JP3521043B2 - Ignition device for internal combustion engine - Google Patents

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 ignition device in which a rotary drive body for rotationally driving a distributor receives a radial load (a radial load).

[0002]

2. Description of the Related Art A distributor for generating an ignition signal for an engine is directly driven by an engine component (corresponding to a rotary driving body) such as a camshaft.

[0003]

However, when the rotary drive member for driving the distributor receives a large radial load, the radial load is also applied to the shaft of the distributor, which causes a problem that the life of the bearing portion supporting the shaft is shortened. . Further, since the bearing portion is formed on the case of the distributor, it is necessary to replace the entire distributor when replacing the bearing portion for the purpose of life.

This will be specifically described with reference to FIGS. 2 and 7. When the distributor 21 is driven by a drive gear 22 (corresponding to a rotary driving body), the drive gear 22 is driven by a crankshaft timing gear 23 as shown in FIG.
Receives rotational torque A from. Further, a large power steering load torque B due to driving the power steering pump drive gear 25 is applied to the drive gear 22. Therefore, the drive gear 22 receives a large rotational torque A from the idle gear 24, and a combined load (radial load) C of the large rotational torque A and the large power steering load torque B is generated in the drive gear 22. That is, a large radial load C is generated on the drive gear 22.

Here, as shown in FIG. 7, when the drive gear 22 directly drives the shaft 26 of the distributor 21, the drive gear 22 receives a large radial load C. Therefore, this radial load C is applied to the shaft 26. Also given to. For this reason, the surface pressure of the bearing portion 27 supporting the shaft 26 becomes high, and the bearing portion 27 is worn early beyond the allowable surface pressure, resulting in a short life of the bearing portion 27 supporting the shaft 26. Occurs. Further, the bearing portion 27 is a case 28 of the distributor 21.
Therefore, in order to replace the worn bearing portion 27, it is necessary to replace the entire distributor 21.

As a measure against bearing wear, the shaft 2
Although it is conceivable to widen the clearance between the shaft 6 and the bearing portion 27, the shaft 26 may be eccentric or may vibrate in the radial direction, resulting in a problem such as variations in the output signal of the distributor 21.

[0007]

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a bearing portion for a shaft of a distributor even when a large radial load is applied to a rotary drive body that drives the distributor. (EN) It is possible to provide an ignition device for an internal combustion engine, which has a long life and does not cause a problem such as a variation in the output signal of the distributor. Another object of the present invention is to provide an ignition device for an internal combustion engine, which can be easily and inexpensively repaired even if the bearing portion is worn.

[0008]

The ignition device for an internal combustion engine of the present invention employs the following technical means. [Means of Claim 1] By performing as in Claim 1,
Even if a large radial load is applied to the rotary drive that drives the distributor, the radial load received by the rotary drive will be received by the discase through the rotary shaft, and the radial load received by the rotary drive on the distributor shaft. Does not get transmitted.

Therefore, the bearing portion of the shaft of the distributor can have a long life. Further, even if the bearing in the discase causes a defect due to wear, the defect does not occur in the bearing portion of the distributor, and the defect can be eliminated by replacing the discase in which the rotary shaft is assembled. In addition, since the bearing that supports the shaft is prevented from wearing out without widening the clearance between the shaft and the bearing, there is no problem of eccentricity or vibration of the shaft, and no problems such as dispersion of the output signal of the distributor. . That is, the shaft diameter of the distributor and the structure of the bearing can be used without changing from the conventional one.

[Means of Claim 2] According to claim 2, oil is supplied to each of the bearing portion of the rotary shaft and the bearing portion of the shaft. Therefore, lubrication of each of the bearing portion of the rotating shaft and the bearing portion of the shaft is ensured, wear of each bearing portion is suppressed, and each bearing portion is cooled by oil, and heat generation is suppressed.

[Means of Claim 3] As described in claim 3, the opening of the oil drain hole on the rotary shaft side is provided above the vertical bottom of the rotary shaft, so that the oil supplied from the oil supply hole is Part of it is securely held by the bearing. For this reason,
It becomes easy to form an oil film on the sliding portion of the bearing portion, and the life of the bearing portion can be extended.

[Means of Claim 4] [0012] As in claim 4, the opening of the oil drain hole on the rotary shaft side is provided between the vertical bottom of the rotary shaft and the opening of the oil supply hole on the rotary shaft side. As a result, the distance that the oil flows from the oil supply hole to the oil drain hole becomes long. Therefore, the oil supply capacity to the bearing portion is increased, and the life of the bearing portion can be extended.

[Means for Claim 5] As described in claim 5, by making the diameter of the rotating shaft larger than the diameter of the shaft, the load of the bearing portion supporting the rotating shaft can be reduced, and the bearing supporting the rotating shaft. The part can have a long life.

[Means of Claim 6] According to claim 6, when the distributor with the rotating shaft and the disk case is mounted on the engine, the load due to the prying of the bearing portion received from the rotating shaft and the radial load. The load on the bearing part due to the load can be reduced. Also, since the rotation of the rotating shaft is transmitted to the shaft via the universal joint,
Even if the rotary shaft is eccentric or vibrates due to the clearance between the rotary shaft and its bearing, the eccentricity or vibration is not transmitted to the shaft. In this way, even if the rotary shaft is eccentric or vibrates, the shaft does not eccentric or vibrate, so that there is no problem such as variation in the output signal of the distributor.

[Means for Claim 7] Since the rotary shaft receives a radial load from the rotary drive body, the side of the rotary shaft near the rotary drive body receives a large radial load. Therefore, claim 7
As described above, by applying the slide bearing closer to the rotary drive to the one having higher wear resistance than the slide bearing on the far side, the wear speed of the plurality of slide bearings supporting the rotary shaft can be made uniform. .

[0016]

BEST MODE FOR CARRYING OUT THE INVENTION Next, an embodiment of the present invention will be described with reference to first and second examples and modified examples. [Structure of First Embodiment] FIGS. 1 and 2 show a first embodiment. FIG. 1 is a sectional view of an internal combustion engine ignition device, and FIG. 2 is a front view of an engine with a gear cover removed. .

In the engine of this embodiment, the distributor 1 is driven by a drive gear 2 (corresponding to the rotary drive body of the present invention). As shown in FIG. 2, the drive gear 2 is integrated with a crankshaft. It rotates by receiving the rotation torque A of the idle gear 4 driven by the rotating crankshaft timing gear 3. Also, drive gear 2
Is the power steering pump drive gear 5 as in the above-mentioned item.
And a large power steering load torque B is applied to the drive gear 2 by the load of the power steering pump. Therefore, the drive gear 2 receives a large rotational torque A from the idle gear 4, and a combined load (radial load) C of the large rotational torque A and the large power steering load torque B is generated in the drive gear 2. That is, a large radial load C is generated on the drive gear 2.

As shown in FIG. 1, the drive gear 2 is rotatably supported in a cantilever state by a ball bearing 8 provided on a gear cover 7 fixed to a gear case 6 which is an engine component. Therefore, drive gear 2
If the shaft 9 of the distributor 1 is directly connected to the shaft 9, the radial load C of the drive gear 2 will be applied to the shaft 9.

Therefore, between the drive gear 2 receiving the radial load C and the shaft 9 of the distributor 1, the radial load C of the drive gear 2 is received and only the rotational force of the drive gear 2 is applied to the shaft 9 of the distributor 1. A radial load removal unit U is provided for transmission to the. Since the shaft 9 of the distributor 1 is provided so as not to transmit the radial load C, the distributor 1 having the conventional structure such as the shaft 9 and the bearings 11 and 12 is adopted.

The unit U comprises a disk case 15 fixed to both the case 1a of the distributor 1 and the gear case 6, and a rotary shaft 10 rotatably supported by the disk case 15. A spline gear 13 that is spline-fitted to the drive gear 2 is fixed to one end of the rotary shaft 10, and the rotary torque of the drive gear 2 is transmitted to the rotary shaft 10. The other end of the rotary shaft 10 is connected to the shaft 9 via a universal joint 14 for absorbing radial vibration and eccentricity and transmitting only the rotational force to the shaft 9.

Between the disk case 15 and the rotary shaft 10, two bearing portions 16 and 17 are arranged in the axial direction in order to reduce the rotational resistance of the rotary shaft 10. In addition,
The bearing portions 16 and 17 of this embodiment employ sliding bearings made of metal bearings. The diameter of the rotating shaft 10 supported by the bearings 16 and 17 is larger than that of the shaft 9 (for example, the diameter of the rotating shaft 10 is about 2 times the diameter of the shaft 9).
It is provided about twice).

In this way, the diameter of the rotary shaft 10 is changed to the shaft 9
By making the diameter larger than the diameter, the surface pressure of the bearing portions 16 and 17 becomes low, and the life of the bearing portions 16 and 17 can be extended. Further, by making the diameter of the rotating shaft 10 thicker, even when a load due to a twist is applied to the rotating shaft 10 when the disk case 15 is assembled to the gear case 6, it is advantageous against the bending stress of the shaft.

A clearance (not shown) is provided between the rotating shaft 10 and the bearing portions 16 and 17 which are plain bearings. By providing this clearance, it is possible to reduce the prying load applied to the bearing portions 16 and 17 from the rotary shaft 10 when the disk case 15 is assembled to the gear case 6, and to reduce the drive load on the rotary shaft 10 to reduce the load on the bearing portion 1.
The surface pressure of the bearings 6 and 17 becomes low, and the life of the bearing portions 16 and 17 can be extended.

Further, even if the rotary shaft 10 is eccentric or vibrates due to the clearance between the rotary shaft 10 and the bearing portions 16 and 17,
Since the eccentricity and vibration are absorbed by the universal joint 14, they are not transmitted to the shaft 9. Thus, even if the rotating shaft 10 is eccentric and vibrates, the shaft 9 is not eccentric and vibrates.
Problems such as variations in the output signal of the distributor 1 do not occur.

A part of the discase 15 is a gear case 6
The oil spattered in the gear cover 7 is disposed in the gear case 6 so that it can be inserted into the gear case 6.
A supply path 6a is provided which leads to the upper part of the insertion part of 5. An oil receiver 15a for receiving the oil supplied from the supply passage 6a is formed in the inserted portion of the disk case 15, and the disk case 15 receives the oil supplied to the oil receiver 15a from the bearing portion 16 of the rotary shaft 10. , 17 and bearing portions 11, 12 of the shaft 9 are provided with oil supply holes 15b, 15c for supplying oil.

Further, the rotating shaft 10 is attached to the case 15.
The oil drain holes 15d and 15e for discharging the oil supplied to the bearing portions 16 and 17 of the shaft 9 and the bearing portion 11 of the shaft 9 and the universal joint 14 into the gear cover 7 are formed. The two oil drain holes 15d and 15e in the first embodiment are provided vertically below the rotary shaft 10, respectively. The oil discharged from the oil drain holes 15d and 15e is returned to the inside of the gear cover 7 from the gap 6b between the gear case 6 and the drive gear 2 or the discharge path 6c provided in the gear case 6.

In this way, the oil in the gear cover 7 is transferred to the bearing portions 16 and 17 of the rotary shaft 10 and the bearing portion 1 of the shaft 9.
1, the bearing portions 16 and 17 of the rotary shaft 10 and the bearing portion 1 of the shaft 9 are supplied to the universal joint 14 respectively.
1, lubrication of the universal joint 14 is ensured and wear is suppressed, and the bearings 11, 16, 17 and the universal joint 1 are
4, the bearings 11, 16, 17 and the universal joint 14 are cooled by the oil, and heat generation can be suppressed.

In the first embodiment, two iron thrust washers 13a are interposed between the spline gear 13 and the bearing portion 16.

[Operation of the First Embodiment] Next, the operation of the first embodiment will be described. During operation of the engine, the crankshaft timing gear 3 is rotated by the rotation of the crankshaft.
The crankshaft timing gear 3 rotationally drives the idle gear 4, the drive gear 2, the power steering pump drive gear 5, and the like. At this time, the drive gear 2
A large radial load C due to a large rotational torque A and a large power steering load torque B is applied.

Since the drive gear 2 is cantilevered by the gear cover 7 via the ball bearings 8, the radial load C applied to the drive gear 2 is the rotary shaft 1
Add to 0. The radial load C received by the rotary shaft 10 is
Disk case 1 via bearings 16 and 17 of rotating shaft 10
5 will receive. Since the shaft 9 is connected to the rotary shaft 10 via the universal joint 14, the radial load C is not transmitted to the shaft 9, but only the rotational force is transmitted to the shaft 9.

[Effects of the First Embodiment] In the internal combustion engine ignition device according to the present embodiment, as described above, even if a large radial load C is applied to the drive gear 2, the radial load C is Since the rotating shaft 10 receives and is not transmitted to the shaft 9, the bearings 11 and 12 of the shaft 9 can have a long life. In addition, since the bearings 11 and 12 are prevented from wearing without widening the clearance between the shaft 9 and the bearings 11 and 12, there is no problem that the shaft 9 is eccentric or vibrates, and the output signal of the distributor 1 varies. The problem of does not occur either. That is, even when a large radial load C is applied to the drive gear 2 that drives the distributor 1, the distributor 1 having the conventional structure such as the shaft 9 and the bearings 11 and 12 can be adopted, and high reliability can be obtained.

Further, even if the bearings 16 and 17 wear out due to the radial load C received from the rotary shaft 10, the bearings 11 and 12 of the distributor 1 do not have any trouble, and the rotary shaft 10 does not have any trouble. The problem can be solved only by replacing the case 15 (unit U) in which 10 is incorporated. Here, the rotating shaft 10 and the case 1
As shown in FIG. 1, the unit U including the bearings 16 and 17 has a simple structure and a small number of parts. Therefore, the unit U is less expensive than the distributor 1, and the defect can be easily and inexpensively solved. .

[Second Embodiment] FIGS. 3 to 5 show a second embodiment. FIG. 3 is a sectional view of an internal combustion engine ignition device.
4A is a cross-sectional view of the case 15 taken along the line II of FIG. 1 (first embodiment), and FIG. 4B is II- of FIG.
It is sectional drawing of the case 15 which follows the II line.

In the first embodiment described above, the bearing portions 16 and 17 are
An oil drain hole 15d for discharging the oil supplied to the rotary shaft 10 is provided vertically below the rotary shaft 10. Therefore, as shown in FIG. 4A, the opening 15f on the rotary shaft 10 side of the oil drain hole 15d of the first embodiment was vertically below the rotary shaft 10. However, in the second embodiment, as shown in FIG. 4B, the opening 15f on the rotary shaft 10 side of the oil drain hole 15d is located above the vertical bottom of the rotary shaft 10 and on the rotary shaft 10. It is provided between vertically below the rotating shaft 10 in the rotating direction and an opening 15g of the oil supply hole 15b on the rotating shaft 10 side. Specifically, the oil drain hole 15d is
It is opened at a position that is advanced by a predetermined angle θ (for example, 60 ° ± 15 °) in the rotation direction of the rotating shaft 10 from below the rotating shaft 10 in the vertical direction.

As described above, by providing the oil drain hole 15d, a part of the oil supplied from the oil supply hole 15b is reliably held between the bearing portions 16 and 17.
Therefore, even if a radial load is applied to the bearing portions 16 and 17, an oil film is easily formed on the sliding surfaces of the bearing portions 16 and 17, and as a result, the life of the bearing portions 16 and 17 can be extended.

This effect is shown in FIG. 5A shows the amount of wear of the bearing portion 16 when the oil drain hole 15d is provided vertically below the rotary shaft 10, and FIG. 5B shows the oil drain hole 15d below the rotary shaft 10 vertically. 5 shows the amount of wear in the case of being provided at a position advanced by a predetermined angle θ from the rotation direction. In the experiment of FIG. 5, after the oil is temporarily supplied from the oil supply hole 15b, the radial load is applied to the rotary shaft 10. In addition, the amount of wear of the bearing portion 16 when the rotary shaft 10 was rotationally driven without lubrication was measured. As can be seen from this experimental result, the bearing portion 1 is provided by providing the oil drain hole 15d at a position advanced by a predetermined angle θ in the rotation direction from vertically below the rotary shaft 10.
The wear amount of No. 6 can be suppressed to a very small amount.

Further, in the second embodiment, the bearing portion 16 which is the sliding bearing on the side closer to the drive gear 2 corresponding to the rotary drive is more than the bearing portion 17 which is the sliding bearing on the side far from the drive gear 2. A material with excellent wear resistance is used. Specifically, the bearing portion 16 is formed of a material having a lower frictional resistance and a higher hardness than the bearing portion 17. Further, although the bearing portion 17 has no groove for guiding oil to the sliding surface, the bearing portion 16 has a groove for guiding oil to the sliding surface. Further, the bearing portion 17 is not crowned, but the bearing portion 16 is crowned.

The bearing portion 16 on the side closer to the drive gear 2 is
Since a larger radial load is applied to the bearing portion 17 on the far side, the bearing portion 16 having a higher wear resistance than the bearing portion 17 can be used to make the wear rates of the bearing portion 16 and the bearing portion 17 uniform. It is possible to prevent the replacement time of the unit U from being accelerated due to uneven consumption.

Further, in the second embodiment, the two thrust washers 13a provided in the first embodiment are eliminated. As described above, by eliminating the thrust washer 13a, the frictional heat between the spline gear 13 and the bearing portion 16 is suppressed, and the temperature rise between the spline gear 13 and the bearing portion 16 can be suppressed.

[Modification] In the above embodiment, the rotary shaft 10 is used.
Although the example in which the slide bearings are used as the bearing portions 16 and 17 is shown, a rolling bearing such as a roller bearing or a ball bearing may be adopted. In the above-described embodiment, the oil drain hole 15d is formed at a predetermined angle θ from below the rotary shaft 10 in the vertical direction.
Although an example of providing it at the advanced position is shown, as shown in FIG.
The oil drain hole 15d may be provided at a position where the oil return hole 15d is returned by a predetermined angle .theta.

[Brief description of drawings]

FIG. 1 is a sectional view of an internal combustion engine ignition device (first embodiment).

FIG. 2 is a front view of the engine with a gear cover removed.

FIG. 3 is a sectional view of an internal combustion engine ignition device (second embodiment).

FIG. 4 is a cross-sectional view of a case.

FIG. 5 is a graph showing the amount of wear of a bearing portion that supports a rotating shaft.

FIG. 6 is a cross-sectional view of a case (modification).

FIG. 7 is a cross-sectional view of an internal combustion engine ignition device (prior art).

[Explanation of symbols]

1 Distributor 2 Drive Gear (Rotation Driving Body) 9 Shaft 10 Rotating Shafts 11 and 12 Shaft Bearing 14 Universal Joint 15 Discases 15b and 15c Oil Supply Holes 15d and 15e Oil Draining Hole 15f Opening of Oil Draining Hole on Rotating Shaft Side Part 15g opening part on the rotary shaft side of the oil supply hole 16 bearing part of the rotary shaft (sliding bearing close to the rotary drive unit) 17 bearing part of the rotary shaft (sliding bearing far from the rotary drive unit) U Rotating after removing radial load A unit that conveys only power

─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Eiji Ito 1 Toyota Town, Toyota City, Aichi Prefecture, Toyota Motor Corporation (72) Inventor Masafumi Takeda 1 Toyota Town, Aichi Prefecture, Toyota Motor Corporation ( 72) Inventor Yuji Ito 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Co., Ltd. (72) Inventor Yuji Matsubara 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Co., Ltd. (56) References 53 -35325 (JP, U) Actually open 60-36580 (JP, U) Actually open 3-65813 (JP, U) Actually open 59-184311 (JP, U) Actually open 1-108303 (JP, U) ) (58) Fields investigated (Int.Cl. ⁷ , DB name) F02P 7/10

Claims (7)

(57) [Claims] 1. An internal combustion engine igniter in which a rotary drive that rotates under a radial load rotates a shaft of a distributor for generating an ignition signal, wherein rotation of the rotary drive is fixed to the distributor. An ignition device for an internal combustion engine, wherein the ignition device is transmitted to the shaft via a rotary shaft rotatably supported by the disk case. 2. The ignition device for an internal combustion engine according to claim 1, wherein the disk case includes an oil supply hole for supplying oil to each of a bearing portion of the rotating shaft and a bearing portion of the shaft, and the rotating shaft. An ignition device for an internal combustion engine, comprising: an oil drain hole for discharging oil supplied to each of the bearing portion and the shaft bearing portion. 3. The ignition device for an internal combustion engine according to claim 2, wherein the opening of the oil drain hole on the rotary shaft side is provided above the vertical bottom of the rotary shaft. Ignition device. 4. The ignition device for an internal combustion engine according to claim 3, wherein the opening of the oil drain hole on the rotary shaft side extends from vertically below the rotary shaft in a rotation direction of the rotary shaft to the oil supply hole. An ignition device for an internal combustion engine, wherein the ignition device is provided up to an opening on the side of the rotating shaft. 5. The ignition device for an internal combustion engine according to claim 1, wherein a diameter of the rotary shaft is larger than a diameter of the shaft. 6. The ignition device for an internal combustion engine according to claim 1, wherein a bearing portion that supports the rotary shaft is a slide bearing, and a clearance is provided between the slide bearing and the rotary shaft. Furthermore, the ignition device for an internal combustion engine, wherein the rotating shaft and the shaft are connected via a universal joint. 7. The ignition device for an internal combustion engine according to claim 6, wherein the bearing portion that supports the rotary shaft comprises a plurality of slide bearings arranged in an axial direction, and the slide bearing near the rotary drive body is the rotary bearing. An ignition device for an internal combustion engine, characterized in that a bearing having excellent wear resistance is applied to the slide bearing farther from the driving body.