference numerals, and duplicate description of these members having the same functions will be omitted.

As shown in each drawing, the casing 37 is provided with an accommodating portion 133, and an engaging member 165 (engaging portion) penetrating into the accommodating portion 133 is welded to the outer periphery of the clutch hub 123. . A viscous damper 167 (damper) and a coil spring 169 (spring) are arranged between the side wall 137 and the side wall 137 of the housing 133 on one side and the other side in the rotation direction of the engaging member 165, respectively. The coil spring 169 presses and supports the engaging member 165 against the viscous damper-167.

A holder-171 is attached to the accommodating portion 133, and an ON-OFF switch 175 (switch) and an ON-OFF switch 175 are disposed in the accommodating chamber 173 formed through the holder-171 and the accommodating portion 133.
A ball 177 (cam member) that hits the ball 177 and a coil spring 179 that presses the ball 177 against the outer periphery of the engaging member 165 are arranged.

The cam surface 18 is provided on the outer periphery of the engaging member 165.
1 is formed.

In this way, the load measuring device 163 is constructed, and the signal from the ON-OFF switch 175 is controlled.
I am sending it to LA 21.

The arrow 183 in FIG. 4 indicates the direction of the torque when the vehicle travels forward. At this time, when the multi-plate clutch 7 is engaged, it is engaged via the internal gear 53 and the multi-plate clutch 7. Torque is applied to the coupling member 165, the engagement member 165 rotates while bending the viscous damper-167, and the cam surface 181 pushes up the ball 177 to activate the ON-OFF switch 175, as shown in FIG.

The load measuring device 163 adjusts the balance between the urging force of the coil spring 179 and the bending characteristic of the viscous damper-167, and the relative position between the cam surface 181 and the ball 177 to adjust the transmission torque. When the upper limit for the supercharger 3 is exceeded, the ON-OFF switch 17
5 is activated.

As described in the first embodiment, when the transmission torque exceeds this upper limit value, the controller 21 releases the multi-plate clutch 7 to disconnect the supercharger 3 from the engine. In the range where the transmission torque is less than or equal to the upper limit value, the opening degree of the electromagnetic bypass valve 35 is adjusted while the multi-plate clutch 7 is engaged and the supercharger 3 is driven, and the excess torque is changed according to the change in the engine speed. Control the supply pressure.

In the accessory drive system of the present invention, the planetary gear type differential mechanism is different from the above embodiment in that, for example, the driving force of the engine is input from the internal gear and the pinion carrier (pinion gear) is used. May be locked or rotation controlled.

The clutch is not limited to the multi-disc clutch,
For example, another friction clutch or a mesh clutch may be used.

The auxiliary equipment is not limited to the supercharger. The accessory drive device of the present invention can protect the accessory and the engine from an excessive load by the feedback function of the transmission torque and the adjustment function of the transmission torque as described above, and can greatly improve the durability. .

[0076]

According to the accessory drive system of the first aspect of the present invention, the load measurement is arranged between the clutch and the stationary member while transmitting the driving force of the engine to the accessory via the planetary gear type differential mechanism. The transmitted torque is detected by the detector.

Therefore, if the transmission torque is monitored by the controller, when the transmission torque becomes abnormally large due to an increase in the engine speed, necessary measures should be taken to reduce the load on the auxiliary machine and the engine. It is possible to protect the auxiliary machine and the engine from an excessive load, prevent damage and seizure, and improve durability.

According to the second aspect of the present invention, the same effect as that of the first aspect can be obtained, and the damper and the spring are arranged between the engaging portion and the accommodating portion constituting the load measuring device.
The sensitive reaction of the load detector with respect to the change in the peak of the transmission torque is alleviated, and the transmission torque can be stably detected.

According to the invention of claim 3, the same effect as that of the structure of claim 1 is obtained, and similarly to claim 2, a damper and a spring are provided between the engaging portion and the accommodating portion which constitute the load measuring device. By arranging and, the hypersensitive reaction of the load detector to the change of the peak property of the transmission torque is alleviated, and the transmission torque can be stably detected.

The invention according to claim 4 obtains the same effect as that of the structure according to any one of claims 1 to 3, and
When the transmission torque exceeds a predetermined value, the auxiliary machine is disconnected from the engine, and the load on the auxiliary machine and the engine is reduced. Therefore, gear damage and seizure of the auxiliary machine are prevented, and the fuel efficiency of the engine is improved.

The invention according to claim 5 has the same effect as that of the structure according to any one of claims 1 to 4, and
When the transmission torque exceeds a specified value, the bypass valve is opened to prevent excessive supercharging pressure from being applied to the engine, and the turbocharger and engine are protected from excessive load. And improve.

The invention according to claim 6 has the same effect as that of the structure according to any one of claims 1 to 5, and
Since the oil pump, hydraulic actuator, valve, etc. are incorporated into the accessory drive unit to form a unit, the above control is possible within the unit, and the accessory drive unit can be handled by assembly or removal. It became easier.

The invention according to claim 7 has the same effect as that of the structure according to any one of claims 1 to 6, and
Since the friction clutch is smoothly connected and disconnected under a torque, the response of connecting and disconnecting the auxiliary machine is fast.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a first embodiment of the present invention.

FIG. 2 is an enlarged view of a main part of the first embodiment.

FIG. 3 is a sectional view taken along line AA of FIG. 2;

FIG. 4 is a cross-sectional view showing another example of the load measuring device used in the present invention.

FIG. 5 is an enlarged view of a main part of FIG.

6 is an enlarged view of an essential part of FIG. 4, showing a state in which the ball is pushed up.

FIG. 7 is a sectional view of a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Auxiliary equipment drive device 3 Supercharger (auxiliary equipment) 5 Planetary gear type differential mechanism 7 Multi-plate clutch (friction clutch) 9,163 Load measuring device 11 Hydraulic actuator 13 Oil pump 15 Solenoid valve (Valve) 21 Controller 35 Electromagnetic bypass valve (bypass valve) 37 Casing (stationary member) 53 Internal gear (3rd gear) 55 Pinion gear (1st gear) 61 Sun gear (2nd gear) 133 Housing section 135, 165 Engagement member (engagement part) 139 Rubber damper (damper) 141, 169 Coil spring (spring) 143 Load detector 167 Viscous damper (damper) 175 ON-OFF switch (switch) 177 ball (Cam member) 181 Cam surface

Claims (7)

[Claims] 1. A planetary gear type, which is arranged in a power transmission system for transmitting a driving force of an engine to an auxiliary machine and has a first gear on the engine side, a second gear on the auxiliary machine side, and a third gear. A differential mechanism, a clutch arranged between the third gear and the stationary member, a load measuring device arranged between the clutch and the stationary member for detecting a transmission torque, and detection of the load measuring device. An accessory drive device comprising a controller for receiving a signal. 2. The invention according to claim 1, wherein the load measuring device has a housing portion provided in a casing that is a stationary side member, and a member integrally provided with the clutch member and penetrating into the housing portion. From the mating portion, the damper and the load detector arranged between the one side of the engaging portion in the rotation direction and the accommodating portion, and the spring arranged between the other side of the engaging portion in the rotating direction and the accommodating portion. The accessory drive device is characterized in that the torque is detected from the load detected by the load detector and the distance from the load detector to the center of rotation. 3. The load measuring device according to claim 1, wherein the load measuring device is integrally provided with the housing member provided in the casing, which is the stationary member, and the clutch member, and is inserted into the housing member. A mating portion, a cam surface provided on the engaging portion, a cam member that moves by contact with the cam surface as the engaging portion rotates, a switch that operates by the movement of the cam member, and an engaging portion of the engaging portion. A damper arranged between the one side in the rotation direction and the accommodating portion.
And an spring disposed between the other side of the engaging portion in the rotation direction and the housing portion. 4. The invention according to any one of claims 1 to 3, wherein when the transmission torque detected by the load measuring device exceeds a predetermined value, the controller releases the clutch. Characteristic accessory drive device. 5. The invention according to any one of claims 1 to 4, wherein the auxiliary machine is an engine supercharger,
It has a bypass valve that returns intake air from the discharge side to the intake side,
An accessory drive device characterized in that a controller adjusts the opening of this bypass valve according to the transmission torque detected by the load measuring device. 6. The invention according to any one of claims 1 to 5, wherein an oil pump driven by a power transmission system and a hydraulic actuator for receiving a hydraulic pressure of the oil pump to operate a clutch. A drive device and an auxiliary device drive device in which a valve for connecting and disconnecting the hydraulic pressure is arranged inside the casing. 7. The accessory drive system according to any one of claims 1 to 6, wherein the clutch is a friction clutch.