JP2001213180A - Auxiliary machinery arrangement structure for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a speed reduction ratio of an electric motor and an engine side to prevent the occurrence of wear and seizure due to excessive rotation of the electric motor, reduce the noise caused by meshing of gears, shorten a total length of an engine to increase engine output, and improve the mounting property on a vehicle in the internal combustion engine constituted so as to transmit power of the electric motor to a crank shaft. SOLUTION: In an internal combustion engine system connecting the electric motor with the crank shaft of the internal combustion engine to transmit its power to the crank shaft, a power transmission device connecting the electric motor with the crank shaft is arranged between the crank shaft and a joint device, and a rotary member of the power transmission device is constituted in such a way that its diameter is smaller than an outside diameter of the joint device and is arranged in such a way that its total length is within a total length of the engine or a transmission so that an output shaft core of the electric motor becomes parallel with a crank shaft core.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an internal combustion engine in which a transmission is connected to a crankshaft via a coupling device such as a flywheel, a clutch or a torque converter, and the power of an electric motor can be transmitted to the crankshaft. The present invention relates to a structure for arranging auxiliary equipment of an engine.

[0002]

2. Description of the Related Art In recent years, automobiles have been started as a means for improving fuel efficiency (fuel consumption rate) due to environmental problems and the like.
It has been proposed to employ a stop system, that is, means for stopping the idling operation of the engine under certain conditions to reduce fuel consumption when the vehicle is stopped. In such a start / stop system, the vehicle is started / stopped by computer control. At the time of such a start, a start-meshing type engine in which a pinion gear of a starter (starting motor) meshes with a ring gear attached to a crankshaft. In this case, the noise generated when the pinion gear meshes with the ring gear and the start-up delay of the vehicle occur without regard to the driver's intention, which often gives the driver an uncomfortable feeling.

[0003] In recent years, hybrid systems have been adopted in automobiles in which an output is obtained by combining an internal combustion engine and an electric motor, and the electric motor is used as a starter. In such a hybrid system, since the motor side is always connected to the engine side, there is no hitting sound due to the engagement between the motor side pinion and the engine side ring gear as in the conventional system, and There is no vehicle start delay. Further, since the gears are always meshed, the accuracy of the gears is increased, and noise due to meshing is also reduced.

FIG. 8 shows an example of the prior art of an internal combustion engine using such a hybrid system and a structure for arranging auxiliary equipment therefor. FIG. 8A shows a case where the coupling device is provided with a torque converter, and FIG. 8B shows a case where the coupling device is provided with a flywheel and a clutch. 8, reference numeral 100 denotes an engine (internal combustion engine), 101 denotes a transmission (transmission), and 18 denotes an electric motor. FIG. 8 (A)
In both cases (B) and (B), the electric motor 18
The engine 100 and the transmission 101 are concentrically disposed between the transmission 100 and the transmission 101.

[0005]

In the start-time meshing method, generally, the outer diameter of a ring gear attached to a crankshaft is configured to be larger than the outer diameter of the coupling device. When the reduction ratio between the pinion gear of the electric motor 18 and the ring gear is set to be equal to that of the conventional starter, it becomes about 10. For example, when the maximum engine speed is 7000 rpm, the electric motor 1
The rotation speed of the pinion gear No. 8 is excessively large at 70,000 RPM, and wear and seizure around the electric motor 18 and the pinion gear are observed.

[0006] The hybrid system is shown in FIG.
As shown in FIG. 1, an electric motor 18 is provided between an engine 100 and a transmission 101.
0 and to are arranged concentrically with the axis 41 of the transmission 101, the total length of the engine system increases the length L ₀ equivalent of the electric motor 18, mounting property is also low in the vehicle.

Further, in the prior art, since the electric motor 18 is connected immediately after the engine 100, the heat of the engine 100 is transmitted to the electric motor 18 to cause the electric motor 18 to overheat. See

The present invention has been made in view of the above-mentioned problems of the prior art, and in an internal combustion engine having a power transmission device capable of transmitting a power of an electric motor to the crankshaft while connecting a transmission to the crankshaft via a coupling device. By reducing the reduction ratio between the pinion gear and the ring gear on the engine side, it is possible to prevent the occurrence of wear and seizure around the motor due to overspeed of the motor, and to shorten the total length of the internal combustion engine system including the motor, It is another object of the present invention to improve the mountability on a vehicle by suppressing the expansion of the entire width, and to prevent the electric motor from being overheated due to the heat of the internal combustion engine.

[0009]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a transmission according to the first aspect of the present invention, wherein a transmission is connected to a crankshaft of an internal combustion engine via a coupling device such as a flywheel, a clutch, a torque converter, or the like. And the output shaft of the motor is arranged parallel to the crankshaft,
An accessory arrangement structure for an internal combustion engine having a power transmission device capable of transmitting the power of the electric motor to the crankshaft, wherein the power transmission device is disposed between the internal combustion engine and a coupling device, The power transmission device includes a rotating member configured to have a smaller diameter than the outer diameter of the coupling device and attached to the crankshaft, and a connection unit that connects the rotating member to an output shaft of the electric motor. We propose a featured structure of auxiliary equipment for internal combustion engines.

According to this invention, a power transmission device for connecting the output shaft of the electric motor and the crankshaft of the internal combustion engine is provided between the rotation shaft of the internal combustion engine and the coupling device, and the electric motor is The output shaft is arranged so as to be parallel to the crankshaft, and the overall length of the internal combustion engine system including the internal combustion engine, the electric motor, the power transmission device, and the transmission is kept compact, and the mountability on the vehicle is deteriorated. Instead, the rotating member of the power transmission device is configured to have a smaller diameter than the outer diameter of the coupling device and is attached to the crankshaft,
The distance between the output shaft of the electric motor and the crankshaft can be set short, and the overall width of the internal combustion engine system is also compact.
Further, the reduction ratio can be significantly reduced to about 3 to 4 as compared with the related art. Accordingly, the number of rotations of the electric motor can be reduced, and wear and seizure around the electric motor and the pinion gear can be prevented.

According to the invention, the power transmission device is disposed between the crankshaft and the coupling device.
Since the electric motor is separated from the high-temperature internal combustion engine by making its output axis parallel to the axis of the crankshaft, the electric motor is connected immediately after the internal combustion engine in the prior art. In addition, the heat of the internal combustion engine is not directly transmitted to the electric motor, and the occurrence of overheating of the electric motor can be prevented.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to an embodiment shown in the drawings. However, unless otherwise specified, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention thereto, but are merely illustrative examples. It's just

FIG. 1 is a configuration diagram showing a first embodiment of an arrangement structure of an automotive internal combustion engine system according to an embodiment of the present invention, in which (A) is a plan view and (B) is a front view. FIG. 2 is a configuration diagram showing a second embodiment, FIG. 3 is a cross-sectional view along a crankshaft center near a starter ring gear of an automotive internal combustion engine according to an embodiment of the present invention, and FIG. 4 is a line AA in FIG. FIG. 5 is a cross-sectional view taken along line BB of FIG. 4, FIG. 6 is a cross-sectional view of a power transmission unit of the electric motor, and FIG. 7 is a second embodiment of the power transmission device.
FIG.

In the internal combustion engine system shown in FIGS.
100 is an engine (internal combustion engine), 101 is a transmission (transmission), 18 is an electric motor, 102 is a power transmission device (length L ₁ ) comprising gear transmission connection means described later, 103 is a flywheel and a clutch or a fluid. It is a joint device including a joint and the like.

In the first embodiment of the internal combustion engine system shown in FIGS. 1A and 1B, a power transmission device 1 is provided between an output end of an engine 100 and an input end of a coupling device 103.
02, and the electric motor 18 is accommodated within the entire length of the engine 100 so that the shaft 42 is parallel to the output shaft 41 and from the power transmission device 102 toward the front of the engine 100. In this way, the engine 100 is arranged at a position near the upper part. The electric motor 18 is installed on the intake side of the engine 100 in order to reduce heat transfer from the engine side.

In the second embodiment of the arrangement structure of the internal combustion engine system shown in FIG. 2, a power transmission device 102 is arranged between an output end of the engine 100 and an input end of the coupling device 103, and the electric motor 18 The transmission of the engine 100 is set so that its axis 42 is parallel to the output axis 41 and extends from the power transmission device 102 to the rear of the transmission 101 so as to fit within the entire length of the transmission 101. It is arranged at a position closer to the top of 101. The electric motor 18
Is installed on the intake side of the engine 100 to reduce heat transfer from the engine side, as in the first embodiment.

FIG. 3 showing details of the power transmission device 102.
In 5 to 5, 5 is a cylinder block of the engine, 7 is a crankshaft, 6 is a main bearing, and 8 is an oil pan. 12
Is an oil hole drilled in the shaft end of the crankshaft 7 to supply lubricating oil to the main bearing 6, and is opened in the bearing surface of the main bearing 6. 1 is a ring gear for a starter, 3 is a flywheel, and the boss 1a of the flywheel 3 and the ring gear 1 is fixed to the shaft end face of the crankshaft 7 by a plurality of bolts 35 together. As shown in FIG. 1, the outer diameter of the ring gear 1 is formed smaller than the outer diameter of the flywheel 3.

Reference numeral 30 denotes a one-way clutch, the input side of which is connected to the ring gear 1 and the output side of which is connected to a boss 1a fixed to the crankshaft 7 so as to move from the ring gear 1 side to the crankshaft 7 side. Only rotation transmission is possible.

A bearing 32 is interposed between the inner circumference of the ring gear 1 and the outer circumference of the boss 1a, and supports the input side and the output side of the one-way clutch 30 so as to be relatively rotatable. An oil hole 31 penetrates through the inside of the crankshaft 7 and the boss 1a. The oil hole 31 communicates the oil hole 12 in the crankshaft 7 with the one-way clutch 30, and the lubricating oil in the oil hole 12 A part is supplied to the one-way clutch 30 through the oil hole 31.

Reference numeral 9 denotes a gear case, and 13 denotes a transmission case. The gear case 9 is fastened and fixed to the cylinder block 5 together with the transmission case 13 by means of bolts 012 on the outer peripheral side.
5 and is fixed to the cylinder block 5 by bolts 25 on the inner peripheral side. Reference numeral 11 denotes a gear cover whose outer peripheral portion is fixed to the gear case 9 by a plurality of bolts 26. An oil reservoir space 23 is formed by the inside of the gear cover 11 and the gear case 9.
The ring gear 1 is housed in 3.

A gap 29 for introducing oil is formed between the crankshaft 7 and the cylinder block 5 so as to communicate with the upper part of the oil reservoir space 23. Reference numeral 21 denotes an oil return hole formed in the gear case 9 and communicates a lower portion of the oil reservoir space 23 with the inside of the oil pan 8. The position of the oil return hole 21 in the engine height direction is the same as that of the ring gear 1.
The outer circumference of the sub gear 2 is set slightly higher than the oil level 24 in the oil pan 8 and is set at a position where a certain amount of lubricating oil is stored in the oil storage space 23.

A breathing hole 22 communicates the upper part of the oil pan 8 with the inside of the oil storage space 23 to release air from the oil storage space 23. An O-ring 14 is interposed between the boss 1a of the ring gear 1 and the outer peripheral surface of the crankshaft 7. Reference numeral 4 denotes an oil seal attached to the gear cover 11, which seals the oil reservoir space 23 from the outside.

4 and 5, reference numeral 18 denotes an electric motor.
It is fixed to the gear case 9 by a plurality of bolts 27. Reference numeral 17 denotes a pinion gear fixed to a motor shaft 19 of the electric motor 18, and 16 denotes both ends of the gear case 9.
As shown in FIG. 4, the pinion gear 17, the intermediate gear 16, and the ring gear 1 are always meshed with each other, and the power of the electric motor 18 is transmitted to the pinion gear 17, the intermediate gear. Gear 1
6 and the ring gear 1 to the flywheel 3 and the transmission 101 (see FIG. 1). 34 is the electric motor 18 and the gear case 9
And an O-ring interposed therebetween.

FIG. 6 shows a power transmission mechanism from the electric motor 18 to the pinion gear 17. In FIG. 6, reference numeral 60 denotes a motor main body, and 51 denotes a first-stage reduction gear connected to an output end of the motor main body 60. , 52 is the first-stage speed reducer 51
Is a motor shaft connected to the output end of the second-stage speed reducer 52, and the pinion gear 17 is fixed to the shaft end of the motor shaft 19.

The first-stage speed reducer 51 and the second-stage speed reducer 5
Reference numeral 2 denotes a known planetary gear type speed reducer, and the speed reduction ratio between the two is such that the speed reduction ratio between the pinion gear 17 and the ring gear 1 is 3 to 3.
It is set to be about 4. 53 is a housing, 5
6, 57 and 59 are bearings for supporting the motor shaft 19, 55 is an oil seal, 58 is an O-ring, and 54 is a starter switch.

In the internal combustion engine system having the accessory arrangement structure having such a configuration, the rotational force of the engine 100 crankshaft 7 passes through the ring gear 1 which is a rotating member of the power transmission device 102 and the flywheel 3 and the clutch, or It is transmitted to a joint device 103 such as a torque converter. On the other hand, the torque of the electric motor 18 from the motor body 60 is reduced by the first-stage speed reducer 51 and the second-stage speed reducer 52, and then transmitted from the motor shaft 19 to the pinion gear 17 of the power transmission device 102.

When the starter switch 54 is turned on when the engine 100 is started, the rotational force of the motor body 60 of the electric motor 18 is reduced by the first-stage speed reducer 51 and the second-stage speed reducer 52, and the motor shaft The transmission is transmitted to the pinion gear 17 via the pinion 19, from the pinion gear 17 to the ring gear 1 via the intermediate gear 16, and the crankshaft 7 is rotated. Then, when the engine 100 starts and the torque of the crankshaft 7 exceeds the torque of the motor shaft 19, the one-way clutch 30 disconnects the connection between the crankshaft 7 and the motor shaft, and the motor stops.

Then, when motor assist is required during traveling, the electric motor 18 is restarted. The rotational force transmitted to the pinion gear 17 is transmitted to the ring gear 1 via the intermediate gear 16, where the engine 100
Is superimposed on the rotational force of the crankshaft 7. Then, the superposed two-system rotational force, that is, the rotational force of the engine 100 and the rotational force of the electric motor 18 are transmitted to the transmission 101 by the connection of the coupling device 103 and become the driving force of the vehicle.

In this case, the outer diameter of the ring gear 1, which is a rotating member of the power transmission device 102, is smaller than the outer diameter of the flywheel 3 constituting the coupling device 103, and is attached to the crankshaft 7. As a result, the reduction ratio between the pinion gear 17 at the output end of the electric motor 18 and the ring gear 1 constituting the rotating member can be significantly reduced to about 3 to 4 as compared with the prior art.
Of the electric motor 18 can be reduced.
The motor assist can be performed without applying an excessive load to the motor, and seizure or the like can be prevented. Further, the meshing ratio of the gear is increased, and the gear meshing noise can be reduced.

According to this embodiment, the power transmission device 102 is disposed between the crankshaft 7 of the engine 100 and the coupling device 103, and the electric motor 18
Is made separate from the high temperature engine 100 side so that its motor axis 42 is parallel to the axis of the crankshaft 7, that is, the output axis 41, so that the heat of the engine 100 Overheating of the electric motor 18 is avoided.

The second embodiment of the power transmission device shown in FIG. 7 does not include the one-way clutch 30 of the first embodiment. In FIG. 7, reference numeral 2 denotes a sub gear, which is fixed to a side surface of the ring gear 1. I have. Reference numeral 10 denotes a torque spring attached to the ring gear 1 and the sub gear 2. In this case, the electric motor always rotates in synchronization with the engine, so that the effect is further enhanced. In this embodiment, in addition to the gap 29, a small-diameter oil hole 20 communicating the oil hole 12 of the crankshaft 7 and the oil storage space 23 is provided, and lubricating oil in the oil hole 12 is provided. Part of the
It may be configured to be introduced into the oil reservoir space 23 through the oil hole 20. Other configurations are the same as those of the first embodiment, and the same members are denoted by the same reference numerals.

[0032]

As described above, according to the present invention, the total length of the internal combustion engine system including the internal combustion engine, the electric motor, and the transmission is smaller than that of the prior art in which the electric motor is arranged in series between the internal combustion engine and the transmission. Compared with this, it is greatly reduced, and the mountability on the vehicle is improved.

Also, since the rotating member of the power transmission device is configured to have a smaller diameter than the outer diameter of the coupling device, the reduction ratio between the output shaft of the electric motor and the crankshaft is smaller than that of the prior art. It becomes possible to make it significantly smaller. As a result, the number of revolutions of the electric motor can be reduced, and the occurrence of wear and image sticking can be prevented.

A power transmission device is disposed between the crankshaft and the coupling device, and the electric motor is separated from the high-temperature internal combustion engine side so that the output shaft of the motor is parallel to the axis of the crankshaft. Since the shaft is used, the heat of the internal combustion engine is not directly transmitted to the electric motor as in the prior art in which the electric motor is connected immediately after the internal combustion engine, so that the overheating of the electric motor can be prevented.

[Brief description of the drawings]

FIG. 1 is a configuration diagram showing a first example of an arrangement structure of an automotive internal combustion engine system according to an embodiment of the present invention, where (A) is a plan view and (B) is a front view.

FIG. 2 is a configuration diagram showing a second embodiment.

FIG. 3 is a cross-sectional view along the crankshaft center near the starter ring gear of the internal combustion engine for an automobile according to the embodiment of the present invention.

FIG. 4 is a sectional view taken along line AA of FIG. 3;

FIG. 5 is a sectional view taken along line BB of FIG. 4;

FIG. 6 is a sectional view of a power transmission unit of the electric motor.

FIG. 7 is a view corresponding to FIG. 3, showing a second embodiment of the power transmission device.

FIG. 8 is a diagram corresponding to FIG. 1 showing a conventional technique.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Ring gear 1a Boss part 3 Flywheel 5 Cylinder block 6 Main bearing 7 Crank shaft 8 Oil pan 9 Gear case 11 Gear cover 12, 20, 31 Oil hole 13 Transmission case 16 Intermediate gear 17 Pinion gear 18 Electric motor 19 Motor shaft 21 Oil return hole 22 Breeze hole 23 Oil reservoir space 30 One-way clutch 32 Bearing 51 First-stage reducer 52 Second-stage reducer 100 Engine 101 Transmission 102 Power transmission device 103 Coupling device

Claims (1)

[Claims] 1. A transmission is connected to a crankshaft of an internal combustion engine via a coupling device such as a flywheel, a clutch, and a torque converter, and an output shaft of an electric motor is arranged parallel to the crankshaft. In an auxiliary machine connection structure for an internal combustion engine having a power transmission device capable of transmitting power to the crankshaft, the power transmission device is disposed between the internal combustion engine and a coupling device, and is provided outside the coupling device. A rotating member configured to have a smaller diameter than the diameter and attached to the crankshaft,
An auxiliary machine arrangement structure for an internal combustion engine, comprising: connecting means for connecting the rotating member to an output shaft of the electric motor.