JPH1030418A - Oil supply device for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce an oil leak amount and prevent hydraulic control from delaying by setting a wound position of an interlocking band of a rotor to be overlapped with an end journal. SOLUTION: A timing pulley 29 as a rotor is fixed rotatably and integrally to an end of an exhaust side cam shaft 3 through a pin 30 and bolt 31. A timing belt 32 as an interlocking band interlocked with a crankshaft is wound around the timing pulley. A wound position of the timing belt 32 to the timing pulley 29 is set to a position of a running line 33 of the timing belt 32 overlapped with an end journal 5. Thus, an oil leak amount in the end journal can be reduced to prevent hydraulic control from delaying.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a gasoline engine,
For oil supply devices for internal combustion engines such as diesel engines,
More specifically, the present invention relates to an oil supply device for an internal combustion engine in which an end journal of a camshaft and a supply passage for hydraulic pressure exist in the camshaft.

[0002]

2. Description of the Related Art There is a hydraulic valve timing control device using this type of oil supply device. For example,
Japanese Patent Laying-Open No. 7-229408 discloses a valve timing control device shown in FIG. In this device,
A variable valve timing mechanism (VVT) 81 is provided at one end of the camshaft 82 and operates to change the valve timing of the intake valve. The camshaft 82 is rotatably supported by a journal 83 and the camshaft 82
Are formed with first and second shaft passages 84 and 85. First and second oil passages 8 communicating with an oil control valve (OCV) not shown in the journal 83.
3a and 83b are formed. Annular grooves 86a and 86b are formed on the outer peripheral surface of the camshaft 82, the first shaft passage 84 is formed in the first oil passage 83a through the annular groove 86a and the communication hole 87, and the second shaft passage 85 is formed in an annular shape. Groove 8
Each of the second oil passages 83b communicates with the corresponding second oil passage 83b via the corresponding one of the oil passages 6b.

A pulley 88 is rotatably supported on the camshaft 82, and a pulley housing 89 for forming an accommodation space is fixed to the pulley 88 so as to be integrally rotatable. An inner cap 90 is fixed to an end of the camshaft 82 by a hollow bolt 91. A ring gear 92 is provided between the pulley housing 89 and the inner cap 90.
Are interposed movably in the axial direction of the camshaft 82, and divide the accommodation space into a first hydraulic chamber 93 and a second hydraulic chamber 94. The first hydraulic chamber 93 communicates with the first shaft passage 84 via a hollow bolt 91, and the second hydraulic chamber 85
Is communicated with the second shaft passage 85 through an annular groove 95 formed in the camshaft 82 and a hole 88a formed in the pulley 88.

Helical teeth meshing with the helical teeth formed on the inner periphery of the pulley housing 89 are provided on the outer periphery of the ring gear 92, and helical teeth meshing with the helical teeth formed on the outer periphery of the inner cap 90 are provided on the inner periphery. Is formed. The rotation of the crankshaft (not shown) is transmitted to the pulley 88 via the timing belt 96, and the rotation of the pulley 88 is transmitted to the camshaft 82 via the ring gear 92 and the like.

When hydraulic oil is supplied from the first shaft passage 84 to the first hydraulic chamber 93, the ring gear 92 moves to the right in FIG. 9 and operates from the second shaft passage 85 to the second hydraulic chamber 94. When oil is supplied, the ring gear 92 moves to the left in FIG. Then, the supply oil passage 83a,
The supply of hydraulic oil to the shaft 83b is controlled, the ring gear 92 is moved in the axial direction of the camshaft 82, and the camshaft 8
2 rotates relatively to the pulley 88, and the opening / closing timing of the intake valve is controlled.

[0006]

However, in the conventional apparatus constructed as described above, the position of the pulley 88 around which the timing belt 96 for transmitting the rotation of the crankshaft is wound is determined by the position of the hydraulic supply path to the VVT 81. The cam 83 is biased toward the end of the camshaft 82 from the journal 83 and is in a cantilever state. When the pulley 88 is in a cantilever state, the camshaft 82 is bent by the tension of the timing belt 96. Therefore, the clearance between the camshaft 82 and the journal 83 needs to be set to a certain value or more so that the camshaft 82 does not seize even when the camshaft 82 is bent, and leakage of hydraulic oil from the clearance increases, and the VVT 81 Responsiveness during control deteriorates.
If the capacity of the oil pump is increased, there is no problem even if there is a leak of hydraulic oil, but there is a problem that the oil pump becomes larger and fuel efficiency deteriorates.

When the position of the camshaft 82 is displaced due to the bending of the camshaft 82, a part of the clearance between the camshaft 82 and the journal 83 becomes large, and the hydraulic oil is easily leaked. Further, the journal 83 is elastically deformed as shown in FIG.
As a result, the clearance between the camshaft 82 and the journal 83 increases, the leakage of hydraulic oil from the clearance increases, and the responsiveness during control of the VVT 81 deteriorates.
Further, the contact pressure of the camshaft 82 with respect to the journal 83 increases, and the contact portion is easily worn.

A similar problem arises not only in the case of the VVT but also in the case where the end journal and the camshaft are used in the supply path of the hydraulic oil to the actuator operated by the hydraulic control.

SUMMARY OF THE INVENTION The present invention has been made in consideration of the above-described problems, and has as its object to reduce the amount of oil leakage at an end journal serving as a supply oil passage and to prevent a delay in hydraulic control. It is an object of the present invention to provide an oil supply device for an internal combustion engine that can be used.

[0010]

In order to achieve the above object, according to the first aspect of the present invention, there is provided a camshaft supported by a plurality of journals, and an end journal located at an end of the camshaft. A rotating body connected to a camshaft at a position outside the end journal, an interlocking band wound around the rotating body and interlocking with a crankshaft, and an inner peripheral surface of the end journal or an outer periphery of the camshaft. A first oil passage provided on the surface, a camshaft internal passage provided inside the camshaft,
A second oil passage provided in a camshaft journal corresponding to the end journal so as to communicate the first oil passage and a camshaft internal passage, wherein the first oil passage and the camshaft are provided. In an oil supply device for an internal combustion engine in which one of the internal passages communicates with an oil supply source and the other communicates with a hydraulic actuator, the winding position of the interlocking band on the rotating body overlaps with the end journal. The end journal was set in the above.

Further, in the invention according to claim 2,
A camshaft supported by a plurality of journals, an end journal located at an end of the camshaft, a rotating body connected to the camshaft, and an interlocking band wound around the rotating body and interlocked with the crankshaft A cam corresponding to the end journal so as to communicate a first oil passage provided on an inner peripheral surface of the end journal or an outer peripheral surface of the camshaft, and the first oil passage and the camshaft internal passage. An internal combustion engine having a second oil passage provided in a shaft journal portion, wherein one of the first oil passage and the camshaft internal passage communicates with an oil supply source, and the other communicates with a hydraulic actuator. In the oil supply device, the end journal may be positioned such that a winding position of the interlocking band on the rotating body is located inward of the end journal. It was set.

(Operation) According to the first aspect of the present invention,
The camshaft is supported by a plurality of journals, and hydraulic oil is supplied to the hydraulic actuator from an oil supply via an end journal located at the end of the camshaft and an oil supply passage formed in the camshaft. When the hydraulic actuator is connected to a camshaft internal passage provided inside the camshaft, the operating oil of the oil supply source is supplied to the first inner surface of the end journal or the first surface provided on the outer surface of the camshaft. The oil is supplied from the oil passage to the hydraulic actuator through a second oil passage provided in the camshaft journal and the camshaft internal passage. When the hydraulic actuator is connected to the first oil passage, the operating oil of the oil supply source is supplied from the camshaft internal passage to the hydraulic actuator via the second oil passage and the first oil passage.

[0013] Since the position of the interlocking belt linked to the crankshaft, which is wound around the rotating body connected to the camshaft, overlaps with the end journal, the camshaft is moved at a position corresponding to the end journal. No bending force acts on the journal, the deformation of the journal is prevented, and the leakage of hydraulic oil is reduced.

According to the second aspect of the invention, the supply path of the hydraulic oil is the same as that of the first aspect. Further, the position where the interlocking belt interlocking with the crankshaft is wound around the rotating body connected to the camshaft is on the inner side (inside) of the end journal. Accordingly, the bending force acting on the camshaft is borne by the end journal and other journals disposed inside the end journal.
Therefore, the deformation at the end journal is suppressed as compared with the case of the cantilever state, and the leakage amount of the hydraulic oil is reduced.

[0015]

BEST MODE FOR CARRYING OUT THE INVENTION

(First Embodiment) A first embodiment in which the present invention is embodied in a valve timing control device will be described below with reference to FIGS.

As shown in FIG. 2, a cylinder head 1 of an engine (not shown) has an intake camshaft 2 for driving an intake valve 2a and an exhaust camshaft 3 for driving an exhaust valve 3a. Are provided in parallel. Both camshafts 2 and 3 have a plurality of journals 4 and 5
(Only the end journals are shown), and each is rotatably supported.

As shown in FIGS. 1 and 2, annular grooves 6 and 7 as first oil passages extend in the inner circumferential surface of the end journal 5 supporting the exhaust camshaft 3 along the circumferential direction. Is formed. As shown in FIG. 1, a first end of the cylinder head 1 is communicated with each annular groove 6, and a second end of the cylinder head 1 is an oil control valve (hereinafter simply referred to as OCV) 8.
And an oil passage 10 whose first end is connected to each annular groove 7 and whose second end is connected to an oil control valve 8. The OCV 8 is connected via a pipe 12 to an oil pump 11 as an oil supply source. OCV8 is an electronic control unit (EC not shown)
U) is controlled according to the rotational state of the engine.

A rotary (vane type) variable valve timing mechanism (hereinafter simply referred to as VVT) 13 as a hydraulic actuator is disposed on the exhaust side camshaft 3 inside the end journal 5. As shown in FIGS. 1 and 3, the VVT 13 includes an internal rotor 15 fixed to the camshaft 3 via a lock nut 14 so as to be integrally rotatable,
A rotor housing 16 is provided so as to be rotatable relative to the internal rotor 15. Internal rotor 15
Is a cylindrical portion 15a fitted to the exhaust side camshaft 3, and a flange 15 formed on one end thereof and the end journal 5 side.
b, and a plurality (four in this embodiment) of vanes 15c protruding from the outer periphery of the cylindrical portion 15a. The rotor housing 16 has a concave portion 16a for accommodating the vane 15c,
A cylindrical portion 16b fitted to the peripheral surface of the flange 15b, and is fitted to the outer periphery of the cylindrical portion 15a of the internal rotor 15 so as to be relatively rotatable. The peripheral surface of the recess 16a is a vane 15c.
Each recess 16a is divided into two hydraulic chambers 17 and 18 by a vane 15c. The rotor housing 16 is rotated relative to the internal rotor 15 by controlling the supply of hydraulic oil to the hydraulic chambers 17 and 18.

A drive gear 19 is rotatably supported on the exhaust side camshaft 3, and is fixed to the rotor housing 16 by screws (not shown) so as to be integrally rotatable. A drive gear 19 is provided on the intake side camshaft 2.
The driven gear 20 is fixed so as to be integrally rotatable. The driven gear 20 is formed of a scissors gear. That is, the rotation of the exhaust-side camshaft 3 is transmitted to the intake-side camshaft 2 via the internal rotor 15, the rotor housing 16, the drive gear 19, and the driven gear 20.

As shown in FIGS. 1 and 2, near the end of the exhaust side camshaft 3, a first camshaft internal passage 21 is provided at the axial center portion, and a second camshaft internal passage is provided at the outer peripheral side. 22 are formed so as to extend along the longitudinal direction of the exhaust-side camshaft 3, respectively. An oil passage 23 serving as a second oil passage connecting the annular grooves 6 and 7 and the camshaft internal passages 21 and 22 is formed in a camshaft journal portion 3b corresponding to the end journal 5 of the exhaust-side camshaft 3. , 24 are respectively formed.

A communication passage 25 for communicating the first camshaft internal passage 21 with the outer peripheral surface of the exhaust-side camshaft 3 is provided at a position corresponding to the internal rotor 15 of the exhaust-side camshaft 3. A communication passage 26 for communicating the camshaft internal passage 22 with the outer peripheral surface of the exhaust-side camshaft 3 is formed. The internal rotor 15 has a communication passage 2
Annular grooves 27a and 28a are formed at positions facing the first and second hydraulic chambers 18 and 5 and 26, respectively, and the second hydraulic chamber 18 communicates with the annular groove 28a. Are formed.

A timing pulley 29 as a rotating body is provided at the end of the exhaust side camshaft 3 with a pin 30 and a bolt 31.
Are fixed so as to be integrally rotatable. A timing belt 32 as an interlocking band interlocking with a crankshaft (not shown) is wound around the timing pulley 29. The position where the timing belt 32 is wound around the timing pulley 29 is set at a position where the running line (indicated by a chain line in FIG. 1) 33 of the timing belt 32 overlaps the end journal 5.

Next, the operation of the above-configured device will be described. When the engine is driven, the rotation of the crankshaft is transmitted to the timing pulley 29 via the timing belt 32, and the exhaust camshaft 3 is rotated integrally with the timing pulley 29. Exhaust camshaft 3
Is transmitted to the intake side camshaft 2 via the VVT 13, the drive gear 19 and the driven gear 20.

When the intake camshaft 2 is advanced with respect to the crankshaft to advance the opening / closing timing of the intake valve, the OCV 8 supplies hydraulic oil to the first hydraulic chamber 17 and the second hydraulic chamber. The oil supply path is switched so that the hydraulic oil of No. 18 is collected in the oil pan.

In this state, the operating oil supplied from the oil passage 9 is supplied to the first oil passage via the annular groove 6, the oil passage 23, the first camshaft internal passage 21, the communication passage 25, the annular groove 27a and the hole 27b. Is supplied to the hydraulic chamber 17. On the other hand, the hydraulic oil in the second hydraulic chamber 18 is supplied to the hole 28b, the annular groove 28a,
6. The oil is discharged to the oil passage 10 through the second camshaft internal passage 22, the oil passage 24, and the annular groove 7, and is collected by the oil pan (not shown) through the OCV 8.

The rotor housing 16 is connected to the vane 1
The rotation of the rotor housing 16 relative to the exhaust-side camshaft 3 is changed in accordance with the magnitude of the hydraulic pressure in each of the hydraulic chambers 17 and 18 acting on 5c. The rotation phase of the intake camshaft 2 that rotates integrally with the driven gear 20 that meshes with the drive gear 19 that rotates integrally is changed, and the opening / closing timing of the intake valve is adjusted to the advance side.

On the other hand, when the intake camshaft 2 is retarded with respect to the crankshaft to delay the opening / closing timing of the intake valve, the OCV 8 supplies the hydraulic oil to the second hydraulic chamber 18 and The oil supply path is switched so that the hydraulic oil in the hydraulic chamber 17 is collected in the oil pan. In this state, the hydraulic oil supplied from the oil passage 10 is supplied to the annular groove 7, the oil passage 24, the second camshaft internal passage 22, the communication passage 26,
The oil is supplied to the second hydraulic chamber 18 through the annular groove 28a and the hole 28b. The hydraulic oil in the first hydraulic chamber 17 is supplied to the oil passage 9 via the hole 27b, the annular groove 27a, the communication passage 25, the first camshaft internal passage 21, the oil passage 23, and the annular groove 6.
To the oil pan via OCV8.

Then, the rotor housing 16 rotates relative to the internal rotor 15 in the opposite direction to the above, the rotation phase of the rotor housing 16 with respect to the exhaust side camshaft 3 is changed, and the drive is rotated integrally with the rotor housing 16. The rotation phase of the intake camshaft 2 rotating integrally with the driven gear 20 meshing with the gear 19 is changed, and the opening / closing timing of the intake valve is adjusted to the retard side.

The timing pulley 29 and the exhaust side camshaft 3 can be considered as an integral rigid body, and the force of the timing belt 32 acting on the exhaust side camshaft 3 via the timing pulley 29 is equal to the travel line 33 of the timing belt 32. It will be the corresponding position. Since the travel line 33 is located at a position overlapping the end journal 5, no bending force is applied to the exhaust camshaft 3 at the position of the end journal 5. Therefore, the end journal 5
Is prevented from being elastically deformed, and leakage of hydraulic oil from a clearance between the end journal 5 and the exhaust-side camshaft 3 is reduced.

This embodiment has the following effects. (A) The position where the interlock belt (timing belt 32) interlocking with the crankshaft is wound around the rotating body (timing pulley 29) connected to the camshaft (exhaust camshaft 3) is the end journal 5. Therefore, no bending force (bending moment) acts on the camshaft at a position corresponding to the end journal 5. Therefore, deformation of the end journal 5 in which the oil supply passage is formed is prevented, and the leakage amount of the working oil is reduced. As a result, the responsiveness of the VVT 13 is improved as compared with the conventional device without increasing the capacity of the oil pump.

(B) The annular grooves 6 and 7 are the end journals 5
Since it is formed on the camshaft side, the strength of the camshaft is greater than when the annular grooves 6 and 7 are provided on the camshaft side.

(C) Rotating body (timing pulley 29)
Is connected to the camshaft (exhaust-side camshaft 3) at a position outside the end journal 5, so that the rotating body can be attached to the camshaft while the camshaft is supported by the journal. Maintenance work becomes easier as compared with a configuration in which the camshaft is connected to a position inside the end journal 5.

(D) A rotary VVT is added to the VVT 13
Is used, so that the entire apparatus becomes compact as compared with a helical gear type VVT. (Second Embodiment) Next, a second embodiment will be described with reference to FIG. In this embodiment, a helical gear type VVT is provided instead of the rotary type VVT 13;
The point that the VVT is provided on the intake side camshaft 2 is significantly different from the above embodiment. The same parts are denoted by the same reference numerals, and detailed description is omitted.

A VVT 34 as a hydraulic actuator is provided at the tip of the intake camshaft 2, and includes a timing pulley 35, a cover 37 fixed to the timing pulley 35 by bolts 36, and a space between the cover 37 and the camshaft 2. And a ring gear 38 disposed at the center. The timing pulley 35 and the cover 37 constitute a rotating body.

The cylindrical inner gear 40 fixed at the tip of the intake side camshaft 2 by a hollow bolt 39 and a pin (not shown) has external teeth 40a on its outer periphery. The timing pulley 35 and the cover 37 are supported to be rotatable relative to the intake camshaft 2,
7 has internal teeth 37a on its inner periphery. The internal teeth 37a and the external teeth 40a are each formed of a helical spline. The annular ring gear 38 disposed between the inner gear 40 and the cover 37 has internal teeth 38a and external teeth 38b on its inner and outer circumferences. The two teeth 38a and 38b are formed of helical splines, and the inner teeth 38a are the outer teeth 40 of the inner gear 40.
a, and the external teeth 38 b mesh with the internal teeth 37 a of the cover 37. A pair of a first hydraulic chamber 41 and a second hydraulic chamber 42 are provided on both sides of the ring gear 38 in the axial direction of the intake camshaft 2 inside the cover 37.

Annular grooves 6 and 7 are formed on the outer peripheral surface of the intake side camshaft 2 at positions facing the ends of the oil passages 9 and 10, respectively. The first camshaft internal passage 21 formed in the axial center of the intake-side camshaft 2 communicates with the first hydraulic chamber 41 through the hole of the hollow bolt 39.
The second camshaft internal passage 22 formed in the intake camshaft 2 communicates with the second hydraulic chamber 42 via a communication passage 43, an annular groove 44, and an oil passage 35 a formed in the timing pulley 35. . The operating oil supplied from the oil pump 11 is supplied to the first hydraulic chamber 41 via the oil passage 9, the annular groove 6, the internal passage 21 and the hollow bolt 39 by the operation of the OCV 8. The state is selectively switched to a state of being supplied to the second hydraulic chamber 42 through the annular groove 7, the internal passage 22, the communication passage 43, and the annular groove 44.

The timing pulley 35 is formed such that the winding portion of the timing belt 32 extends to a position facing the end journal 5. The winding position of the timing belt 32 around the timing pulley 35 is set at a position where the running line 33 of the timing belt 32 overlaps with the end journal 5.

In this embodiment, when the engine is operating, V
In order to operate the VT 34, the hydraulic oil is selectively supplied to each of the hydraulic chambers 41 and 42, so that the ring gear 38
Rotate while moving along the axial direction of the intake side camshaft 2. By this operation, torque is applied to the intake-side camshaft 2, the rotation phase of the intake-side camshaft 2 with respect to the timing pulley 35 is changed, and the opening / closing timing (valve timing) of the intake valve is changed. The ring gear 38 is movable within a predetermined range in the axial direction of the intake-side camshaft 2, and the adjustment amount of the valve timing is changed depending on the position of the ring gear 38. Each hydraulic chamber 4
By controlling the supply of hydraulic oil (oil pressure) to the hydraulic valves 1 and 42, the hydraulic pressure balance between the hydraulic chambers 41 and 42 is appropriately adjusted, the position of the ring gear 38 is changed, and the valve timing of the intake valve is continuously (no Stage).

Since the relationship between the end journal 5 and the position where the timing belt 32 is wound around the timing pulley 35 is the same as in the above-described embodiment, the position corresponding to the end journal 5 is applied to the intake side camshaft 2. No bending force acts. Therefore, similarly to the above-described embodiment, deformation of the end journal 5 in which the oil supply passage is formed is prevented, and the amount of leakage of hydraulic oil is reduced.

In this embodiment, since the VVT 13 is attached to the intake side camshaft 2 outside the end journal 5, the maintenance work of the VVT 13 can be easily performed. Third Embodiment Next, a third embodiment will be described with reference to FIG. This embodiment is different from the above-described embodiments in the configuration of the power transmission unit that transmits the rotation of the crankshaft to the camshaft, and the other configurations are the same as the second embodiment. That is, a sprocket 45 is supported on the intake camshaft 2 in place of the timing pulley 35 so as to be rotatable relative to the intake camshaft 2, and the rotation of the crankshaft is performed via a chain 46 wound around the sprocket 45. The power is transmitted to the intake side camshaft 2. The position of the sprocket 45 is set at a position facing an intermediate position between the annular grooves 6 and 7 formed at a position corresponding to the end journal 5. Therefore, in this embodiment, the same operation and effect as in the second embodiment are exhibited.

(Fourth Embodiment) Next, a fourth embodiment will be described with reference to FIG. This embodiment is characterized in that the running line 33 of the timing belt 32 is located inside the position of the end journal 5 in the first to fifth embodiments.
This is significantly different from the third embodiment. Other configurations are basically the same as those of the first embodiment.

The cylinder head 1 is formed such that the end journal 5 supports the exhaust side camshaft 3 at its tip. The timing pulley 45 is formed such that the winding portion of the timing belt 32 is located inside a position facing the end journal 5. That is, the winding position of the timing belt 32 is set between the end journal 5 and the second journal 5a.

Accordingly, in this embodiment, the VVT 13 is operated in the same manner as in the first embodiment. Since the bending force acting on the exhaust camshaft 3 due to the tension of the timing belt 32 is shared by the two end journals 5 and the second journal 5a, the end journal 5 in which the oil supply passage is formed is formed. The elastic deformation and the increase in the clearance between the exhaust-side camshaft 3 and the end journal 5 cause
The end journal is restrained in a cantilevered state as compared with a conventional device in which a bending force is exerted. As a result, the amount of hydraulic oil leaking from the oil supply passage formed in the end journal 5 is reduced, and the responsiveness of the VVT 13 is improved as compared with the conventional device.

(Fifth Embodiment) Next, a fifth embodiment will be described with reference to FIG. This embodiment is characterized in that a rotating body for transmitting the rotation of the crankshaft to the camshaft is rotatably supported by the camshaft at an intermediate position between the end journal 5 and the second journal 5a of the camshaft. , VVT 13 are provided on the intake-side camshaft 2, which is greatly different from the fourth embodiment.

The internal rotor 15 and the rotor housing 16 constituting the VVT 13 are the same as those in the above-described embodiment.
A sprocket 48 is fixed to the rotor housing 16 so as to be integrally rotatable. A drive gear and a driven gear (not shown) for transmitting the rotation of the intake-side camshaft 2 to the exhaust-side camshaft 3 include a VVT for each of the camshafts 2 and 3.
13 is provided at the end opposite to the mounting portion.

In this embodiment, the rotational force of the crankshaft is transmitted to the sprocket 48 via the chain 46. The rotational force transmitted to the sprocket 48 is transmitted to the vane 15c by the hydraulic oil supplied into each of the hydraulic chambers 17 and 18, and transmitted from the vane 15c to the intake camshaft 2 via the internal rotor 15. And VVT13
According to the magnitude of the hydraulic pressure in each of the hydraulic chambers 17 and 18 acting on the vane 15c of the
The valve timing is changed by the relative rotation in the same direction as or in the opposite direction.

In this embodiment, similarly to the fourth embodiment, the camshaft (intake side camshaft 2) acts on the camshaft (intake side camshaft 2) by the tension of the interlocking band (chain 46) that transmits the rotation of the crankshaft to the rotating body (sprocket 48). The bending force is shared by the two journals, the end journal 5 and the second journal 5a. As a result, the amount of leakage of hydraulic oil from the oil supply passage formed in the end journal 5 is reduced in the same manner as described above, and the responsiveness of the VVT 13 is improved as compared with the conventional device.

In this embodiment, the rotating member (sprocket 48) for transmitting the rotation of the crankshaft to the camshaft is located at the intermediate position between the end journal 5 and the second journal 5a of the camshaft (intake side camshaft 2). It is supported by. Therefore, unlike the above-described embodiment, the end journal 5 is provided inside the rotating body (timing pulley 47).
And a space that can accommodate the VVT 13 is not required,
The structure of the rotating body and its manufacture are simplified, and the rotating body is made compact, so that the entire apparatus can be made compact.

In this embodiment, the sprocket 48
48 and the chain 4 as a rotating body for transmitting the rotation of the crankshaft to the camshaft and an interlocking band.
6, the space required in the axial direction of the camshaft for mounting the rotating body is also reduced.

(Sixth Embodiment) Next, a sixth embodiment will be described with reference to FIG. FIG. 8 shows a timing pulley 29,
FIG. 4 is a partially cutaway schematic view showing a relationship between an end journal 5 and a VVT 13, in which cams of camshafts 2 and 3, a middle journal, and the like are omitted. This embodiment includes a rotating body that transmits the rotation of the crankshaft to the camshaft,
The point that the VVT is arranged at a position separated from the VVT is greatly different from the above embodiments.

The basic configuration is the same as that of the first embodiment except that the VVT 13 is provided at the end opposite to the side corresponding to the end journal 5. A timing pulley 29 is fixed to a first end of the exhaust-side camshaft 3 so as to be integrally rotatable, and the VVT 13 is disposed at a second end of the exhaust-side camshaft 3. First and second camshaft passages 2
Reference numerals 1 and 22 are formed over substantially the entire length of the exhaust-side camshaft 3.

Hydraulic oil flows from the first end of the exhaust-side camshaft 3 to the first and second camshaft internal passages 21, 22.
And is supplied to the hydraulic chambers 17 and 18 of the VVT 13 disposed on the second end side via the internal passages 21 and 22. Then, the VVT 13 is operated in the same manner as described above, and the rotation phase of the drive gear 19 with respect to the exhaust camshaft 3 is changed. As a result, the rotation phase of the intake camshaft 2 that rotates integrally with the driven gear 20 that meshes with the drive gear 19 is changed, and the opening / closing timing of the intake valve is changed.

Also in this embodiment, as in the first to third embodiments, an interlocking belt (timing belt 32) interlocking with a crankshaft is connected to a rotating body connected to a camshaft (exhaust camshaft 3). Since the position wound around the (timing pulley 29) overlaps the end journal 5, no bending force (bending moment) acts on the camshaft at a position corresponding to the end journal 5. Therefore, deformation of the end journal 5 in which the oil supply passage is formed is prevented, and the leakage amount of the working oil is reduced.

The present invention is not limited to the above embodiments, but may be embodied with the following modifications, for example. (1) Even in a configuration in which the rotating body that transmits the rotation of the crankshaft to the camshaft is supported at a position (outside) outside the end journal with respect to the camshaft, the rotor-type VVT 13 is provided to the intake-side camshaft 2. It may be provided.

(2) The scissors gear is used as the rotation transmitting member between the camshafts 2 and 3. Alternatively, sprockets may be attached to the intake and exhaust camshafts 2 and 3, respectively, and both sprockets may be connected by a chain. Good.

(3) In each of the above embodiments, the rotor type VV
At T, the number of the vanes 15c was set to four.
The number of 5c may be 3 or less, or 5 or more. When the number of the vanes 15c is smaller than that in the embodiment, the configuration of the hydraulic passages such as the holes 27b and 28b formed in the internal rotor 15 can be simplified. When the number of the vanes 15c is larger than that in the above-described embodiment, a larger rotation torque can be applied to the vanes 15c.

(4) In each of the above embodiments, the opening / closing timing of the intake valve 2a is changed.
The opening / closing timing of the exhaust valve 3a may be changed.

(5) Each of the above embodiments is applied to the supply of hydraulic oil to the VVT as a hydraulic actuator, but may be applied to an oil supply device for supplying hydraulic oil to another hydraulic actuator.

The inventions other than those described in the claims which can be grasped from the embodiment and the modified examples will be described below together with their effects. (1) In the invention described in claim 2, the rotating body is connected to the camshaft at a position outside the end journal. In this case, the rotating body can be attached to the camshaft while the camshaft is supported by the journal, and the rotating body is connected to the camshaft at a position inside (inside) the end journal. Work becomes easy.

(2) In the second aspect of the present invention,
The rotating body is connected to the camshaft at a position inside the end journal. In this case, there is no need to provide a space for accommodating the end journal inside the rotating body, so that the structure of the rotating body and its manufacture are simplified, and the rotating body is made compact, so that the entire apparatus can be made compact.

(3) Claims 1 and 2 and (1),
(2) In the invention described in any one of (2), the first oil passage is formed on an inner peripheral surface of the end journal. In this case, the first
The strength of the camshaft is greater than when the oil passage is provided on the camshaft side.

[0062]

As described in detail above, according to the first aspect of the present invention, the position of the interlocking band interlocking with the crankshaft, which is wound around the rotating body connected to the camshaft, is set at the end portion. To overlap with the journal,
A bending force that bends the camshaft at a position corresponding to the end journal does not act, so that the amount of oil leakage at the end journal serving as the supply oil passage can be reduced, and a delay in hydraulic control can be prevented.

According to the second aspect of the present invention, the position where the interlocking belt interlocking with the crankshaft is wound around the rotating body connected to the camshaft is located inside (inside) the end journal. . Therefore, since the bending force acting on the camshaft is carried by the end journal and other journals disposed inside the end journal, the deformation at the end journal is suppressed as compared with the case of the cantilever state. Therefore, the amount of leakage of hydraulic oil can be reduced, and delay in hydraulic control can be prevented.

[Brief description of the drawings]

FIG. 1 is a partially cutaway side view of a valve timing control device according to a first embodiment.

FIG. 2 is a partially broken plan view.

FIG. 3 is a sectional view of a VVT.

FIG. 4 is a partially cutaway side view of a valve timing control device according to a second embodiment.

FIG. 5 is a partially broken side view of a valve timing control device according to a third embodiment.

FIG. 6 is a partially cutaway side view of a valve timing control device according to a fourth embodiment.

FIG. 7 is a partially cutaway side view of a valve timing control device according to a fifth embodiment.

FIG. 8 is a partially broken schematic plan view of a sixth embodiment.

FIG. 9 is a sectional view of a conventional valve timing control device.

FIG. 10 is a schematic view showing a deformed state of a cam shaft and an end journal.

[Explanation of symbols]

2 ... intake camshaft, 3 ... exhaust camshaft, 3
b: camshaft journal, 5: end journal,
5a: No. 2 journal, 6, 7: annular groove as first oil passage, 8: OCV, 11: oil pump as oil supply source, 13, 34: VVT as hydraulic actuator,
21: first camshaft internal passage, 22: second camshaft internal passage, 23, 24 ... oil passage as second oil passage, 29, 35, 47 ... timing pulley as rotating body, 32 ... interlocking Timing belt as a belt, 33 ...
A running line, 45, 48 ... a sprocket as a rotating body, 46 ... a chain as an interlocking band.

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁶ Identification code Agency reference number FI Technical display location F02B 67/06 F02B 67/06 D F02F 1/24 F02F 1/24 R

Claims (2)

[Claims] A camshaft supported by a plurality of journals; an end journal located at an end of the camshaft; a rotating body coupled to the camshaft at a position outside the end journal; An interlocking band wound around the rotating body and interlocking with a crankshaft; a first oil passage provided on an inner peripheral surface of the end journal or an outer peripheral surface of the camshaft; and provided inside the camshaft. A camshaft internal passage, and a second oil passage provided in a camshaft journal corresponding to the end journal so as to communicate the first oil passage and the camshaft internal passage; In an oil supply device for an internal combustion engine, one of an oil passage and the camshaft internal passage is communicated with an oil supply source, and the other is communicated with a hydraulic actuator. Oil supply device for an internal combustion engine, wherein a winding position of the interlocking zone of the rotating body is set to said end journal so as to overlap with said end journal. 2. A camshaft supported by a plurality of journals; an end journal located at an end of the camshaft; a rotating body connected to the camshaft; and a crankshaft wound around the rotating body. A first oil passage provided on an inner peripheral surface of the end journal or an outer peripheral surface of the camshaft; and an end portion for communicating the first oil passage and a camshaft internal passage. A second oil passage provided in a camshaft journal portion corresponding to a journal, wherein one of the first oil passage and the camshaft internal passage is communicated with an oil supply source, and the other is connected to a hydraulic actuator. In the oil supply device for an internal combustion engine that is communicated, the winding position of the interlocking band in the rotating body is positioned inward from the end journal. Oil supply device for an internal combustion engine, characterized in that setting the said end journal.