JPH07139327A - Cam shaft in engine with valve timing controller - Google Patents

Abstract

PURPOSE:To sufficiently supply lubricating oil to a cam shaft journal large load. CONSTITUTION:A pulley 10 and a cam shaft 1 are connected to each other by a ring gear 25 formed into a helical spline. The first and the second oil pressure chambers 26, 26 are formed in the pulley 10 by the ring gear 25. An oil pump 41 supplies lubricating oil to respective parts of an engine by pressurization according to the driving conditions of the engine. An oil control valve (OCV) regulates pressure of lubricating oil discharged from the oil pump 41. The lubricating oil discharged from the OCV 44 is supplied to the first oil pressure chamber 26 via a journal groove 6 and the first shaft oil path 28, or supplied to the second oil chamber 27 via a journal groove 7 and the second shaft oil path 30, and lubricates the first cam journal 2a so that the ring gear 25 is operated by oil pressure of the lubricating oil and relative position between the pulley 10 and the cam 3 is made to change. The lubricating oil supplied to the first and the second oil chambers 26, 27 is supplied to the second cam journal 2b, which approaches to the first cam journal 2a, so as to lubricate it.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a camshaft in an engine provided with a valve timing control device for varying the opening / closing timing of a valve when the engine is operating, and more specifically to a lubricating oil supplied to the valve timing control device. The present invention relates to a camshaft which supplies a part to a cam journal.

[0002]

2. Description of the Related Art Conventionally, as an engine equipped with a valve timing control device, for example, one disclosed in Japanese Patent Laid-Open No. 2-67407 has been proposed. In this technique, a ring gear having a helical sply on its outer circumference is provided on the outer circumference of the camshaft. Lubricating oil from the oil pump is supplied to the hydraulic chamber of the ring gear via the pressurizing passage and the hydraulic passage. And when the engine is running, by switching the solenoid valve,
Lubricating oil is supplied to the hydraulic chamber. By this supply, the ring gear receives hydraulic pressure in the axial direction of the cam shaft, and the ring gear moves in the axial direction of the cam shaft. At this time, the helical spline causes the rotational phase of the pulley and the cam shaft drivingly connected to the engine to change, and the relative position of the pulley and the cam to change. Therefore, the opening / closing timing of the valve is adjusted.

The lubricating oil from the oil pump is the first
It is supplied to the hydraulic chamber via a supply passage formed in the cam journal and the cam shaft. Therefore, the first cam journal is lubricated by the lubricating oil supplied to the hydraulic chamber.
Further, in the case of a 6-cylinder engine, the lubricating oil is supplied to the second to seventh cam journals from another route. That is,
The lubricating oil from the oil pump is supplied from the seventh cam journal to the second cam journal.

[0004]

However, when a ring gear or the like for changing the relative position between the pulley and the cam shaft is attached to the cam shaft, the weight of the cam shaft on the side where the ring gear or the like is provided is reduced. To increase. Therefore, when the cam shaft rotates, the load increases toward the cam journal on the side where the ring gear or the like is provided.

Further, the amount of lubricating oil supplied to the first cam journal is such that the lubricating oil for supplying to the hydraulic chamber is directly supplied from the oil pump, and since the supply amount is large, damage is suppressed even if the load is large. be able to. However, the second
The cam journal has the next largest load due to the weight of the ring gear and the like, but the lubricating oil is supplied in the order of the seventh and second cam journals, and is the last of the cam journals.

Therefore, since the lubricating oil corresponding to the load received by the second Kunraku journal is not supplied to the second cam journal, there is a problem that the damage received by the second cam journal becomes large.

As a countermeasure against this, it is conceivable to make the supply hole large in order to supply sufficient lubricating oil to the second cam journal, but it is difficult on the production line to make only the supply hole of the second cam journal large. There is a problem that is. Further, if the supply holes of all the cam journals are made large, there is a problem that the amount of lubricating oil in the entire valve train is increased and the loss of the oil pump is increased.

Furthermore, in order to supply sufficient lubricating oil to the second cam journal at low engine speed and high temperature, the oil pump discharge capacity must be increased considerably.

The present invention has been made in view of the above-mentioned circumstances, and an object thereof is to provide a camshaft in an engine with a valve timing control device capable of sufficiently supplying lubricating oil to a cam journal having a large load. To do.

[0010]

In order to achieve the above object, in the invention according to claim 1, a pulley provided on the outer periphery of one end of the camshaft, and first and second hydraulic chambers on the pulley are provided. A ring gear that has a spline on its inner and outer peripheral surfaces, and a helical spline is formed on at least one of the inner and outer peripheral surfaces, and that connects the pulley and the camshaft by a spline; A pressure lubricating oil supply source that pressurizes and supplies a lubricating oil for lubricating each part of the engine according to the state, and a lubrication for adjusting the oil pressure of the lubricating oil discharged from the pressure lubricating oil supply source. Supplying the oil pressure adjusting means and the lubricating oil discharged from the lubricating oil pressure adjusting means to the first or second hydraulic chamber via a first cam journal closest to the pulley side formed on the camshaft, A cam provided with first and second supply passages for lubricating the first cam journal and operating the ring gear by the hydraulic pressure of the lubricating oil to change the relative position between the pulley and the cam on the cam shaft. In the shaft, the lubricating oil supplied to the first or second supply passage is supplied to lubricate the cam journal adjacent to the first cam journal in which the first and second supply passages are formed. This is the gist.

According to the second aspect of the invention, when the camshaft is rotated by driving the pulley, the ring gear is positioned in a direction in which the ring gear moves along the axial direction of the camshaft due to the thrust force generated in the ring gear. The gist of the invention is that a lubricating oil passage for supplying the lubricating oil supplied to the hydraulic chamber to the cam journal adjacent to the first cam journal is formed.

According to the third aspect of the present invention, a pulley provided on one end of the camshaft and an outer periphery of the camshaft are arranged so that first and second hydraulic chambers are formed in the pulley, and splines are formed on the inner and outer peripheral surfaces. A ring gear having a helical spline formed on at least one side thereof and connecting the pulley and the camshaft by a spline, and a lubricating oil for lubricating each part of the engine according to the operating state of the engine. A pressurized lubricating oil supply source that pressurizes and supplies the lubricating oil, a lubricating oil pressure adjusting means for adjusting the oil pressure of the lubricating oil discharged from the pressurized lubricating oil supply source, and a lubricating oil discharged from the lubricating oil pressure adjusting means. Oil is supplied to the first or second hydraulic chamber via a first cam journal formed on a camshaft to lubricate the first cam journal, and by the hydraulic pressure of the lubricating oil. In a camshaft provided with first and second supply paths for operating a ring gear to change the relative position of the pulley and the cam on the camshaft, the camshaft is supplied to the first or second supply path. A connection supply path for supplying the lubricating oil to a cam journal adjacent to the first cam journal in which the first and second supply paths are formed,
Camshaft rotation detecting means for detecting the rotation of the camshaft, crankshaft rotation detecting means for detecting the rotation of the crankshaft, and a pulley based on the detection signals from the camshaft rotation detecting means and the crankshaft rotation detecting means A relative position for detecting the relative position with respect to the cam and controlling the lubricating oil pressure adjusting means so that the relative position is a relative position suitable for the operating state of the engine at that time and correcting the relative position between the pulley and the cam. The gist of the invention is to have the correction control means.

[0013]

According to the first aspect of the present invention, the pressurized lubricating oil supply source pressurizes and supplies the lubricating oil for lubricating each part of the engine according to the operating state of the engine. The lubricating oil pressure adjusting means adjusts the oil pressure of the lubricating oil discharged from the pressurized lubricating oil supply source. The lubricating oil whose oil pressure is adjusted by the lubricating oil pressure adjusting means is supplied to the first or second supply passage provided in the first cam journal closest to the pulley side of the camshaft. The first cam journal is lubricated by the lubricating oil supplied to the first or second supply passage. The lubricating oil supplied to the first or second supply passage is supplied to the first or second hydraulic chamber. The ring gear acts by the hydraulic pressure of the lubricating oil supplied to the first or second hydraulic chamber. The action of this ring gear changes the relative position between the pulley and the cam on the cam shaft. Further, the lubricating oil supplied to the first or second supply passage is supplied to the cam journal adjacent to the first cam journal for lubrication.

Therefore, it becomes possible to sufficiently supply the lubricating oil to the cam journal to which the next largest load is applied after the first cam journal. According to the second aspect of the invention, when the pulley and the cam shaft rotate, the helical spline generates thrust force in the ring gear. At this time, the ring gear tries to move along the axial direction of the cam shaft. Therefore, the lubricating oil is supplied to the hydraulic chamber on the side where the ring gear is about to move. This lubricating oil is supplied to the cam journal adjacent to the first cam journal via the lubricating oil passage. Then, the movement of the ring gear is blocked and the relative position between the pulley and the cam on the cam shaft is held so as not to change. Therefore, it becomes possible to sufficiently supply the lubricating oil having a high hydraulic pressure to the cam journal.

According to the third aspect of the present invention, the pressurized lubricating oil supply source pressurizes and supplies the lubricating oil for lubricating each part of the engine according to the operating state of the engine. The lubricating oil pressure adjusting means adjusts the oil pressure of the lubricating oil discharged from the pressurized lubricating oil supply source. The lubricating oil whose oil pressure is adjusted by the lubricating oil pressure adjusting means is supplied to the first or second supply passage provided in the first cam journal of the camshaft. The first cam journal is lubricated by the lubricating oil supplied to the first or second supply passage. The lubricating oil supplied to the first or second supply passage is supplied to the first or second hydraulic chamber. The ring gear acts by the hydraulic pressure of the lubricating oil supplied to the first or second hydraulic chamber. The action of this ring gear changes the relative position between the pulley and the cam on the cam shaft. Further, the lubricating oil supplied to the first or second supply passage is supplied to the cam journal adjacent to the first cam journal via the first or second connection supply passage.

Then, the relative position correction control means detects the relative position between the pulley and the cam based on the detection signals from the crankshaft rotation detection means and the camshaft rotation detection means. After that, the relative position correction control means controls the lubricating oil pressure adjusting means to correct the relative position between the pulley and the cam so that the relative positional relationship suitable for the operating state of the engine at that time is maintained.

Therefore, it becomes possible to sufficiently supply the lubricating oil to the cam journal to which the next largest load is applied after the first cam journal. Moreover, the lubricating oil supplied to the cam journal leaks from the cam journal, and the ring gear acts to maintain the relative position between the pulley and the cam of the camshaft at an appropriate relative position regardless of the change in the leakage amount. It becomes possible.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment embodying the present invention will now be described with reference to FIG.
~ It demonstrates based on FIG. FIG. 1 is a sectional view showing a valve timing control device provided on a camshaft 1 of a 6-cylinder engine, and FIG. 2 is a partial side view showing the structure of the camshaft 1. The cam shaft 1 is provided to drive an intake valve or an exhaust valve of an engine (not shown). Further, the camshaft 1 is formed with first to seventh cam journals 2a to 2g at seven locations (in the present embodiment, 2a, 2 are shown in the drawing notation).
Only b and 2g are shown).

The second to seventh cam journals 2b to 2g are also included.
Cams 3 for driving intake valves or exhaust valves are provided on the cam shafts 1 on both sides of the cam shafts 1, respectively. The first cam journal 2a is rotatably supported between the bearing portion 4a of the cylinder head 4 and the bearing cap 4b. The other second to seventh cam journals 2b to 2g have the same configuration, but the illustration of the configuration is omitted for convenience of description.

The first cam journal 2a is formed with two journal grooves 6 and 7 which form first and second supply passages extending along the outer circumference of the first cam journal 2a. Further, the cylinder head 4 is formed with a first head oil passage 8 and a second head oil passage 9 for supplying lubricating oil to the respective journal grooves 6, 7 and the first cam journal 2a.

Further, in this embodiment, an oil pump 41 as a pressurized lubricating oil supply source, an oil pan 42, an oil filter 43, a valve operating mechanism, a crank mechanism and the like constitute an engine lubricating system. That is, the first head oil passage 8
And one end of the second head oil passage 9 has an oil control valve (hereinafter, referred to as an electromagnetic control type lubricating oil pressure adjusting means).
This OCV44 is connected to the OCV44
Is an oil filter 43, an oil pump 41, and
It is connected to the oil pan 42 via an oil strainer 45. The oil pump 41 is drivingly connected to the engine and pumps and discharges lubricating oil in conjunction with the operation of the engine.

Then, by driving the oil pump 41, the lubricating oil is sucked up from the oil pan 42 through the oil strainer 45. After the lubricating oil has passed through the oil filter 43, it is supplied to the head oil passages 8 and 9 with a predetermined pressure by the operation of the OCV 44 and then to the journal grooves 6 and 7 and the first cam journal 2a. Has become. Here, the supply of the lubricating oil to the first and second head oil passages 8 and 9 can be arbitrarily adjusted by the OCV 44. The detailed configuration of the OCV 44 will be described later.

The oil filter 43 and the OCV 44 are also provided.
A main oil passage 46 is formed in a branched manner between and, and the oil passage 46 communicates with a valve mechanism, a crank mechanism, and the like.

Next, a mechanism for adjusting the valve timing will be described. At the tip of the camshaft 1,
A timing pulley housing 10 that constitutes a pulley is provided. The timing pulley housing 10 includes a pulley body 11, a cover 1 assembled to cover one side surface of the pulley body 11 and a tip portion of the camshaft 1.
2 and.

The pulley body 11 has a substantially circular plate shape, a plurality of outer teeth 13 formed on the outer periphery thereof, and a boss 14 formed at the center thereof. The pulley body 11 is mounted by the boss 14 so as to be rotatable relative to the cam shaft 1. Further, a timing belt 15 is attached to the outer teeth 13, and the timing pulley housing 10 is drive-connected via the belt 15 to a crank shaft (not shown) of the engine.

On the other hand, the cover 12 has a cylindrical shape with a bottom, a flange 16 is formed on the outer periphery thereof, and a communication hole 17 is formed in the center of the bottom. Also, on the inner circumference of the cover 12,
A plurality of inner teeth 12a are formed. The cover 12 is fixed to one side surface of the pulley body 11 by a plurality of bolts 18 and pins 19 at its flange 16. A lid 20 is detachably attached to the communication hole 17.
The space surrounded by the pulley body 11 and the cover 12 serves as a housing space 21 formed inside the timing pulley housing 10.

In this housing space 21, at the tip of the camshaft 1, a cylindrical inner cap 22 having a bottom is fastened by a hollow bolt 23, and a pin 24 is provided.
It has been stopped by. The peripheral wall 22a of the inner cap 22 is mounted so as to include the boss 14 of the pulley body 11, and the two 11 and 22 are relatively rotatable. Further, a plurality of outer teeth 22b are formed on the outer periphery of the peripheral wall 22a of the inner cap 22.

A ring gear 25 is arranged between the timing pulley housing 10 and the cam shaft 1, and the ring gear 25 connects the two 10, 10. That is, the ring gear 25 is formed in an annular shape, and the camshaft 1 is accommodated in the accommodation space 21 of the timing pulley housing 10.
It is housed so as to be able to reciprocate along the axial direction. This ring gear 25 has a plurality of teeth 25 provided on its inner and outer circumferences.
Both a and 25b have helical teeth, and can move relative to the camshaft 1 by moving in the axial direction. The teeth 25a on the inner circumference of the ring gear 25 mesh with the outer teeth 22b of the inner cap 22, and the teeth 25b on the outer circumference of the ring gear 25 mesh with the inner teeth 12a of the cover 12.

Therefore, the timing pulley housing 10
Is rotationally driven, the timing pulley housing 10 and the inner cap 22 connected by the ring gear 25 are integrally rotated, and the camshaft 1 is also rotationally driven integrally with the timing pulley housing 10. When the ring gear 25 rotates, the ring gear 2
5. A plurality of teeth 25, which are helical teeth provided on the inner and outer circumferences of 5,
Thrust force is generated in the ring gear 25 by the a and 25b, the outer teeth 22b of the inner cap 22 and the inner teeth 12a of the cover 12. In this embodiment, the ring gear 25
Receives a thrust force in a direction away from the pulley body 11.

In the accommodation space 21, a first hydraulic chamber 26 is formed between one axial end of the ring gear 25 and the bottom wall of the cover 12. Similarly, in the accommodation space 21, a second hydraulic chamber 27 is formed between the other axial end of the ring gear 25 and the pulley body 11.

Here, in order to supply the lubricating oil to the first hydraulic chamber 26, the camshaft 1 is provided with a first shaft oil as a connecting supply passage which constitutes a first supply passage extending along the center of the camshaft 1. A path 28 is formed. This shaft oil passage 2
The tip side of 8 is communicated with the first hydraulic chamber 26 through the central hole 23a of the hollow bolt 23. The shaft oil passage 28 has an oil hole 29 extending in the radial direction of the camshaft 1.
Through to the journal groove 6.

On the other hand, in order to supply the hydraulic pressure by the lubricating oil to the second hydraulic chamber 27, the camshaft 1 has a second supply passage extending in parallel with the first shaft oil passage 28.
Shaft oil passage 30 is formed. Further, one peripheral groove 31 extending along the outer periphery of the cam shaft 1 is formed near the tip of the cam shaft 1. A part of the circumferential groove 31 communicates with the second shaft oil passage 30.

Further, an oil hole 32 is formed in a part of the boss 14 of the pulley body 11 so that the circumferential groove 31 and the second hydraulic chamber 27 communicate with each other. Also, the second shaft oil passage 3
The base end side of 0 is communicated with the other journal groove 7.
In addition, in the second hydraulic chamber 27, a spring 33 is interposed between the ring gear 25 and the pulley body 11 to urge the ring gear 25 to return to the initial position (retard side in FIG. 1). Has been done.

Then, as shown in FIG. 3, the OCV 44 supplies the lubricating oil to the first head oil passage 8 and opens the second head oil passage 9 to the drain 47, so that the oil pressure is changed. Journal groove 6, oil hole 29, first
Shaft oil passage 28 and the central hole 23a of the hollow bolt 23
Is supplied to the first hydraulic chamber 26 through. By applying this hydraulic pressure to one end of the ring gear 25, the ring gear 25 causes the urging force of the spring 33 and the second hydraulic chamber 27.
It rotates while being moved in the axial direction against the lubricating oil inside.

Therefore, the camshaft 1 is twisted. As a result, the relative position of the camshaft 1 and the timing pulley housing 10 in the rotational direction is changed, and the differential timing of the intake valve or the exhaust valve is advanced. Therefore, when the hydraulic pressure is applied to the first hydraulic chamber 26, the ring gear 25
3, the stroke end is moved to a position close to the pulley main body 11 as shown in FIG. 3, and the stroke end is the position on the maximum advance side.

On the other hand, as shown in FIG. 4, while the OCV 44 supplies the lubricating oil to the second head oil passage 9,
By opening the first head oil passage 8 to the first drain 47, its oil pressure is transferred to the second oil pressure chamber 27 through the journal groove 7, the second shaft oil passage 30, the circumferential groove 31, and the oil hole 32. Supplied. By applying this hydraulic pressure to the other end of the ring gear 25, the ring gear 25 is rotated while being axially moved against the oil in the first hydraulic chamber 26, and the cam shaft 1 is twisted in the opposite direction. A twist is added.

As a result, the relative position of the camshaft 1 and the timing pulley housing 10 in the rotational direction is changed, and the operation timing of the intake valve or the exhaust valve is retarded. Therefore, the second hydraulic chamber 27
By applying hydraulic pressure to the ring gear 25, as a stroke end, the ring gear 25 is moved to a position close to the cover 12, and the stroke end becomes a position on the maximum retard side.

In the present embodiment, the supply of the lubricating oil to both head oil passages 8 and 9 is stopped by the OCV 44 to return to the stroke end on the maximum retard side,
The state is the same as that shown in FIG.
Further, in this embodiment, the OCV 44 is used for the first hydraulic chamber 26.
It is also possible to move the ring gear 25 in the axial direction and hold it at an arbitrary position by adjusting the balance of the hydraulic pressures supplied to the second hydraulic chamber 27.

In this case, when the ring gear 25 rotates,
The ring gear 25 is moved by the thrust force into the first hydraulic chamber 26.
Side to side along the axial direction of the camshaft 1. Then, the relative position with respect to the timing pulley housing 10 adapted to the operating state of the engine at that time cannot be accurately maintained. Therefore, from OCV44 to the first
Lubricating oil is supplied to the head oil passage 8 of the first hydraulic chamber 2
Lubricating oil is supplied to 6 to apply hydraulic pressure to one end of the ring gear 25, and the ring gear 25 is held so as not to move to the stroke end on the first hydraulic chamber 26 side by the thrust force.

Further, the ring gear 25 and the inner cap 22
A sealing surface 34 is provided between the and. And
Between the ring gear 25 and the cover 12, the ring gear 2
A seal ring 35, which is assembled to the outer peripheral surface of No. 5, is interposed. With this configuration, the first hydraulic chamber 26 and the second hydraulic chamber 27 are separated from each other as separate spaces, and are in a dead-end state. Therefore, each hydraulic chamber 2
In and out of the lubricating oil to and from the oil passages 6, 27
9, 28, 30 etc. will be performed through separate and independent circuits.

The OCV 44 is driven and controlled by the ECU 71 as a relative position correction control means. ECU
At the input side of 71, a rotation speed sensor 81 for detecting the engine speed and whether or not the engine has been started, and a cam angle sensor 8 as a camshaft rotation detecting means for detecting the cam angle.
2. Crank angle sensor 83 as crankshaft rotation detecting means for detecting crank angle, throttle sensor 84 for detecting throttle valve opening, water temperature sensor 85 for detecting cooling water temperature, air flow meter for detecting intake air amount 86 etc. are connected.

An OCV 44 is connected to the output side of the ECU 71. Then, the ECU 71 determines the operating state of the engine at that time based on the detection signals from the various sensors 81 to 86, and outputs a control signal for driving the OCV 44. And EC
U71 indexes the relative position between the timing pulley housing 10 and the cam 3 that is suitable for the engine operating condition at that time, and drives the OCV 44 to reach that relative position. Then, the ECU 71 controls the valve timing mechanism provided on the camshaft 1 by driving the OCV 44.

The first shaft oil passage 28 formed in the camshaft 1 is connected to the lubricating oil supply hole 50 formed in the second cam journal 2b. Further, the first shaft oil passage 28 has a third shaft oil passage 51 having a smaller diameter than the first shaft oil passage 28 on the other end side of the camshaft 1, and the third shaft oil passage 51 is formed. Is communicated with the first shaft oil passage 28. Further, a bearing 55 is inserted in the first shaft oil passage 28 and arranged at the boundary between the first shaft oil passage 28 and the third shaft oil passage 51. The bearing 55 divides the first shaft oil passage 28 and the third shaft oil passage 51,
Independent oil passages are formed.

Further, the third shaft oil passage 51 communicates with the lubricating oil supply hole 50 formed in each of the third to sixth cam journals 2c to 2f and the journal groove 56 of the seventh cam journal 2g. For convenience of explanation, only the journal groove 56 formed in the seventh cam journal 2g is shown). The lubricating oil branched and supplied from the main oil passage 46 is supplied to the journal groove 56 of the seventh cam journal 2g. The lubricating oil supplied to the journal groove 56 of the seventh cam journal 2g is passed through the third shaft oil passage 51 to the third to sixth cam journals 2.
c to 2f, respectively.

Next, the operation of the present embodiment constructed as described above will be described. First, when the engine is stopped, as shown in FIG. 1, the ring gear 25 is held at the stroke end position on the maximum retard side by the urging force of the spring 33.

When the engine operates in this state, the pulley body 11, the timing pulley housing 10, the ring gear 25 and the cam shaft 1 rotate via the timing belt 15.

The ECU 71 also determines the operating state of the engine at that time based on the detection signals from the various sensors 81 to 86. Then, the timing pulley housing 10 and the cam 3 suitable for the engine operating condition at that time
The relative position with and is indexed, and OC is set to be the relative position.
Control V44.

In this case, the ECU 71 controls the OCV 44 to adjust the oil pressure of the lubricating oil from the oil pump 41, and the first oil pressure chamber 26 through the first head oil passage 8 and the first shaft oil passage 28. Supply lubricating oil to. On the other hand, the ECU 71
Controls the OCV 44 to connect the second head oil passage 9 to the drain 47, so that the lubricating oil in the second hydraulic chamber 27 is drained through the second shaft oil passage 30 and the second head oil passage 9
Discharge to 7.

Therefore, the ring gear 25 moves to the second hydraulic chamber 27 side, that is, the advance side while resisting the urging force of the spring 33 by the hydraulic pressure of the lubricating oil supplied to the first hydraulic chamber 26. Due to the movement of the ring gear 25, the timing pulley housing 10 and the cam shaft 1 relatively rotate, the relative position of the timing pulley housing 10 and the cam 3 is changed, and the operation timing of the intake valve or the exhaust valve is advanced. Will be.

The lubricating oil supplied from the first head oil passage 8 to the first shaft oil passage 28 is also sufficiently supplied to the lubricating oil supply hole 50 of the second cam journal 2b. Further, the ECU 71 determines whether the relative position between the timing pulley housing 10 and the cam 3 is a relative position suitable for the operating state of the engine at that time based on the detection signals from the cam angle sensor 82 and the crank angle sensor 83. To judge.

Then, the timing pulley housing 10
If the relative position between the cam 3 and the cam 3 is not suitable for the engine operating condition at that time, the ECU 71 controls the OCV 44 to move the ring gear 25, and the relative position between the timing pulley housing 10 and the cam 3 is adjusted to a suitable position. Correct to.

Further, for example, when the ECU 71 determines that it is appropriate that the ring gear 25 is located substantially in the middle of the accommodation space 21 based on the operating state of the engine, the ECU 7
1 controls the OCV 44 to accommodate the ring gear 25 in the space 2
It is controlled so as to be positioned approximately in the middle of 1. At this time, the ring gear 25 is rotated by the thrust force and the spring 33.
The urging force of the cam shaft 1 tends to move to the first hydraulic chamber 26, that is, the stroke end on the retard side, along the axis of the camshaft 1. Then, it becomes impossible to position the ring gear 25 substantially in the center of the accommodation space 21.

Therefore, the ECU 71 uses the cam angle sensor 82.
Also, the relative position between the timing pulley housing 10 and the cam 3 is indexed based on the detection signal from the crank angle sensor 83, and the OCV 44 is controlled so that the ring gear 25 is located at substantially the center of the housing space 21. That is, a hydraulic pressure higher than that of the second hydraulic chamber 27 is applied to the first hydraulic chamber 26 via the first head oil passage 8 and the first shaft oil passage 28 so that the ring gear 25 does not move to the retard side. Block to.

Therefore, the ECU 71 controls so that the ring gear 25 is always positioned substantially in the center of the accommodation space 21.
Therefore, when the valve timing control is performed, a hydraulic pressure higher than that of the second hydraulic chamber 26 is constantly applied to the first hydraulic chamber 26 so that the ring gear 25 does not move to the retard side. This high oil pressure can be supplied to the lubricating oil supply hole 50 of the second cam journal 2b, and sufficient supply can be performed.

As a result, the first and second cam journals 2
Even if a large load is applied to the a and 2b by the variable valve timing mechanism, the lubricating oil can be sufficiently supplied, so that damage to the first and second cam journals 2a and 2b can be reduced.

Further, the first and second cam journals 2a, 2
The oil pressure of the lubricating oil supplied to b is adjusted by the OCV 44. As a result, the first and second cam journals 2
It is possible to supply an appropriate lubricating oil to a and 2b and apply an appropriate hydraulic pressure.

Furthermore, the first and second cam journals 2a,
The lubricating oil supplied to 2b will leak. Therefore, the first
When the amount of leakage of the lubricating oil from the second cam journals 2a and 2b changes, an appropriate amount of the lubricating oil is supplied to the first or second
Even if the hydraulic pressure is supplied to the hydraulic chambers 26 and 27, it may not be possible to position the timing pulley housing 10 and the cam 3 at a relative position suitable for the operating state of the engine at that time.

In the present embodiment, the ECU 7 is based on the detection signals of the cam angle sensor 82 and the crank angle sensor 83.
1 determines whether the relative position between the timing pulley housing 10 and the cam 3 is a relative position suitable for the operating state of the engine at that time. Then, the OCV 44 is adjusted so that the relative position is suitable for the engine operating condition at that time.
Is controlled to correct the position of the ring gear 25. As a result, appropriate valve timing control can be performed even if the amount of leakage of lubricating oil from the first and second cam journals 2a and 2b changes.

In the present embodiment, the lubricating oil supplied to the first hydraulic chamber 26 is supplied to the lubricating oil supply hole 50 of the second cam journal 2b, but it is supplied to the second hydraulic chamber 27. The lubricating oil may be supplied to the lubricating oil supply hole 50 of the second cam journal 2b.

In this embodiment, since the ring gear 25 moves to the first hydraulic chamber 26 side by the thrust force,
In order to prevent this, the oil is supplied to the first hydraulic chamber 26, and this lubricating oil is supplied to the lubricating oil supply hole 50 of the second cam journal 2b.

On the contrary, when the ring gear 25 is configured to move to the second hydraulic chamber 27 side by the thrust force, the lubricating oil is supplied to the second hydraulic chamber 26 in order to prevent this. Need to be configured. In this case, the lubricating oil supplied to the second hydraulic chamber 27 is supplied to the second cam journal 2
You may comprise so that it may supply to the lubricating oil supply hole 50 of b. As a result, lubricating oil having a high hydraulic pressure can be supplied to the second cam journal 2b, and sufficient lubrication can be performed.

Further, in the present embodiment, the first shaft oil passage 28 and the third shaft oil passage 51 are set in a penetrating state, and the bearing 55 is used to make the first shaft oil passage 28 and the third shaft oil passage 51. And are configured as independent oil passages. Alternatively, the first shaft oil passage 28 and the third shaft oil passage 51 may be independently formed in the shaft 1.

In this embodiment, the lubricating oil supplied from the OCV 44 is supplied only to the second cam journal 2b. In addition to this, the load is the third cam journal 2c.
If it takes a lot of time, it is possible to supply the lubricating oil from the OCV 44 to the third cam journal 2c if necessary.

Further, when the third shaft oil passage 51 is formed from the other end side of the camshaft 1, conventionally, a guide hole which is the same as the third shaft oil passage 51 is formed from one end side of the camshaft 1. From the other end of the camshaft 1
The shaft oil passage 51 is formed so as to communicate with the guide hole. Then, the guide hole is further processed to form the first shaft oil passage 28. In this case, processing is performed 3 times.

However, in this another example, the first shaft oil passage 28 is formed from one end side of the camshaft 1, and the third shaft oil passage 51 is formed from the other end side of the camshaft 1 so that they communicate with each other. It may be formed as follows. As a result, the first and third shaft oil passages 2 of the camshaft 1
The process of forming 8, 51 can be simplified.

[0066]

As described in detail above, according to the present invention, there is an excellent effect that the lubricating oil can be sufficiently supplied to the crank journal having a large load.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram showing a valve timing control device in an embodiment embodying the present invention.

FIG. 2 is a partially cutaway side view showing a structure of a camshaft according to the present invention.

FIG. 3 is an operation diagram showing that the ring gear has moved to an advance side.

FIG. 4 is an operation diagram showing that the ring gear has moved to a retard side.

[Explanation of symbols]

1 ... Cam shaft, 2a ... First cam journal, 2b ...
Cam journal, 6 ... journal groove forming first supply path, 7 ... journal groove forming second supply path, 10
... Timing pulley housing that constitutes a pulley, 25
... ring gear, 26 ... first hydraulic chamber, 27 ... second hydraulic chamber, 28 ... first shaft oil passage as connecting supply passage constituting first supply passage, 30 ... second supply passage A second shaft oil passage which is configured, 41 ... an oil pump as a pressurized lubricating oil supply source, 44 ... an OCV as a lubricating oil pressure adjusting means,
71 ... ECU as relative position correction control means, 82 ... Cam angle sensor as camshaft rotation detection means, 83 ...
Crank angle sensor as crankshaft rotation detecting means

Claims (3)

[Claims] 1. A pulley provided on an outer periphery of one end of a camshaft, a pulley arranged to form first and second hydraulic chambers in the pulley, and a spline on inner and outer peripheral surfaces, and at least A helical spline is formed on one side of the ring gear, and a ring gear that connects the pulley and the camshaft by a spline and a lubricating oil for lubricating each part of the engine are pressurized and supplied according to the operating state of the engine. A pressure lubricating oil supply source, a lubricating oil pressure adjusting means for adjusting the oil pressure of the lubricating oil discharged from the pressurized lubricating oil supply source, and a lubricating oil discharged from the lubricating oil pressure adjusting means are formed on a camshaft. The first cam journal closest to the pulley side is supplied to the first or second hydraulic chamber to lubricate the first cam journal, and the hydraulic pressure of the lubricating oil causes the phosphorus to flow. A camshaft provided with first and second supply paths for operating a gear to change the relative position of the pulley and the cam of the camshaft, wherein the first and second supply paths are formed. A camshaft in an engine with a valve timing control device, characterized in that the lubricating oil supplied to the first or second supply passage is supplied to a cam journal adjacent to one cam journal for lubrication. 2. When the cam shaft is rotated by driving the pulley, the thrust force generated in the ring gear supplies the ring gear to a hydraulic chamber located in a direction in which the ring gear moves along the axial direction of the cam shaft. Lubricating oil first
The camshaft in an engine with a valve timing control device according to claim 1, wherein a lubricating oil passage for supplying the cam journal adjacent to the cam journal is formed. 3. A pulley provided on the outer circumference of one end of the camshaft, and a pulley arranged to form first and second hydraulic chambers in the pulley, and having a spline on the inner and outer peripheral surfaces, and at least A helical spline is formed on one side of the ring gear, and a ring gear that connects the pulley and the camshaft by a spline and a lubricating oil for lubricating each part of the engine are pressurized and supplied according to the operating state of the engine. A pressure lubricating oil supply source, a lubricating oil pressure adjusting means for adjusting the oil pressure of the lubricating oil discharged from the pressurized lubricating oil supply source, and a lubricating oil discharged from the lubricating oil pressure adjusting means are formed on a camshaft. The first through the first cam journal
Alternatively, the first and second hydraulic pressure chambers may be supplied to lubricate the first cam journal and to cause the ring gear to act by the hydraulic pressure of the lubricating oil to change the relative position between the pulley and the cam on the camshaft. In a camshaft having a second supply passage, the lubricating oil supplied to the first or second supply passage is supplied to the first supply passage.
And a connection supply path for supplying the cam journal adjacent to the first cam journal in which the second supply path is formed, a camshaft rotation detecting means for detecting rotation of the camshaft, and a crank for detecting rotation of the crankshaft. The relative position between the pulley and the cam is detected based on the detection signals from the shaft rotation detecting means and the camshaft rotation detecting means and the crankshaft rotation detecting means, and the relative position is suitable for the engine operating condition at that time. A camshaft in an engine with a valve timing control device, comprising: relative position correction control means for correcting the relative position between the pulley and the cam by controlling the lubricating oil pressure adjusting means to be in a relative position.