JP2004138076A - Valve timing change device of internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing change device of an internal combustion engine which can effectively prevent occurrence of improper lubrication of a sprocket. <P>SOLUTION: A nearly semi-cylindrical housing body 5 has the sprocket 3 to which a timing chain is attached, and a vane 18 which rotates integrally with a cam shaft 1 forms hydraulic fluid rooms 19, 20 separately within the housing body 5. The housing body 5 and the vane 18 are relatively rotated by supplying and draining hydraulic fluid to and from the hydraulic fluid rooms 19, 20. The sprocket 3 is integrally molded with the housing body 5 by using porous sintered metal, and is arranged in the axial direction area and on the outer peripheral side of the hydraulic fluid rooms 19, 20. The both sides of the housing body 5 are sealed by plate members 6, 7 which have different thickness, and the thinly-formed plate member 6 is formed of non-porous material. <P>COPYRIGHT: (C)2004,JPO

Description

The present invention relates to a valve timing changing device for changing the opening / closing timing of an intake valve or an exhaust valve during operation of an internal combustion engine.

This type of valve timing changing device is provided between a sprocket rotated by a timing chain in synchronization with the rotation of the internal combustion engine and a camshaft that drives an intake valve or an exhaust valve, and the camshaft is moved relative to the sprocket. The opening and closing timing of the intake valve or the exhaust valve is changed by relative rotation.

For example, Patent Document 1 discloses a sprocket that is rotated by a timing chain in synchronization with the rotation of an internal combustion engine, a housing that rotates with the sprocket, a rotor that is housed in the housing, and rotates with a camshaft. A plurality of vanes are provided on the rotor so as to protrude in the radial direction and form a plurality of hydraulic oil chambers in the housing, and hydraulic suction / discharge means for supplying and discharging hydraulic oil to and from the hydraulic oil chambers. A valve timing changing apparatus is shown in which the housing and the rotor are relatively rotated by supplying and discharging the same.

The sprocket is provided integrally with the housing, and the housing and the sprocket are made of cast iron.

Further, external teeth are provided on the outer periphery of the sprocket, and a timing chain is wound around the sprocket.
JP-A-9-324611

By the way, the lubrication of the sprocket and the timing chain meshing with the sprocket is performed by using the oil splash in the oil pan and using the oil splash accompanying the rotation of the crankshaft. Is difficult to supply lubricating oil.

Therefore, there is a possibility that poor lubrication may occur at a portion where the sprocket meshes with the timing chain.

The present invention has been devised in view of the above-mentioned conventional circumstances, and has as its object to provide a valve timing changing device capable of effectively preventing poor lubrication of a sprocket.

Therefore, the invention according to claim 1 is provided between a sprocket that is rotated by a timing chain in synchronization with the rotation of the internal combustion engine and a camshaft that drives an intake valve or an exhaust valve. A valve timing changing device for an internal combustion engine capable of changing the opening / closing timing of an intake valve or an exhaust valve by relatively rotating the sprocket, wherein the sprocket is provided, and a substantially cylindrical housing main body which rotates together with the sprocket; A housing member composed of plate members having different thicknesses for sealing both sides is provided so as to be relatively rotatable with respect to the housing member. A vane housed therein and forming a plurality of hydraulic oil chambers in a circumferential direction inside a housing member; A hydraulic oil chamber formed between the managing body and the vanes,
And a hydraulic supply / discharge means for supplying and discharging hydraulic oil to and from the hydraulic oil chamber to relatively rotate the housing member and the vane. The housing body is formed by integrating a sprocket having external teeth with a porous material. The sprocket provided in the housing body is formed in the axial direction of the hydraulic oil chamber and on the outer peripheral side, and the thin plate member is formed of a non-porous material.

In such a configuration, the sprocket is rotated by the timing chain in synchronization with the rotation of the internal combustion engine, and the camshaft is rotated via the valve timing changing device. Thereby, the camshaft drives the intake valve or the exhaust valve.

Further, the relative rotation of the camshaft with respect to the sprocket is performed by supplying and discharging hydraulic oil to and from a hydraulic oil chamber formed between a housing member that rotates with the sprocket and a vane that rotates with the camshaft. This is performed by relative rotation of the vane. In this case, the supply and discharge of the hydraulic oil to and from the hydraulic oil chamber are performed by hydraulic suction and discharge means.

(4) By rotating the camshaft relative to the sprocket, the rotation phase of the camshaft with respect to the rotation of the internal combustion engine is changed, and the opening / closing timing of the intake valve or the exhaust valve is changed.

Here, in the present invention, a sprocket having external teeth is integrally formed of a porous material in the housing body of the housing member, and the sprocket provided in the housing body has an axial range of the hydraulic oil chamber. It may be arranged on the outer peripheral side. In this case, the hydraulic oil guided to the hydraulic oil chamber is permeated and held in the gap of the porous material by receiving the pressure and centrifugal force in the hydraulic oil chamber, and lubricates the meshing portion between the sprocket and the timing chain. I do.

Thus, the risk of poor lubrication at the portion where the sprocket meshes with the timing chain is advantageously prevented.

Therefore, a valve timing changing device capable of effectively preventing poor lubrication of the sprocket can be obtained.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

FIG. 1 is an explanatory view showing a cross section of a main part of a valve timing changing device for an internal combustion engine showing an embodiment of the present invention. FIG. 2 is a cross-sectional view taken along line AA of FIG. FIG. 3 is an enlarged sectional view showing a main part of FIG.

In the figure, a camshaft denoted by reference numeral 1 can drive an intake valve or an exhaust valve of an internal combustion engine, and in this embodiment, is a camshaft that drives an intake valve.

The camshaft 1 is rotatably supported by a bearing 2 fixed to a cylinder head (not shown). A cam (not shown) is formed on a main portion (not shown) of the camshaft 1 on the right side of the bearing 2 in FIG. 1, and the intake valve is opened and closed by the cam.

The camshaft 1 is rotatably driven by a sprocket 3 which is rotated in synchronization with the internal combustion engine. The sprocket 3 is rotatable together with a housing member 4. Relative rotation by a predetermined angle.

That is, the sprocket 3 is integrally formed on the outer peripheral side of the housing main body 5 of the housing member 4 including the substantially cylindrical housing main body 5 and the plate members 6 and 7 that seal both ends of the housing main body 5. I have. Here, in this embodiment, the housing member 4 corresponds to a first rotating body of the present invention. The housing body 5 of the housing member 4 and the plate members 6 and 7 are integrally connected by a plurality of connection bolts 8.

ス プ External teeth 9 are formed on the outer peripheral side of the sprocket 3, and a timing chain 10 driven by a crankshaft (not shown) is wound around the external teeth 9.

The sprocket 3 is provided at a position farther from the camshaft 1 than the center in the axial direction of the housing body 5 (to the left in FIG. 1), and the thickness of the plate member 6 is formed smaller than the thickness of the plate member 7. It is. Therefore, the sprocket 3 is provided at a position farther from the camshaft 1 than the axial center position of the housing member 4 (first rotating body). The sprocket 3 can be provided substantially at the center of the housing body 5 in the axial direction. In this case as well, the thickness of the plate members 6 and 7 is adjusted so that the sprocket 3 is positioned at the center of the housing member 4 in the axial direction. It can be provided at a position farther from the camshaft 1 than at the position.

ハ ウ ジ ン グ In the housing member 4, the sprocket 3 and the housing body 5 are formed of sintered metal, and the plate members 6, 7 are formed of a steel plate or the like. That is, the sprocket 3 and the housing body 5 are formed of a porous material, and the plate members 6, 7 are formed of a non-porous material.

Further, the inside of the housing member 4 is hollow as a whole, and a plurality of (four in this embodiment) projections 12 projecting inward in the radial direction of the substantially cylindrical housing body 5 are formed. As a result, four rooms 13 connected at the center are formed radially outward (see FIG. 2).

A vane member 15 is accommodated in the housing member 4 so as to be relatively rotatable by a predetermined angle. The vane member 15 and the housing member 4 are used as main elements to constitute a relative rotation means 16 described later in detail. I have. Here, in this embodiment, the vane member 15 corresponds to a second rotating body of the present invention.

The vane member 15 has a plurality (four in this embodiment) of vanes 18 radially protruding from a body portion 17 of the vane member 15. 4.

ベ ー By disposing the vane 18 of the vane member 15 in the room 13, a pair of hydraulic oil chambers 19 and 20 are formed in the room 13 so as to face both sides in the circumferential direction of the vane 18. That is, the hydraulic oil chambers 19 and 20 are formed between the housing member 4 as the first rotating body and the vane member 15 as the second rotating body. Further, four pairs of the hydraulic oil chambers 19 and 20 are formed in this embodiment.

The sealing between the hydraulic oil chambers 19 and 20 is performed by pressing a seal member 21 provided at the tip of a protrusion 12 formed on the inner peripheral side of the housing body 5 with a spring member 22 by using a spring member 22. This is accomplished by sliding the seal member 23 provided at the tip of the vane 18 with a spring member 24 and sliding the seal member 23 on the inner periphery of the housing body 5.

The vane member 15 has a radial oil chamber-side passage 25 communicating with the hydraulic oil chamber 19 and a radial oil chamber-side passage 26 communicating with the hydraulic oil chamber 20. A hole 27 that is open at one end and that opens at 25 and 26 is formed in the axial direction. The oil chamber side passages 25 and 26 are open at positions separated from each other in the axial direction of the hole 27.

Thereby, the housing member 4 and the vane member 15 can be relatively rotated by selectively supplying and discharging hydraulic oil to and from the hydraulic oil chambers 19 and 20 via the oil chamber side passages 25 and 26. It has become.

The vane member 15 is connected to the camshaft 1. That is, the end of the camshaft 1 is inserted into the hole 27 of the vane member 15 and is connected to the camshaft 1 by a bolt 29 that passes through the body 17 of the vane member 15 in the axial direction.

Here, while the sprocket 3 is provided in the housing member 4, the vane member 15 connected to the camshaft 1 is rotatable relative to the housing member 4, so that the oil chamber side passages 25 and 26 are provided. The housing member 4 and the vane member 15 can be relatively rotated within a predetermined angle range by selectively supplying and discharging the hydraulic oil to and from the hydraulic oil chambers 19 and 20 via. Therefore, relative rotation means 16 for rotating the sprocket 3 relative to the camshaft 1 is constituted by using the housing member 4 and the vane member 15 as main elements.

(4) Between the housing member 4 and the vane member 15, a rotation restricting means 34 for restricting the relative rotation between the housing member 4 and the vane member 15 is provided. In this embodiment, the rotation restricting means 34 is an engaging member provided in a cylinder hole 35 formed in the vane member 15 so as to be able to protrude in the axial direction of the vane member 15 by being housed together with a spring member 36. The tip of 37 is configured to be able to engage with an engagement hole 38 provided in (the plate member 6 of) the housing member 4.

The cylinder hole 35 is formed in the vane member 15, more specifically, in one of the vanes 18 in which the circumferential width of the vane member 15 is increased, in the axial direction. A spring receiver 39 for a spring member 36 is press-fitted and fixed to one open end of the cylinder hole 35, and the spring receiver 39 is preferably formed of a material having a higher hardness than the vane 18. A cutout groove 40 for venting air is provided at a predetermined position on the outer peripheral side of the spring receiver 39, and the cutout groove 40 is a radial groove provided on the side surface of the body 17 of the vane member 15. It communicates with 41. As a result, the inside of the cylinder hole 35 located on the rear end side of the engagement member 37 is open to the atmosphere through the notch groove 40 and the groove 41 on the opening end side.

The distal end of the engaging member 37 is formed in a tapered shape, and the tapered distal end can protrude from the inside of the cylinder hole 35. The engaging member 37 has a recess 42 at the front end thereof and a blind hole 43 opened at the rear end side of the engaging member 37, thereby reducing the weight.

In this embodiment, the engagement hole 38 is made of a material having a hardness higher than that of the housing member 4 (the plate member 7 of the housing member 4). (Plate member 7).

The shape of the engagement hole 38 is such that the opening end side is formed in a cup shape having a large diameter, and an oil chamber 45 is formed at the bottom of the engagement hole 38 in a state where the engagement member 37 is engaged. It has become. The inside of the engagement hole 38 and the inside of the oil chamber 45 communicate with the hydraulic oil chamber 19 via an oil hole 46 formed in the plate member 7 and the engagement hole member 44.

油 圧 In the camshaft 1 inserted into the hole 27 formed in the vane member 15, hydraulic-side passages 51 and 52 are formed in the axial direction. The hydraulic side passages 51 and 52 communicate with oil chamber side passages 25 and 26 formed in the vane member 15, respectively, and also communicate with a hydraulic suction / discharge unit described later.

That is, the hydraulic side passage 51 is formed in a blind hole shape whose front end side does not open in the axial direction from the end face of the camshaft 1, and the opening end is sealed at the bottom side of the hole 27. The hydraulic side passage 51 communicates with the oil chamber side passage 25 through a radial passage 53 branched from the hydraulic side passage 51 and a circumferential groove 54 to which the radial passage 53 communicates on the opening end side. The hydraulic side passage 51 communicates with a hydraulic suction / discharge unit, which will be described later, via a radial passage 55 branched from the hydraulic side passage 51 and a peripheral groove 56 communicating with the radial passage 55 on the distal end side. (See FIG. 3).

The hydraulic side passage 52 is formed in a blind hole shape whose axial end does not open from the end surface of the camshaft 1 in the axial direction, and the opening end is sealed by a plug member 57. The hydraulic side passage 52 communicates with the oil chamber side passage 26 through a radial passage 58 branched from the hydraulic side passage 52 on the opening end side and a circumferential groove 59 through which the radial passage 58 communicates. . The hydraulic passage 52 communicates with a hydraulic suction / discharge unit, which will be described later, via a radial passage 60 branched from the hydraulic passage 52 and a circumferential groove 61 communicating with the radial passage 60 at the distal end. (See FIG. 3).

The hydraulic suction / discharge means 66 communicating with the hydraulic side passages 51 and 52 formed in the camshaft 1 includes a suction / discharge passage 67 communicating with the hydraulic side passage 51, a suction / discharge passage 68 communicating with the hydraulic side passage 52, and the suction / discharge passage 67. , 68 are selectively switched between a supply passage 70 from an oil pump 69 and a discharge passage 72 communicating with an oil storage tank 71 for communication or shutoff, and a control device 74 for controlling the switching valve 73. As main elements (see FIG. 1).

４A four-port valve is employed as the switching valve 73 in this embodiment. Various signals indicating the operating state of the internal combustion engine are input to a control device 74 that controls the switching valve 73.

In such a configuration, when the internal combustion engine is started, when hydraulic oil is not sufficiently supplied from the oil pump 69, or when a signal for maintaining the most retarded state is input to the control device 74, relative rotation is performed. The vane member 15 of the means 16 is at the most retarded position with respect to the housing member 4 (see FIG. 2), and the tip of the engaging member 37 of the rotation restricting means 34 engages with the engaging hole 38, 4 and the vane member 15 are connected. Therefore, the rotational driving force applied to the sprocket 3 from the unillustrated crankshaft via the timing chain 10 is transmitted to the camshaft 1 via the housing member 4 and the vane member 15. In this case, the vane 18 of the vane member 15 does not abut on the side surface of the projection 12 forming the room 13 in the housing member 4.

(4) When the camshaft 1 rotates, the intake valve of the internal combustion engine is driven, and the opening and closing of the intake valve is controlled.

When the vane member 15 is at the most retarded position with respect to the housing member 4, the engagement member 37 of the rotation restricting means 34 is pressed by the spring member 36, and the tip of the engagement member 37 is engaged with the engagement hole 38. The relative rotation between the housing member 4 and the vane member 15 is restricted. Therefore, when the camshaft 1 drives an intake valve (not shown), the vane member 15 rotates relative to the housing member 4 even if a positive or negative reversing torque acts on the camshaft 1. Since there is no vane, it is advantageous to prevent the vane 18 of the vane member 15 from abutting against the side surface of the projection 12 to generate a tapping sound or the like.

Next, when the advance angle control is performed, the switching valve 73 of the hydraulic supply / discharge means 66 is switched and controlled by the control device 74 so that the supply passage 70 from the oil pump 69 is connected to the supply / discharge passage 67 and the supply By connecting the discharge passage 68 to the discharge passage 72, the operating oil from the oil pump 69 is supplied from the supply / discharge passage 67 to the peripheral groove 56, the radial passage 55, the hydraulic side passage 51, the radial passage 53, and the peripheral groove 54. And, it is led into the working oil chamber 19 through the oil chamber side passage 25. Hydraulic oil guided into the hydraulic oil chamber 19 flows through an oil hole 46 formed in the plate member 7 and the engagement hole member 44 into an engagement hole 38 with which the tip of the engagement member 37 engages. And into the oil chamber 45 formed at the bottom of the engagement hole 38.

At the same time, the inside of the hydraulic oil chamber 20 is discharged to the discharge passage 72 via the oil chamber side passage 26, the circumferential groove 59, the radial passage 58, the hydraulic side passage 52, the radial passage 60, the circumferential groove 61, and the supply / discharge passage 68. Will be in communication.

The hydraulic oil is guided into the hydraulic oil chamber 19 and the engagement hole 38 (and the oil chamber 45) of the rotation restricting means 34, so that the engagement member 37 has the hydraulic oil chamber 19 and the engagement hole 38 (and The hydraulic oil pressure in the oil chamber 45) acts, and the engaging member 37 is urged toward the spring receiver 39 against the spring force of the spring member 36, and is pushed back into the cylinder hole 35. Therefore, the distal end of the engaging member 37 is disengaged from the inside of the engaging hole 38 and the engagement is released, whereby the restraint of the housing member 4 and the vane member 15 by the engaging member 37 is released.

While the hydraulic oil is supplied into the hydraulic oil chamber 19, the hydraulic pressure in the hydraulic oil chamber 19 acts on the side surface of the vane 18 by the hydraulic oil chamber 20 communicating with the discharge passage 72, and the vane member 15 Is rotated with respect to the housing member 4 in the direction of the arrow in FIG. As a result, the sprocket 3 and the camshaft 1 rotate relatively, the rotation phase of the camshaft 1 with respect to the crankshaft is changed, and the camshaft 1 is advanced and is driven by the camshaft 1. The opening and closing timing of the intake valve can be advanced.

When the camshaft 1 is advanced and the vane member 15 is relatively rotated with respect to the housing member 4 and is at the most advanced position, the engaging member 37 is moved to the cylinder hole 35 by the hydraulic pressure in the hydraulic oil chamber 19. The state of being pushed back inside is continued, and the front end of the engagement member 37 does not contact the side surface of the plate member 6.

Next, the switching valve 73 of the hydraulic supply / discharge means 66 is controlled by the control device 74 to connect the supply passage 70 from the oil pump 69 to the supply / discharge passage 68 and connect the supply / discharge passage 67 to the discharge passage 72. Then, the hydraulic oil from the oil pump 69 is guided to the hydraulic oil chamber 20 via the circumferential groove 61, the radial passage 60, the hydraulic passage 52, the radial passage 58, the circumferential groove 59, and the oil chamber side passage 26. . The hydraulic oil in the hydraulic oil chamber 19 passes through the oil chamber side passage 25, the circumferential groove 54, the radial passage 53, the hydraulic side passage 51, the radial passage 55, the circumferential groove 56, the suction / discharge passage 67, and the discharge passage 72. The oil is discharged to the oil storage tank 71.

When the hydraulic oil in the hydraulic oil chamber 19 is discharged, the engaging member 37 is urged by the spring force of the spring member 36 acting on the engaging member 37. In a state where the housing member 4 and the vane member 15 are not engaged with the engagement holes 38, the state in which the restraint by the rotation restricting means 34 is released is continued.

While the hydraulic oil is supplied into the hydraulic oil chamber 20, the hydraulic pressure in the hydraulic oil chamber 20 acts on the side surface of the vane 18 by the hydraulic oil chamber 19 communicating with the discharge passage 72, and the vane member 15 Is rotated counterclockwise in FIG. 2 with respect to the housing member 4, that is, in the retard direction. As a result, the sprocket 3 and the camshaft 1 rotate relative to each other, the rotation phase of the camshaft 1 with respect to the crankshaft is changed, and the camshaft 1 is again retarded and driven by the camshaft 1 The opening / closing timing of the intake valve is delayed.

When the camshaft 1 is retarded and the vane member 15 is relatively rotated with respect to the housing member 4 to the most retarded position, the tip of the engaging member 37 is engaged by the spring force of the spring member 36. It is re-engaged in the hole 38.

When the vane member 15 is rotating with respect to the housing member 4 in the advancing direction or the retarding direction, the switching valve 73 of the hydraulic supply / discharge means 66 is switched by the control device 74 and is controlled. When the communication between 67, 68 and the supply passage 70 or the discharge passage 72 is interrupted, the housing member 4 and the vane member 15 are held at an intermediate position of the relative rotation. As a result, the sprocket 3 and the camshaft 1 are held at an intermediate position of the relative rotation, and the camshaft 1 controls the intake valve driven by the camshaft 1 at a desired timing. Will be.

In this case, since the inside of the hydraulic oil chamber 19 is maintained in a predetermined pressure state and is in a closed state, the spring force of the spring member 36 acts on the engagement member 37. Since the engaging member 37 does not engage with the engaging hole 38, the housing member 4 and the vane member 15 continue to be released from the restraint by the rotation restricting means 34.

Here, in the present invention, the sprocket 3 and the housing body 5 provided with the sprocket 3 are integrally formed of sintered metal, and the housing member 4 as the first rotating body is provided on the housing member 4. The sprocket 3 is disposed in the axial range of the hydraulic oil chambers 19 and 20 and on the outer peripheral side. As a result, the hydraulic oil guided to the hydraulic oil chambers 19 and 20 receives the pressure and centrifugal force in the hydraulic oil chambers 19 and 20 and is permeated and held in the voids of the porous sintered metal. Lubricate the portion that engages with the timing chain 10.

Thus, the risk of poor lubrication at the portion where the sprocket 3 meshes with the timing chain 10 is advantageously prevented.

Therefore, it is possible to obtain a valve timing device capable of effectively preventing poor lubrication of the sprocket 3 from occurring.

Since the sprocket 3 is provided at a position farther from the camshaft 1 than the center of the housing member 4 in the axial direction, whirling due to misalignment or unbalance of the valve timing device can be prevented. That is, in the valve timing device, since the vane member 15 is attached to the end of the camshaft 1, there is a possibility that whirling may occur if there is misalignment or imbalance in the attachment. However, in the present embodiment, the sprocket 3 is used. The timing chain 10 wound around the valve timing device applies a restraining force to the valve timing device at a position away from the camshaft 1. That is, the tension of the timing chain 10 acts on the valve timing device including the housing member 4 as a restraining force against whirling. Thereby, whirling can be prevented.

The housing member 4 includes a substantially cylindrical housing body 5 provided with the sprocket 3 and plate members 6 and 7 for sealing both ends of the housing body 5. , The housing main body 5 is easily formed. That is, since the housing main body 5 provided with the sprocket 3 has a shape symmetrical with respect to the center line in the axial direction, the shape of the mold is simplified at the time of sintering, and variation in the density of the sintered metal is suppressed. Thus, the sintering of the housing body 5 is facilitated.

The housing member 4 includes a substantially cylindrical housing body 5 provided with the sprocket 3 and plate members 6 and 7 for sealing both ends of the housing body 5. Since only the sintered metal is formed, the operating oil guided to the operating oil chambers 19 and 20 is effectively permeated and held in the sprocket 3 and the housing body 5. That is, by forming the plate members 6 and 7 from a non-porous steel plate or the like, the operating oil does not permeate the plate members 6 and 7 but effectively penetrates into the sprocket 3 and the housing body 5. is there.

Further, the first housing member 4 includes a substantially cylindrical housing main body 5 provided with the sprocket 3 and plate members 6 and 7 for sealing both ends of the housing main body 5. Since the vane 18 which is rotatably accommodated inside the member 4 and which forms a plurality of hydraulic oil chambers 19 and 20 in the circumferential direction inside the housing member 4 is provided, the hydraulic oil chambers 19 and 20 are provided with shafts. Therefore, the sprocket 3 can be formed relatively long in the direction, so that the degree of freedom of the arrangement of the sprocket 3, that is, the degree of freedom of the arrangement in the axial direction can be increased.

Although the embodiment has been described with reference to the drawings, the specific configuration is not limited to this embodiment, and can be changed without departing from the spirit of the invention. For example, the first rotating body is the housing member 4, and the second rotating body is relatively rotatably housed inside the housing member 4, and a plurality of hydraulic oil chambers 19, Although the embodiment has been described in which the housing member 4 is provided with the vanes 18 forming the first and second rotating members 20, the first rotating member and the second rotating member are connected by a helical gear, and the helical gear is connected to the first rotator. The first rotating body and the second rotating body may be relatively rotated by operating with hydraulic oil guided to a working oil chamber formed between the first rotating body and the second rotating body.

Although the embodiment in which the camshaft 1 is advanced is described, the invention can be applied to a valve timing changing device that performs retard control.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an explanatory diagram illustrating a cross section of a main part of a valve timing device for an internal combustion engine according to an embodiment of the present invention. FIG. 2 is a sectional view taken along the line AA of FIG. 1, showing the bolt removed. 1. Sectional drawing which expands and shows the principal part of FIG.

Explanation of reference numerals

DESCRIPTION OF SYMBOLS 1 ... Camshaft 3 ... Sprocket 4 ... Housing member (1st rotating body)
5 Housing body 15 Vane member (second rotating body)
18 ... Vane 19 ... Hydraulic oil chamber 20 ... Hydraulic oil chamber 22 ... Spring member 23 ... Seal member 34 ... Rotation restricting means 66 ... Hydraulic suction / discharge means

Claims (5)

Provided between a sprocket rotated by a timing chain in synchronization with the rotation of the internal combustion engine and a camshaft that drives an intake valve or an exhaust valve. In a valve timing changing device of an internal combustion engine capable of changing the opening / closing timing of a valve,
The sprocket is provided, a housing member including a substantially cylindrical housing body that rotates together with the sprocket, and a plate member having a different thickness that seals both sides of the housing body.
The housing member is provided so as to be relatively rotatable, rotates together with the camshaft, is housed in the housing member so as to be relatively rotatable, and forms a plurality of hydraulic oil chambers in the housing member in a circumferential direction. Vane,
A hydraulic oil chamber formed between the housing body and the vane;
Hydraulic oil supply and discharge means for supplying and discharging hydraulic oil to and from the hydraulic oil chamber and for relatively rotating the housing member and the vane;
With
The housing main body is formed by integrally forming a sprocket having external teeth with a porous material, and the sprocket provided in the housing main body is disposed in an axial range and an outer peripheral side of the hydraulic oil chamber,
A valve timing changing device for an internal combustion engine, wherein the thinly formed plate member is formed of a nonporous material. An engaging member housed in the vane and urged by a spring member to protrude in the axial direction, and an engaging hole provided on the thickly formed plate member and capable of engaging the engaging member. Rotation control means is provided,
The valve timing changing device for an internal combustion engine according to claim 1, wherein the rotation restricting means is released from the restriction by the action of hydraulic oil pressure. The valve timing changing device for an internal combustion engine according to claim 1, wherein the thinly formed plate member is formed of a steel plate. The valve timing changing device for an internal combustion engine according to claim 1, wherein the housing body and the plate member are integrally connected by a plurality of connection bolts inserted from the thin plate member side. 2. The valve timing changing device for an internal combustion engine according to claim 1, wherein the porous material is a sintered metal that receives the pressure and centrifugal force in the hydraulic oil to permeate and hold the hydraulic oil. 3.

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