JP2000297730A - Automotive engine starter - Google Patents

Abstract

(57) [Summary] [PROBLEMS] To reduce the time lag when restarting after stopping the engine in an idle stop car, and to eliminate the uncomfortable feeling given to the driver. SOLUTION: A ring gear 1 formed on an outer periphery of a flywheel 11 and a pinion gear 2a are always meshed. A roller clutch 13 is provided between the inner peripheral surface of the pinion gear 2a and the outer peripheral surface of the output shaft 12 of the motor 3 for rotating the pinion gear 2a. The roller clutch 13 transmits rotation only from the output shaft 12 to the pinion gear 2a. Further, since the cam surface is formed on the inner peripheral surface of the outer ring 16, when the pinion gear 2a rotates at high speed, the rollers 18, 18 are displaced to the outer diameter side,
The frictional contact between the rolling surfaces of these rollers 18 and the outer peripheral surface of the output shaft 12 is prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an apparatus for activating an automobile engine for activating an engine for traveling of an automobile. In particular, the engine is stopped (without idling) when the automobile is stopped. This is incorporated in a so-called idling stop vehicle to smoothly perform a starting operation.

[0002]

2. Description of the Related Art An automobile engine is started by rotating a flywheel fixed to a crankshaft of the engine by a motor. 10 to 11 show an example of a vehicle engine starting device that has been actually used conventionally and is widely known as described in various documents. The starting device includes a ring gear 1 formed on a flywheel of an automobile engine, a pinion gear 2 which can be disengaged from the ring gear 1, and a pinion gear 2.
And a motor 3 for rotationally driving the motor. The rotation of the motor 3 is performed by the drive gear 4, the idle gear 5, the outer gear 6,
The power can be transmitted to the pinion gear 2 via the overrunning clutch 7. The drive shaft 8 supporting the pinion gear 2 is supported inside the spline tube 37 via a torsion spline.

When the automobile engine is started, the drive shaft 8 is pushed to the left in FIG. 11, and the pinion gear 2 is moved forward while being displaced in the rotational direction, so as to mesh with the ring gear 1. Then, the ring gear 1 is rotationally driven by the motor 3 via the pinion gear 2 to start the engine. When the engine is started and the rotation speed of the drive shaft 8 is higher than the rotation speed based on the motor 3, the connection of the overrunning clutch 7 which is a spring clutch is disconnected, and the rotation of the started engine is reduced by the motor 3 To prevent transmission. Further, with the stop of energization of the electric motor 3,
The pinion gear 2 retracts from the ring gear 2.

The structure and operation of the starting device for an automobile engine are as described above. In recent years, for the purpose of energy saving and suppression of carbon dioxide emission, the engine is stopped without idling while the vehicle is stopped. It is possible to stop idling, and some are actually used. In the case of an idling stop vehicle having such a function, when the vehicle stops, the engine is stopped based on a signal of a vehicle speed of zero detected by a vehicle speed sensor.

On the other hand, when the vehicle is restarted, a clutch sensor for detecting the movement of the clutch pedal (in the case of a manual transmission vehicle) or an accelerator sensor for detecting the operation of the accelerator pedal (in the case of an automatic transmission vehicle) ), The vehicle engine is restarted as shown in the flowchart of FIG. 9B. That is, when it is recognized that the clutch pedal (or the accelerator pedal) is depressed, first, the pinion gear 2 moves forward and meshes with the ring gear 1 (see FIG. 10). Next, the motor 3
(FIG. 10) is started, and after restarting the automobile engine, the pinion gear 2 is moved backward.

[0006]

In the case of a conventional idle-stop vehicle, in order to restart the vehicle, a period from when a clutch pedal (or an accelerator pedal) is depressed to when the motor 3 is started to restart the engine. First, the pinion gear 2 needs to be advanced. For this reason, the time lag existing between the start of the operation for restarting the vehicle and the actual restart of the engine is increased, which gives the driver a sense of discomfort. In view of such circumstances, the present invention reduces the time lag existing between the start of the operation for restarting the car and the actual restart of the engine, and the driver feels uncomfortable. The present invention realizes a start-up device for an automobile engine without any problem.

[0007]

According to a first aspect of the present invention, there is provided an automobile engine starting apparatus, comprising: a ring gear formed on a flywheel of the automobile engine; A pinion gear having teeth formed on its outer peripheral surface meshed with the ring gear; a motor for driving the pinion gear; and a one-way clutch provided between an output shaft of the motor and the pinion gear. . The one-way clutch transmits torque from the output shaft to the pinion gear, but does not transmit torque from the pinion gear to the output shaft.

The starting device for an automobile engine according to a third aspect of the present invention includes a ring gear formed on a flywheel of the automobile engine and an axial direction, similarly to a conventionally known starting device for an automobile engine. Can be freely displaced over,
A pinion gear that meshes with the ring gear in a forward state for starting the vehicle engine and releases the meshing state with the ring gear in a backward state when the vehicle engine is operating; and rotationally drives the pinion gear. And a motor to perform. In particular, in the vehicle engine starter of the present invention, the pinion gear advances immediately after the stop of the vehicle engine, and meshes with the ring gear before the signal for starting the vehicle engine is issued. It becomes.

[0009]

According to the starting apparatus for an automobile engine of the present invention having the above-described configuration, in order to restart the automobile, the driver starts the motor to restart the engine after depressing a clutch pedal (or an accelerator pedal). There is no need to move the pinion gear forward until this occurs. For this reason, the time lag existing between the start of the operation for restarting the vehicle and the actual restart of the engine is reduced, and the driver does not feel uncomfortable.

[0010]

1 and 2 show a first example of an embodiment of the present invention corresponding to claims 1 and 2. FIG. This engine 9 is provided between the engine 9 and the transmission 10.
Flywheel 11 that rotates with the crankshaft
The ring gear 1 is provided on the outer peripheral edge of the ring gear 1. The ring gear 1 and the pinion gear 2a are always meshed. The pinion gear 2a is entirely formed in a cylindrical shape, and the teeth formed on the outer peripheral surface thereof are meshed with the ring gear 1.

An output shaft 12 of a motor 3 for driving the pinion gear 2a is provided on the inner diameter side of the pinion gear 2a.
Is inserted concentrically with the pinion gear 2a. And this pinion gear 2
a, a pair of one-way support bearings 14 and 14 and a seal ring 15 are provided between the inner peripheral surface of the shaft a and the outer peripheral surface of the output shaft 12.
a and 15b. In the illustrated example, the roller clutch 13 and the support bearings 14 and 14 share the same outer ring 16, and the outer ring 16 is internally fixed to the pinion gear 2a by interference fitting.

In order to constitute the roller clutch 13, a plurality of cam recesses, each called a ramp portion, are formed at equal intervals in the circumferential direction at an axially intermediate portion of the inner peripheral surface of the outer ring 16 in the axial direction. An intermediate portion in the axial direction of the inner peripheral surface is a cam surface 17. Then, on the inner diameter side of the cam surface 17,
A plurality of rollers 18;
And a retainer 19 which supports the roller so as to be able to roll and slightly displace in the circumferential direction. The retainer 19 engages the outer peripheral edge with a part of the cam surface 17 and
Relative rotation with respect to. On the other hand, a gap is provided between the inner peripheral edge of the retainer 19 and the outer peripheral surface of the output shaft 2. Further, between the retainer 19 and the rollers 18, 18, these rollers 18, 18 are provided.
Are provided in the same direction (the direction in which the cam recesses become shallower) with respect to the circumferential direction. Although the structure and operation of such a roller clutch 13 are well known, the starting device for an automobile engine of the present invention transmits such a torque to the roller clutch 13 from the output shaft 12 to the pinion gear 2a. However, it is assembled in a direction in which torque is not transmitted from the pinion gear 2a to the output shaft 12.

In order to form the support bearings 14, 14, the cam surface 1 is formed at both axial ends of the outer ring 16.
Portions sandwiching 7 from both sides in the axial direction form outer raceways 20 and 20 each having a cylindrical surface shape. And, between each of these outer raceways 20, 20 and the outer peripheral surface of the output shaft 12,
The rolling elements 21, 21 such as rollers are respectively attached to cages 23, 2.
A plurality is provided in a state of being held in a freely rolling manner by 3
Each of the support bearings 14 is a radial roller bearing. Each of these support bearings 1
Reference numerals 4 and 14 support a radial load applied to the pinion gear 2a when the engine 9 is started to prevent the roller clutch 13 from being damaged.

At both ends of the outer race 16, flanges 22, 22 having an inward flange shape are provided to prevent the support bearings 14, 14 from coming off. Further, a positive radial gap is provided in each of the support bearings 14 and 14.
When a radial load is applied to the pinion gear 2a, a radial gap between the support bearings 14 and 14 is generated.
This radial load is reduced to such an extent that it can be supported without transmitting it to the roller clutch 13. However, the pinion gear 2a rotates at high speed around the output shaft 12,
When the rolling elements 21 are pressed against the inner peripheral surface of the outer race 16 by centrifugal force, the outer peripheral surface of the output shaft 12 and the rolling surface of the rolling elements 21 The rolling contact is made only at the portion that supports the contact, and the other portions are not rubbed.

Further, seal rings 15a and 15b are provided between the inner peripheral surfaces of both ends of the pinion gear 2a and the outer peripheral surface of the output shaft 12, respectively, so that the roller clutch 13 and the support bearings 14 and 14 are respectively provided. To prevent leakage of grease filled into the grease. Note that, of both ends of the pinion gear 2a to which the seal rings 15a and 15b are mounted, the tip (the left end in FIGS. 1 and 2) has a small diameter to abut the end of the outer ring 16. On the other hand, the base end (the right end in FIGS. 1 and 2) has a large diameter so that the outer race 16 can be press-fitted.

According to the starting apparatus for an automobile engine of the present invention configured as described above, in order to restart the automobile, the motor 3 is depressed by depressing a clutch pedal (or an accelerator pedal) and then restarting the engine 9. There is no need to advance the pinion gear 2a until the start of the operation.
That is, since the pinion gear 2a is always meshed with the ring gear 1, the engine 9 can be restarted as long as the motor 3 is started by a signal generated based on the operation of restarting the automobile. Therefore, the time lag existing between the start of the operation for restarting the vehicle and the actual restart of the engine 9 is reduced, and the driver does not feel uncomfortable.

When the engine is restarted, the pinion gear 2
When the rotation speed of a becomes higher than the rotation speed of the output shaft 12, the connection of the roller clutch 13 is disconnected, and the rotation of the started engine is prevented from being transmitted to the motor 3. When the rotation speed of the pinion gear 2a further increases, each roller 18 constituting the roller clutch 13
18 moves to the bottom (deepest part) of the cam recess (not shown) against the elasticity of the spring (not shown) due to centrifugal force. Then, the rolling surface of each of the rollers 18, 18 and the outer peripheral surface of the output shaft 12 are separated from each other, and these two surfaces are prevented from friction with each other. As a result, the high-speed rotation of the pinion gear 2a (up to 70,000 to 80,000 rpm.
The roller clutch 1
3 will not burn.

Next, FIG. 3 corresponds to claims 1 and 2.
9 shows a second example of the embodiment of the present invention. In the case of this example, a reduction gear 27 including a drive gear 24, an idle gear 25, and a driven gear 26 is provided between the output shaft 12 of the motor 3 and the drive shaft 8a inserted on the inner diameter side of the pinion gear 2a. I have. Therefore, the rotational force of the output shaft 12 is reduced (for example, at a reduction ratio of about 4 to 5) and the torque is increased before the drive shaft 8a
The ring gear 1 (see FIG. 1) is rotationally driven by the pinion gear 2a disposed around the drive shaft 8a.

As described above, the rotational speed of the output shaft 12 is reduced and the torque is increased before the pinion gear 2 is rotated.
a, the speed reduction ratio between the pinion 2a and the ring gear 1 can be made smaller than in the case of the above-described first example. For this reason, after the engine is started, the rotation speed of the pinion gear 2a in a state in which the ring gear 1 is driven to rotate by the engine is compared with the case of the first example described above (by an amount corresponding to the reduction ratio). Can be smaller. The speed reducer provided between the output shaft 12 and the drive shaft 8a is not limited to the structure shown in the figure, but may be another structure such as a planetary gear type. If a planetary gear type speed reducer is used, the output shaft 12 and the drive shaft 8a are arranged coaxially, and the size of the starting device of the automobile engine can be reduced. Other configurations and operations are the same as in the case of the above-described first example.

Next, FIG. 4 corresponds to claims 1-2.
13 shows a third example of the embodiment of the present invention. In the case of this example, a deep groove type is provided between the inner peripheral surface of the base end portion (right end portion in FIG. 4) of the pinion gear 2b and the outer peripheral surface of the intermediate portion of the output shaft 12 (or the drive shaft 8a; the same applies hereinafter). Ball bearing 28 is provided. The inner ring 29 that constitutes the ball bearing 28 has a pair of retaining rings 3 locked on the outer peripheral surface of the intermediate portion of the output shaft 12.
Positions in the axial direction are achieved by 0 and 30.
Further, the outer ring 36 constituting the ball bearing 28 is sandwiched between a stepped portion 31 formed near the inner peripheral surface base end of the pinion gear 2b and a retaining ring 32 locked at the inner peripheral surface base end. hand,
The positioning is performed in the axial direction. Therefore, the pinion gear 2b is axially positioned by the ball bearing 28. Other configurations and operations are the same as those of the first example or the second example.

Next, FIG. 5 corresponds to claims 1-2.
14 shows a fourth example of an embodiment of the present invention. In the case of the present example, a deep groove ball bearing 28 is provided between the inner peripheral surface of the tip end portion (left end portion in FIG. 5) of the pinion gear 2c and the outer peripheral surface of the intermediate portion of the output shaft 12. Inner ring 2 constituting this ball bearing 28
9 is a stepped portion 3 formed on the outer peripheral surface of the intermediate portion of the output shaft 12.
3 and a retaining ring 3 locked to the outer peripheral surface of the distal end portion of the output shaft 12
0 to achieve positioning in the axial direction. The outer ring 36 constituting the ball bearing 28 is internally fixed to the pinion gear 2c by interference fit. Therefore, the pinion gear 2c is positioned in the axial direction by the ball bearing 28. In the case of this example, the support bearing between the roller clutch 13 and the ball bearing 28 is omitted, and the axial dimension of the outer ring 16a is shortened accordingly. In the illustrated example, the ball bearing 2
8 seal rings 34a, 34b
When the grease for lubricating the ball bearing 28 and the grease for lubricating the roller clutch 13 and the support bearing 14 are of the same type, the seal ring 34b on the roller clutch 13 side is omitted. Is also good. Other configurations and operations are the same as those of the above-described first or second example.

Next, FIG. 6 corresponds to claims 1-2.
15 shows a fifth example of the embodiment of the present invention. In the case of this example, a seal ring 15c provided on the base end side of the pinion gear 2d is provided between the inner peripheral surface of the outer ring 16b and the outer peripheral surface of the intermediate portion of the output shaft 12. Other configurations and operations are the same as those of the above-described fourth example.

Next, FIG. 7 corresponds to claims 1-2.
16 shows a sixth example of the embodiment of the present invention. In the case of the present example, only the roller clutch 13 is provided on the inner diameter side of the outer ring 16c which is fitted and fixed on the inner peripheral surface of the intermediate portion of the pinion gear 2e.
A pair of ball bearings 28 provided on both axial sides of the roller clutch 13 are used as support bearings. The inner races 29, 29 constituting the respective ball bearings 28, 28 are engaged with the stepped portions 33, 33 formed on the outer peripheral surface of the intermediate portion of the output shaft 12 and the outer peripheral surface or the intermediate portion of the distal end portion of the output shaft 12. It is sandwiched between the retaining rings 30 and 30 to achieve positioning in the axial direction. The outer races 36, 36 constituting the respective ball bearings 28, 28 are internally fitted and fixed to the pinion gear 2e by interference fit. Each of these ball bearings 28, 2
8 seal rings 34a, 34b attached to the openings at both ends
Of these, the seal ring 34 on the roller clutch 13 side
b and 34b may be omitted. Other configurations and operations are the same as those of the above-described first or second example.

Next, FIG. 8 corresponds to claims 1-2.
14 shows a seventh example of the embodiment of the present invention. In the case of this example, as a one-way clutch mounted between the intermediate portion of the inner peripheral surface of the pinion gear 2f and the outer peripheral surface of the intermediate portion of the output shaft 12,
A sprag clutch or cam clutch 35 is used. As the sprag clutch or cam clutch 35, at the time of high-speed rotation, the sprag or cam is displaced to the outer diameter side due to centrifugal force, and the sprag or cam and the outer peripheral surface of the output shaft 12 are separated from each other. Use the engagement type. Therefore, when the engine rotates at a high speed after the start of the engine, the sprags or cams do not rub against the outer peripheral surface of the output shaft 12.

When the present embodiment is carried out, a cylindrical sleeve made of hard metal is fitted to one or both of the intermediate portion of the inner peripheral surface of the pinion gear 2f and the outer peripheral surface of the intermediate portion of the output shaft 12. It may be fixed. However, in the illustrated example, the intermediate portion of the inner peripheral surface of the pinion gear 2f and the outer peripheral surface of the intermediate portion of the output shaft 12 are induction hardened and subjected to carbonitriding (for example, HR).
c55 or more) and the sleeve is omitted. Other configurations and operations are the same as those of the above-described sixth example.

Next, according to the invention described in claim 3,
This will be described with reference to FIG. 9A and FIGS. When the idle stop vehicle stops, the engine stops based on the signal from the vehicle speed sensor, despite the ignition switch being ON. However, in the case of the invention described in claim 3, when the ignition switch is ON, immediately after the engine stops, the drive shaft 8 is pushed to the left in FIG. 11 to displace the pinion gear 2 in the rotational direction. Then, it is moved forward to engage with the ring gear 1 and stand by as it is.

Then, the clutch pedal is depressed,
When a start operation such as depression of an accelerator pedal is performed, the motor 3 is started and the pinion gear 2 is started.
The ring gear 1 is driven to rotate via the, and the engine is restarted. Since the operation such as advancing the pinion gear is not performed between the start operation and the start of the motor 3, the engine is actually restarted after the operation for restarting the vehicle is started. The time lag existing until the vehicle is started is reduced, and the driver does not feel uncomfortable. When the engine is restarted in this way and the rotation speed of the drive shaft 8 becomes higher than the rotation speed based on the motor 3, the overrunning clutch 7 is disconnected, and the rotation of the started engine is reduced by the motor 3 To prevent transmission. Further, the pinion gear 2 retreats from the ring gear 1 with the stop of the power supply to the electric motor 3.

[0028]

Since the starting device for an automobile engine according to the present invention is constructed and operates as described above, it can be incorporated in, for example, an idling stop car to smoothly start the vehicle. And the spread of idle stop vehicles can contribute to air purification and carbon dioxide reduction.

[Brief description of the drawings]

FIG. 1 is a partial cross-sectional view partially showing a first example of an embodiment of the present invention;

FIG. 2 is an enlarged cross-sectional view showing only the upper central portion of FIG.

FIG. 3 is a partial cross-sectional view showing only a main part of a second example of the embodiment of the present invention.

FIG. 4 is a view similar to FIG. 2, showing a third example of the embodiment of the present invention;

FIG. 5 is a view similar to FIG. 2, showing the fourth example.

FIG. 6 is a view similar to FIG. 2, showing the fifth example;

FIG. 7 is a view similar to FIG. 2, showing the sixth example;

FIG. 8 is a view similar to FIG. 2, showing the seventh example;

FIG. 9A shows the operation of the invention described in claim 3;
(B) is a flowchart showing the operation of the conventional device, respectively.

FIG. 10 is a perspective view of a main part of a conventionally known starting device for an automobile engine.

FIG. 11 is a half cutaway view of a pinion gear and an overrunning clutch.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Ring gear 2, 2a, 2b, 2c, 2d, 2e, 2f Pinion gear 3 Motor 4 Drive gear 5 Idle gear 6 Outer gear 7 Overrunning clutch 8, 8a Drive shaft 9 Engine 10 Transmission 11 Fly hole 12 Output shaft 13 Roller clutch 14 Support Bearing 15a, 15b, 15c Seal Ring 16, 16a, 16b, 16c Outer Ring 17 Cam Surface 18 Roller 19 Cage 20 Outer Ring Track 21 Rolling Element 22 Flange 23 Cage 24 Drive Gear 25 Idle Gear 26 Idle Gear 26 Follower Gear 27 Reduction Device 28 Ball Bearing 29 Inner Ring 30 Retaining Ring 31 Step 32 Retaining Ring 33 Step 34a, 34b Seal Ring 35 Sprag Clutch or Cam Clutch 36 Outer Ring 37 Spline Tube

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Takeyuki Yoshiba, 1-5-50 Kugenuma Shinmei, Fujisawa City, Kanagawa Prefecture Nippon Seiko Co., Ltd. (72) Inventor Akira Iwamoto 1-5 Kugenuma Shinmei, Fujisawa City, Kanagawa Prefecture No. 50 Inside NSK Ltd.

Claims (3)

[Claims] 1. A ring gear formed on a flywheel of an automobile engine, a pinion gear formed into a cylindrical shape and having teeth formed on an outer peripheral surface thereof mesh with the ring gear, and a motor for driving the pinion gear; A one-way clutch provided between the output shaft of the motor and the pinion gear; the one-way clutch transmits torque from the output shaft to the pinion gear; however, the one-way clutch transmits torque from the pinion gear to the output shaft. A starting device for an automobile engine, which does not transmit power. The one-way clutch is selected from a disengagement type sprag clutch, a disengagement type cam clutch, and a roller clutch having a cam surface formed on an inner peripheral surface of an outer ring, and the centrifugal force transmits power. 2. The starting device for an automobile engine according to claim 1, wherein the starting device has a structure that acts in a direction in which the vehicle engine is disconnected. 3. A ring gear formed on a flywheel of an automobile engine, which is displaceable in the axial direction, meshes with the ring gear in a forward state for starting the automobile engine, and the automobile engine operates. In a starting device for an automobile engine including a pinion gear in which the meshing state with the ring gear is released in a retreat state when the vehicle is retracted, and a motor that rotationally drives the pinion gear, the pinion gear includes A starting device for an automobile engine, wherein the starting device for the automobile engine immediately moves forward after the stop and is engaged with the ring gear before a signal for activating the automobile engine is issued.