JP2000230430A - Planetary gear mechanism of internal combustion engine - Google Patents

Abstract

(57) [Summary] [Configuration] Internal gear 3 rotating integrally with crankshaft 2, sun gear 6 rotating integrally with crank pulley 8, and planetary gear 5 meshing with both 3, 6
And a planetary carrier 4 rotatably supporting the planetary gear 5 and rotatable around the sun gear 6.
And A motor generator 9 for controlling the rotation of the planetary carrier 4 is provided on the planetary carrier 4.
Is provided. [Effect] By controlling the drive of the planetary carrier 4, it is possible to operate the auxiliary devices with optimum efficiency.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear mechanism of an internal combustion engine applied to an automobile or the like, which rotates accessories in reverse with respect to a crankshaft of the internal combustion engine.

[0002]

2. Description of the Related Art Direct-injection gasoline engines and direct-injection diesel engines have been in the limelight due to the increasing interest in improving fuel efficiency of automobiles in response to recent environmental problems. Since the combustion excitation force is relatively large, the roll vibration accompanying the torque fluctuation is also large, which causes a problem that the muffled sound and the floor vibration at the time of idling deteriorate.

As one means for solving such a problem, for example, JP-A-6-42591 and JP-A-6-5
As described in Japanese Patent No. 0388, by providing a sub flywheel that rotates in reverse with respect to a main flywheel that rotates integrally with the crankshaft, a direction opposite to the moment acting on the internal combustion engine body as a reaction of torque generation is provided. There is known a technique of generating a moment of the internal combustion engine to reduce the roll vibration of the internal combustion engine body.

However, in this case, with the addition of the sub flywheel, a problem that hinders practical use, such as an increase in weight and a sufficient space for arrangement, is invited.

Therefore, for example, in Japanese Unexamined Patent Application Publication No. 7-35199, a heavy object such as an auxiliary flywheel is removed by using a planetary gear mechanism for rotating a crank pulley for an alternator in reverse with respect to a crankshaft. The roll vibration of the main body of the internal combustion engine is reduced without being separately provided. That is, the planetary gear mechanism has a planetary gear that meshes with the outer periphery of a sun gear connected to a crank pulley and meshes with the inner periphery of an internal gear connected to a crankshaft. The planetary carrier that supports this planetary carrier is The orbit around the sun gear of the planetary gear is fixed to the main body.

Therefore, when the crankshaft rotates,
The crank pulley of the alternator rotates reversely with respect to the crankshaft via the internal gear, the planetary gear, and the sun gear, and the inertia moment of the alternator becomes
Acts on the engine body via the planetary carrier. Since the moment of inertia on the alternator side is opposite to the moment acting on the main body of the internal combustion engine as a reaction to the torque generation of the crankshaft, roll vibration of the main body of the internal combustion engine can be reduced.

[0007]

However, the technique described in the above-mentioned Japanese Patent Application Laid-Open No. 7-35199 has the following problems. That is, since the revolution of the planetary gear is fixed, the speed of the crank pulley connected to the auxiliary equipment is increased or reduced at a constant rotation ratio with respect to the crankshaft, and the rotation speed of the auxiliary equipment is reduced to the rotation speed of the internal combustion engine. It fluctuates in proportion to the number. As a result, depending on the operating condition of the internal combustion engine, the rotation speed on the accessory side may deviate significantly from the vicinity of the most efficient rotation speed.

Further, as another problem, from the viewpoint of improving the fuel efficiency of a vehicle in response to recent environmental problems, it is desired to stop idling of the internal combustion engine in a vehicle stopped state. In particular, it is necessary to frequently stop idling when traveling in an urban area or during a traffic jam. In this case, while idling is stopped, that is, while the internal combustion engine is stopped, it is necessary to drive auxiliary equipment such as a compressor of the air conditioner or to frequently start the internal combustion engine.

The present invention has been made in view of such a problem.

[0010]

SUMMARY OF THE INVENTION Accordingly, the invention of claim 1 is a planetary gear mechanism for an internal combustion engine that rotates accessories in reverse with respect to the crankshaft of the internal combustion engine. A planetary gear meshing with both the internal gear and the sun gear; a planetary carrier rotatably supporting the planetary gear and rotating around the sun gear together with the planetary gear; And a rotor of a motor generator for controlling the rotation of the planetary carrier is provided on the planetary carrier.

With the above arrangement, when the crankshaft is driven to rotate, the sun gear connected to the auxiliary equipment via the internal gear rotating integrally with the crankshaft and the planetary gear meshing with the internal gear is connected to the crankshaft. Reverse rotation with respect to the shaft.

According to the present invention, by controlling the rotation of the planetary gear around the sun gear, it is possible to arbitrarily control the rotation speed of the auxiliary devices regardless of the rotation speed of the crankshaft. The accessories can be maintained at a rotational speed at which the efficiency is optimal.

Further, the invention of claim 2 is characterized in that it has a means for restraining the rotation of the planetary carrier and the rotor.

A third aspect of the present invention is characterized in that there is provided means for restraining rotation of the crankshaft and the internal gear.

According to a fourth aspect of the present invention, there is provided a one-way clutch for inhibiting reverse rotation of the crankshaft and the internal gear.

A fifth aspect of the present invention is characterized in that there is provided a means for temporarily increasing the driving resistance on the crankshaft and the internal gear side compared with the driving resistance on the auxiliary equipment and the sun gear side.

A sixth aspect of the present invention is characterized in that the above-mentioned auxiliary devices and means for restraining rotation on the sun gear side are provided.

According to a seventh aspect of the present invention, there is provided a one-way clutch for inhibiting the sun gear from rotating in the same direction as the crankshaft.

The invention according to claim 8 is characterized in that there is provided a means for temporarily increasing the driving resistance on the auxiliary equipment and the sun gear side compared with the driving resistance on the crankshaft and the internal gear side.

According to a ninth aspect of the present invention, there is provided a clutch mechanism which integrates the clutch for restraining rotation of the planetary carrier and the rotor, and the clutch for restraining rotation of the accessory and the sun gear. And

[0021]

According to the first aspect of the invention, by controlling the rotation of the planetary carrier around the sun gear, the rotation speed of the accessories is controlled arbitrarily regardless of the rotation speed of the crankshaft. It is possible to maintain the rotational speed at which the efficiency of the accessories is optimized.

Further, by regenerating the rotational energy of the planetary carrier by the motor generator, it is possible to further reduce fuel consumption and the like.

In addition, the planetary carrier, which is a component of the planetary gear mechanism, functions as a rotor of the motor generator, and the size of the apparatus itself can be reduced.

Also, by restricting the rotation on the planetary carrier side, the inertia moment on the accessory that rotates in the reverse direction with respect to the crankshaft is reduced via the planetary carrier. Acts on the body side. As a result, the roll vibration of the internal combustion engine can be reliably reduced by utilizing the moment of inertia on the accessory devices side, similarly to that described in Japanese Patent Application Laid-Open No. 7-35199.

Further, in the present invention, by controlling the drive of the planetary carrier by the motor generator, it is possible to drive the auxiliary equipment or crank the internal combustion engine while the internal combustion engine is stopped, for example, when idling is stopped.

For example, when driving auxiliary equipment while the engine is stopped, the motor generator rotates the planetary carrier by restricting the rotation of the crankshaft and the internal gear as in the third aspect of the invention. A situation in which the crankshaft rotates due to the torque can be reliably prevented. As a result, it is possible to reliably prevent a decrease in the driving torque of the accessories due to the rotation of the crankshaft.

In the case where the auxiliary equipment is driven by the motor generator while the engine is stopped, the internal gear on the crankshaft side receives a rotational torque in a direction opposite to that during normal operation. Therefore, claim 4
By prohibiting reverse rotation of the crankshaft side with a one-way clutch as in the invention described in (1), it is possible to rotate the crankshaft side when driving auxiliary equipment without separately providing a means as in claim 3. The situation can be reliably prevented.

Also, in the case where the driving resistance on the crankshaft side is temporarily increased as compared with the driving resistance on the auxiliary equipment side, as in the invention according to the fifth aspect, the invention according to the third and fourth aspects can be realized. Similarly, it is possible to prevent a situation where the crankshaft rotates when the accessory is driven.

On the other hand, when the internal combustion engine is cranked by rotating the crankshaft by the motor generator, the rotation of the auxiliary devices and the sun gear side is restricted as in the invention according to claim 6. A situation in which the sun gear on the accessory side rotates due to the driving torque by which the motor generator rotates the planetary carrier can be reliably prevented. As a result, a decrease in the driving torque of the crankshaft due to the rotation of the accessories can be reliably prevented.

Further, as in the invention according to the seventh aspect, the one-way clutch prohibits the sun gear from rotating in the same direction as the crankshaft. It is possible to reliably prevent a situation in which the auxiliary equipment rotates during ranking.

Further, in the case where the driving resistance on the auxiliary equipment side is temporarily increased as compared with the driving resistance on the crankshaft side as in the invention according to the eighth aspect, the invention according to the sixth and seventh aspects can be realized. Similarly, it is possible to reliably prevent a situation in which the auxiliary devices rotate during cranking.

According to the ninth aspect of the invention, the effects of both the second and sixth aspects of the invention can be obtained by one clutch mechanism, and the size of the entire apparatus can be reduced. be able to.

[0033]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a configuration diagram showing a planetary gear mechanism of an internal combustion engine according to a first embodiment of the present invention. The planetary gear mechanism is interposed between a crankshaft 2 rotatably supported by an internal combustion engine main body 1 and a crank pulley 8 connected to auxiliary equipment (not shown) via a belt (not shown) or the like. The crank pulley 8 is rotated in the opposite direction with respect to the crankshaft 2.

That is, the planetary gear mechanism is fixed to the front end of the crankshaft 2 and
An internal gear 3 which rotates integrally with the internal gear 3, a sun gear 6 which is fastened and fixed to the crank pulley 8 via a shaft 7 by a bolt 7 a and rotates integrally with the crank pulley 8, and an inner periphery of the internal gear 3. And a plurality of planetary gears 5 that mesh with the outer periphery of the sun gear 6 and a planetary carrier 4 that supports the planetary gears 5 so as to be able to rotate (rotate around the shaft) and that can rotate around the sun gear 6 together with the planetary gears 5. ing. When the crankshaft 2 rotates, the internal gear 3, the planetary gear 5, and the sun gear 6
And the crank pulley 8 is configured to rotate in the opposite direction with respect to the crankshaft 2.

Case 12 for housing this planetary gear mechanism
Are fixed to the internal combustion engine body 1 via bolts and nuts 19. The shaft 7 is rotatably supported by a case 12 via a bearing 11. The planetary carrier 4 is rotatably supported on the outer periphery of the shaft 7 via a bearing 10. That is, the planetary carrier 4 is rotatably supported by the internal combustion engine body 1 via the shaft 7 and the case 12.

Then, the planetary carrier 4 and the case 1
2, an electromagnetic motor generator 9 is interposed. The motor generator 9 has both a function as an electric motor for rotatingly driving the planetary carrier 4 and a function as a generator for regenerating the rotational energy of the planetary carrier 4. More specifically, the motor generator 9 is fixed to the outer periphery of the planetary carrier 4, and the shaft 7 is integrated with the planetary carrier 4.
It has a rotor (rotor) 9a that rotates around and a stator (stator) 9b fixed to the inner periphery of the case 12. A battery (not shown) is connected to the stator 9b. When the motor generator 9 functions as an electric motor, a current flows from the battery to the stator 9b. The current generated in the child 9b is regenerated to the battery. The operation of the motor generator 9 is controlled by a control unit (not shown) connected to the stator 9b.

The bearing 10 has an oil seal function, and an oil seal 18 is interposed between the planetary carrier 4 and the case 12.
The bearing 10 and the oil seal 18 separate the motor generator 9 and the clutch 13 from lubricating oil that lubricates sliding parts such as the crankshaft 2.

Further, the planetary carrier 4 and the case 12
Between them, a clutch 13 for appropriately restricting (fixing) the rotation of the planetary carrier 4 with respect to the engine body 1 is interposed. The clutch 13 is mounted on a slide plate 15 slidably held by a pin 14 fixedly pressed into the case 12, a first friction portion 16 mounted on the slide plate 15, and mounted on the planetary carrier 4.
Second friction portion 17 disposed opposite to and able to contact friction portion 16
And is constituted by. The slide plate 15 is held so as to be slidable in the axial direction while being restrained in the rotation direction with respect to the pin 14. The slide plate 15 is moved in the axial direction of the crankshaft 2 (the left-right direction in the figure). Thus, the engagement / release of the clutch 13 can be switched.

Next, the operation of the planetary gear mechanism when the clutch 13 is released will be described with reference to FIG. In addition,
In the alignment chart of FIG. 2, three vertical axes 21, 22 and 23 correspond to the crankshaft 2 and the internal gear 3, respectively.
3 shows the number of rotations on the side, the planetary gear 5 and the rotor 9a side of the motor generator 9, the sun gear 6 and the crank pulley 8 side. An area above the horizontal axis 28 indicating the case where the rotation number is zero indicates a positive rotation number, and an area below the horizontal axis 28 indicates a negative rotation number. In this embodiment, a positive rotation speed indicates a forward rotation direction of the crankshaft 2, and a negative rotation speed indicates a reverse rotation direction. Therefore, the crank pulley 8 and the accessories that rotate in the opposite direction to the crankshaft 2 have a negative rotation speed. That is, each component is designed on the assumption that the accessories rotate in the opposite direction with respect to the crankshaft 2.

The distance A between the vertical axes 21 and 22 and the vertical axis 2
The ratio A / B to the interval B of 2, 23 is the ratio of (the number of teeth of the sun gear 6) / (the number of teeth of the internal gear 3). That is, the rotation speeds of the crankshaft 2, the motor generator 9, and the crank pulley 8 at a certain time are plotted on one straight line 24. The inclination and the Y-intercept of the straight line 24 change according to the number of rotations of the crankshaft 2 and the motor generator 9.
And the vertical axis 23 is the rotation speed of the crank pulley 8 at that time.

Here, in the present embodiment, the rotation speed of the crank pulley 8 is maintained in a preset target rotation speed region 25 so that the accessories are driven in a predetermined rotation speed region with the highest efficiency. Can be. Specifically, the rotation speed 22 of the motor generator 9 is variably controlled (reference numeral 27) in accordance with the change of the rotation speed 21 of the crankshaft 2 (reference numeral 26), and the rotation speed of the motor generator 9 is controlled. 22 is a reverse rotation, that is, a negative rotation speed with respect to the crankshaft 2 when the rotation speed 21 on the crankshaft 2 side is relatively low, and the crankshaft 2 when the rotation speed 21 of the crankshaft 2 is relatively high. , That is, a positive rotation in the same direction, that is, a positive rotation speed.

As described above, according to the present embodiment, by controlling the rotation speed of the motor generator 9 for driving the planetary carrier 4 to rotate, the rotation speed of the crank pulley 8 can be maintained in the predetermined rotation speed region 25. Is possible,
As a result, it is possible to maintain a state in which the accessories are efficiently driven.

FIG. 3 is a front view corresponding to FIG. 1 as viewed from the left, and shows the balance of the forces (torques) acting on each part of the planetary gear mechanism when the clutch 13 is released.

The internal gear 3 fixed to the crankshaft 2 rotates clockwise in the figure by the combustion torque 31 of the internal combustion engine. At this time, a driving force (torque) 32 acts on the internal gear 3 to the planetary gear 5, and a reaction force 33 acts on the internal gear 3.
The driving force 32 applied from the internal gear 3 rotates the planetary gear 5, and the driving force 34 acts on the sun gear 6. As a reaction, a force 35 is applied to the planetary gear 5.
Works. Further, a resultant 36 of the force 32 and the force 35 acting on the planetary gear 5 acts on the planetary gear bearing portion 4 a of the planetary carrier 4 that rotatably supports the planetary gear 5. The force 36 acts on the planetary carrier 4 to apply a torque 37 in a clockwise direction in the drawing.

Here, in order to keep the number of rotations of the planetary carrier 4 rotating around the shaft 7 constant, the above-mentioned torque 37 must be balanced with the torque acting on the rotor 9a of the motor generator 9. For this purpose, it is necessary for the motor generator 9 to generate a counterclockwise torque 38 of the same magnitude in the figure. The direction of the torque 38 is opposite to the direction of the combustion torque 31 of the internal combustion engine. Therefore, when the internal combustion engine is operated at a relatively low speed, the motor generator 9 rotates in the direction opposite to the crank rotation while generating the torque 38 in the direction opposite to the crank rotation direction. Work. On the other hand, when the internal combustion engine is operated at a relatively high speed, the motor generator 9 rotates in the same direction as the crank rotation while generating the torque 38 in the direction opposite to the crank rotation direction. It will absorb energy and generate electricity.

FIG. 4 is a front view of the internal combustion engine shown in FIG. 1 and shows the force (torque) acting on the internal combustion engine main body 1. The configuration of the planetary gear mechanism and the like is not shown.

Since the internal combustion engine main body 1 generates a combustion torque for rotating the crankshaft 2 around the crank center 41 clockwise in the drawing, it receives a reaction torque 42 thereof. Since the combustion torque is generated intermittently, the torque 42 has a vibration component, and the vibration component causes the internal combustion engine main body 1 to roll vibrate. On the other hand, since motor generator 9 generates counterclockwise torque, internal combustion engine body 1 receives the reaction torque 43 clockwise. Therefore, if a vibration component having a phase opposite to that of the combustion torque reaction 42 is applied to the generated torque of the motor generator 9, the roll vibration of the internal combustion engine body 1 can be effectively reduced. Note that the magnitude of the roll vibration reduction effect is determined by the magnitude of the vibration component of the torque generated by the motor generator 9 and the like.

In the above description, the clutch 13 for fixing the rotation of the planetary carrier 4 is released, and the rotation of the planetary carrier 4 is permitted. Carrier 4
The state in which the rotation is restricted will be described with reference to FIGS.

The planetary carrier 4 has a combined force 36 of a driving force 32 and a driving reaction force 35 acting on the planetary gear 5.
Is input to the internal combustion engine main body 1 via the clutch 13 and the case 12 to rotate the planetary carrier 4 clockwise generated by the resultant force 36. This torque is expressed as a clockwise torque 43 shown in FIG. 4 and acts in a direction to cancel the combustion torque reaction force 42 of the internal combustion engine. The vibration components of these forces and torques are determined by the vibration component of the rotational speed of each part and the moment of inertia of each part.

Here, the moment of inertia about the roll axis of the whole engine is I, the roll angular displacement of the engine is φ, and the engine rotation system (flywheel or drive plate, connecting rod rotation equivalent, The inertia moment of the internal gear 3 and the like is I1, and the equivalent moment of inertia of the sun gear 6 and the rotating body downstream of the sun gear 6 (the crank pulley 8 and the like) is I1.
2. Assuming that the speed increase ratio between the internal gear 3 and the sun gear 6 is ρ, the equation of motion relating to the roll vibration of the engine body 1 is given by the following equation.

[0052]

(Equation 1)

As the coefficient relating to T on the right side in equation (1) approaches 0, the amount of reduction in roll vibration increases.

As described above, when the clutch 13 is engaged and the rotor 9a of the motor generator 9 is stopped, the combustion is performed by utilizing the inertia force of the accessories rotating in the opposite direction to the crankshaft 2. The torque 43 in the direction opposite to the torque reaction force 42 acts on the internal combustion engine main body 1 via the planetary carrier 4, the clutch 13 and the case 12, and the roll vibration of the internal combustion engine is effectively reduced.

In the present embodiment, as shown in FIG. 5 corresponding to FIG.
Even when the internal combustion engine is stopped such as during idling, that is, even when the number of revolutions 21 of the crankshaft 2 is zero, the crank pulley 8 is rotated in the reverse direction by driving the motor generator 9 to rotate in the reverse direction. It is possible to drive auxiliary equipment.

The specific operation in this case will be described with reference to FIG. 6 corresponding to FIG. When the motor generator 9 generates a counterclockwise torque 61 in the figure, a force (torque) 62 acts on the center of the planetary gear 5. This force 62 is distributed to the internal gear 3 and the sun gear 6, and driving forces 63 and 64 act on each of them. As the reaction force, a force 65 and a force 66 act on the planetary gear 5. When the driving force 63 acts on the internal gear 3, a torque 67 in the reverse rotation direction acts on the internal gear 3 and the crankshaft 2. Then, the crank pulley 8 rotates counterclockwise in the figure by the driving force 64 applied to the sun gear 6, and drives the accessories.

As described above, when the accessories are driven while the engine is stopped, the rotation of the crankshaft 2 and the internal gear 3 is preferably restrained by a clutch or the like. As a result, it is possible to reliably prevent the crankshaft 2 from rotating when the accessories are driven. As a result,
It is possible to reliably prevent a decrease in the driving torque of the accessories due to the rotation of the crankshaft 2.

However, if the torque for starting the rotation of the crankshaft 2 of the internal combustion engine is sufficiently larger than the driving torque of the accessories, the crankshaft 2 does not start to rotate due to the torque 67 described above. Such a clutch or the like for restraining rotation on the crankshaft 2 side is not required.

As described above, in the present embodiment, even when the internal combustion engine is stopped at the time of idling or the like in order to reduce fuel consumption, the motor generator 9 is used to supplement the compressor of the air conditioner. Machines can be driven to rotate.

FIG. 7 is a collinear diagram similar to FIG. 2, and shows the rotation speed of each part when the internal combustion engine is cranked using the motor generator 9. In FIG.

When the motor generator 9 is driven to rotate in the forward direction in order to crank the internal combustion engine, the crank pulley 8 and the sun gear 6 connected to the accessories do not generate rotational torque by themselves. Its rotation speed 2
3 cannot be negative. In addition, if the accessory has a function of prohibiting rotation of the accessory itself in a direction opposite to the original rotation direction, the rotation speed 23 does not become positive. As a result, the rotation speed 23 of the crank pulley 8 is maintained at zero.

Therefore, the number of rotations 2 on the crankshaft 2 side
1 is proportional to the number of revolutions 22 of the motor generator 9,
More specifically, it is a value obtained by multiplying the rotational speed 22 by the speed increase ratio between the planetary carrier 4 and the internal gear 3 in the planetary gear mechanism.

FIG. 8 shows the force balance in this case. A force 82 acts on the center of the planetary gear 5 by the torque 81 generated by the motor generator 9.
This force 82 is distributed to the internal gear 3 and the sun gear 6, and drive forces 83 and 84 act on the respective gears. The planetary gear 5 receives a force 85 and a force 86 as the reaction force. The driving force 8 acting on the internal gear 3
3, a torque 87 for rotating the crankshaft 2 clockwise is generated, and the internal combustion engine can be cranked.

As described above, in the present embodiment, the internal combustion engine can be cranked by using the motor generator 9 described above, and a starter motor provided at the rear end of a normal internal combustion engine is used. It can also be omitted.

If the rotation of the accessories, the crank pulley 8 and the sun gear 6 is appropriately restricted as described above, the accessories do not rotate during cranking. There is no danger that the driving torque of the crankshaft 2 will decrease due to the rotation of the auxiliary equipment.

FIG. 9 shows a planetary gear mechanism of an internal combustion engine according to a second embodiment of the present invention, and is a configuration diagram corresponding to FIG. 1 of the first embodiment. Although the basic configuration is the same as that of the first embodiment, the detailed description will be appropriately omitted, but the one-way clutch 9 is provided between the outer peripheral portion of the internal gear 3 and the case 12.
1 is different. This one-way clutch 91 has a ratchet 94 between an outer ring 92 and an inner ring 93.
And has a function of prohibiting the crankshaft 2 from rotating in the opposite direction to that during normal operation.

The basic operation of this embodiment is the same as that of the first embodiment. That is, when the internal combustion engine is stopped such as an idle stop, the motor generator 9 is connected to the crankshaft 2.
When driving the accessories by rotating in the opposite direction, torque 67 for rotating crankshaft 2 in the opposite direction (see FIG. 6).
However, in the present embodiment, the reverse rotation of the crankshaft 2 can be reliably prevented even when the reverse rotation torque 67 is applied by the one-way clutch 91. Therefore, it is possible to reliably prevent the occurrence of vibrations due to the reverse rotation of the crankshaft 2 and the failure of the internal combustion engine. Also, if the crankshaft 2 rotates in the reverse direction when the accessories are driven, the force 63 in FIG. 6 decreases and the force 64 that balances the force 63 also decreases, so that the driving torque of the accessories decreases. According to this embodiment, however, there is no danger that the driving torque of the accessories will decrease due to the reverse rotation of the crankshaft 2.

FIG. 10 shows a third embodiment of the present invention. At the front end of the internal combustion engine body 1, a planetary gear mechanism 101 similar to that of the first embodiment shown in FIG. 1 is provided with a front end of the crankshaft 2 and a crank pulley 8 connected to accessories via a belt. It is interposed between. On the other hand, a transmission 102 is connected to a rear end of the internal combustion engine body 1. Further, a flange 103 is attached to the rear end of the crankshaft 2, and a brake mechanism 104 that appropriately fixes (restrains) the rotation of the flange 103 is attached to the transmission 102.

The operation and effects of this embodiment are basically the same as those of the second embodiment. However, in the second embodiment, the reverse rotation of the crankshaft 2 is controlled by the one-way clutch 91 mounted inside the planetary gear mechanism. This embodiment differs from the embodiment in that the brake mechanism 104 inside the transmission 102 prevents the reverse rotation of the crankshaft 2. That is, when the motor generator 9 is rotated in the opposite direction to the crankshaft 2 to drive the auxiliary equipment when the internal combustion engine is stopped such as an idle stop, the torque 67 (see FIG. 6) for rotating the crankshaft 2 in the opposite direction is provided. However, in the present embodiment, the brake mechanism 104 is actuated to temporarily increase the drive resistance on the crankshaft 2 side than the drive resistance on the auxiliary equipment side, thereby causing the reverse of the crankshaft 2 to move. It is designed to prevent rotation. Also in this case, similarly to the above-described second embodiment, it is possible to reliably prevent the occurrence of vibration due to the reverse rotation of the crankshaft 2 and the failure of the internal combustion engine.
It is possible to prevent a decrease in the driving torque of the accessories due to the reverse rotation of the crankshaft 2.

FIG. 11 shows a fourth embodiment of the present invention. The basic configuration is the same as that of the first embodiment, but a clutch 13 for fixing (restricting) the rotation of the planetary carrier 4 is provided.
The first point is that the clutch 110 for appropriately fixing (restraining) the rotation of the crank pulley 8 is provided.
This is different from the embodiment. This clutch 110 is
And a first friction portion 112 provided on the front side (left side in the drawing) of the internal combustion engine of the disk 111.
And the case 12 so as to face the first friction portion 112.
And a second friction portion 113 provided thereon.

The disk 111 is spline-coupled to the shaft 7, and rotation around the shaft 7 is prohibited, but the disk 111 is slidable along the shaft 7. A fork 114 supporting the disk 111
By sliding in the front-back direction (left-right direction in the figure),
The first friction portion 112 and the second friction portion 113 can be pressed.

This embodiment operates basically in the same manner as in the first embodiment when the clutch 13 is released, except that the motor generator 9 is rotated in the same direction as the rotation direction of the crankshaft 2. The operation when cranking the internal combustion engine is different. That is, when the internal combustion engine is cranked by rotating the motor generator 9 in the same direction as the rotation direction of the crankshaft 2, a driving force 84 (see FIG. 8) acts on the sun gear 6 in the same direction as the crankshaft rotation direction. However, in this embodiment, the fork 114
Is slid forward, and the rotation of the shaft 7 is fixed by the clutch 110, whereby the rotation of the sun gear 6 can be prevented.

Here, during cranking, if the sun gear 6
Is rotated, the force 84 decreases, and the force 83 that balances the force 84 decreases, so that the torque 87 for rotating the crankshaft 2 decreases. On the other hand, by fixing the sun gear 6 at the time of cranking as in the present embodiment,
A decrease in the driving torque of the crankshaft 2 due to the rotation of the sun gear 6 on the accessory side can be prevented.

FIG. 12 shows a fifth embodiment of the present invention. At the front end of the internal combustion engine main body 1, the above-described planetary gear mechanism 101 is interposed between the front end of the crankshaft 2 and the crank pulley 8. A fluid pump 123 such as a power steering pump as one of accessories is connected to the crank pulley 8 via a belt 122. A valve 125 that restricts the flow of the working fluid is provided in a part of the working fluid circuit 124 of the pump 123.

When the motor generator 9 is rotated in the same direction as the rotation direction of the crankshaft 2 to crank the internal combustion engine, the sun gear 6 applies a driving force 84 in the same direction as the rotation direction of the crankshaft 2 (see FIG. 8). Works.
At this time, in this embodiment, by closing the valve 125, the driving resistance of the pump 123 as the auxiliary equipment, that is, the rotation resistance on the sun gear 6 side is temporarily increased from the driving resistance on the crankshaft 2 side. I have. Thus, by increasing the driving torque (resistance) of the sun gear 6, the upper limit of the driving force of the crankshaft 2 is prevented from being limited by the driving torque of the sun gear 6.

That is, the operation and effect of this embodiment are basically the same as those of the third embodiment, but in the third embodiment, the clutch 110 for directly fixing the sun gear 6 inside the planetary gear mechanism is used. In contrast to this, the present embodiment is different from the first embodiment in that a function of indirectly increasing the rotational resistance of the sun gear 6 is provided on the side of the pump 123 as an accessory driven by the crank pulley 8. This embodiment has an advantage that the structure of the planetary gear mechanism 101 itself can be simplified as compared with the third embodiment.

FIG. 13 shows a sixth embodiment of the present invention. Although the basic configuration is the same as that of the first embodiment, the configuration of the clutch mechanism 130 for fixing the rotation of the planetary carrier 4 is different from that of the first embodiment. That is, the clutch mechanism 130 includes a first clutch 131 that fixes (restrains) the planetary carrier 4 to the internal combustion engine main body 1 and a shaft 7.
Clutch 1 for fixing (restraining) the engine to the internal combustion engine body 1 side
33 and 33 are integrated. The first clutch 131 includes a pair of friction portions 13 opposing each other so as to be able to press against each other.
1a and 131b, and the second clutch 133 has a pair of friction portions 133a and 133b opposed to each other so as to be able to press against each other.

One of the friction portions 131a and 133a is attached to a slide disk 134. The slide disk 134 is connected to a rod 136 via a pin 135 press-fitted into the case 12, and is slidably supported with respect to the case 12 while being restricted from rotating. That is, the sliding disk 134 can be slid in the axial direction of the crankshaft 2 along the pin 135 by sliding the rod 136 in the left-right direction in the figure. The other friction part 131b is attached to the planetary carrier 4, and the friction part 133b is
It is attached to a disk 132 supported by the shaft 7.

When the slide disk 134 is held at the intermediate position, the clutches 131 and 133 are released, and both the planetary carrier 4 and the crank pulley 8 are rotatable. In this case, the same operation and effect as in the case where the clutch 13 is released in the first embodiment can be obtained.

When the sliding disk 134 is slid rightward in the figure (the state shown in FIG. 13), the first clutch 131
The friction of the friction portions 131a and 131b causes the rotation of the planetary carrier 4 to be prohibited. In this case, the operation is the same as when the clutch 13 is engaged in the first embodiment, and the roll vibration of the internal combustion engine is effectively reduced by utilizing the inertia moment of the crank pulley 8 and the accessories.

When the sliding disk 134 is slid to the left in the figure, the friction portions 133a, 133 of the second clutch 133 are moved.
The rotation between the crank pulley 8 and the sun gear 6 is fixed by friction between the members 33b. As a result, when the motor generator 9 is rotated in the same direction as the rotation direction of the crankshaft 2 to crank the internal combustion engine, the sun gear 6 applies a driving force 84 in the same direction as the rotation direction of the crankshaft 2 (see FIG. 8). However, since the rotation of the sun gear 6 is prevented by the second clutch 133 as in the case of the third embodiment, it is possible to prevent the reduction of the driving torque of the crankshaft 2 due to the rotation of the accessories. it can.

As described above, in the present embodiment, the first clutch 131 for restraining the rotation of the planetary carrier 4 and the second clutch 133 for restraining the rotation of the crank pulley 8 are integrated with each other. The number of parts can be reduced as compared with the case where the 133 is individually installed, and the size of the entire apparatus can be reduced and the manufacturing cost can be reduced.

[Brief description of the drawings]

FIG. 1 is a schematic diagram showing a planetary gear mechanism of an internal combustion engine according to a first embodiment of the present invention.

FIG. 2 is an alignment chart showing the rotational speed ratio of each component in a state where the clutch of FIG. 1 is released.

FIG. 3 is an explanatory view showing forces acting on each part of the planetary gear mechanism in the state of FIG. 2;

FIG. 4 is an explanatory diagram showing a force acting on the internal combustion engine body in the state of FIG. 2;

FIG. 5 is a nomographic chart showing the rotation speed ratio of each component when driving auxiliary equipment while the engine is stopped.

FIG. 6 is an explanatory diagram showing forces acting on each part of the planetary gear mechanism in the state of FIG. 5;

FIG. 7 is a nomographic chart showing a rotation speed ratio of each part when the engine is started.

FIG. 8 is an explanatory diagram showing a force acting on each component of the planetary gear mechanism when cranking is performed by the motor generator.

FIG. 9 is a schematic diagram showing a planetary gear mechanism of the internal combustion engine according to the second embodiment.

FIG. 10 is a schematic diagram showing a planetary gear mechanism of an internal combustion engine according to a third embodiment.

FIG. 11 is a schematic diagram showing a planetary gear mechanism of an internal combustion engine according to a fourth embodiment.

FIG. 12 is a schematic diagram showing a planetary gear mechanism of an internal combustion engine according to a fifth embodiment.

FIG. 13 is a schematic diagram showing a planetary gear mechanism of an internal combustion engine according to a sixth embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Internal combustion engine main body 2 ... Crank shaft 3 ... Internal gear 4 ... Planetary carrier 5 ... Planetary gear 6 ... Sun gear 8 ... Crank pulley 9 ... Motor generator 9a ... Rotor 9b ... Stator 13 ... Clutch

Claims (9)

[Claims] 1. A planetary gear mechanism for an internal combustion engine that rotates accessories in reverse with respect to a crankshaft of the internal combustion engine, an internal gear that rotates integrally with the crankshaft, and a sun gear that is connected to the accessories. A planetary gear that meshes with both the internal gear and the sun gear, and a planetary carrier that rotatably supports the planetary gear and that can rotate around the sun gear together with the planetary gear. A planetary gear mechanism for an internal combustion engine, comprising a rotor of a motor generator for controlling rotation of a carrier. 2. The apparatus according to claim 1, further comprising means for restraining rotation of the planetary carrier and the rotor.
3. The planetary gear mechanism for an internal combustion engine according to claim 1. 3. The planetary gear mechanism for an internal combustion engine according to claim 1, further comprising means for restraining rotation of the crankshaft and the internal gear. 4. The planetary gear mechanism for an internal combustion engine according to claim 1, further comprising a one-way clutch for inhibiting reverse rotation of the crankshaft and the internal gear. 5. The apparatus according to claim 1, further comprising means for temporarily increasing the driving resistance on the side of the crankshaft and the internal gear as compared with the driving resistance on the side of the auxiliary equipment and the sun gear. Planetary gear mechanism of internal combustion engine. 6. The planetary gear mechanism for an internal combustion engine according to claim 1, further comprising means for restraining rotation of the auxiliary devices and the sun gear. 7. The planetary gear mechanism for an internal combustion engine according to claim 1, further comprising a one-way clutch that prohibits the sun gear from rotating in the same direction as the crankshaft. 8. The apparatus according to claim 1, further comprising means for temporarily increasing the driving resistance on the auxiliary gear and the sun gear side than the driving resistance on the crankshaft and the internal gear side. A planetary gear mechanism for an internal combustion engine according to any one of the above. 9. A clutch mechanism in which a clutch for restraining rotation of the planetary carrier and the rotor is integrated with a clutch for restraining rotation of the accessory and the sun gear. 3. The planetary gear mechanism for an internal combustion engine according to claim 1.