JP3996895B2 - Valve timing changing device for internal combustion engine - Google Patents

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 that is rotated by a timing chain in synchronization with the rotation of an internal combustion engine and a camshaft that drives an intake valve or an exhaust valve. The opening / closing timing of the intake valve or 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 rotation of an internal combustion engine, a housing that rotates together with the sprocket, a rotor that is housed in the housing and rotates together with a camshaft, The rotor includes a plurality of vanes that project in the radial direction and form a plurality of hydraulic oil chambers in the housing, and hydraulic suction / discharge means that supplies and discharges the hydraulic oil to and from the hydraulic oil chamber. A valve timing changing device is shown in which the housing and the rotor are rotated relative to each other by supplying and discharging the gas.

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

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

  By the way, the lubricating oil in the oil pan is used to lubricate the sprocket and the timing chain meshing with the sprocket, and the oil splash accompanying the rotation of the crankshaft is used. Is hard to be supplied with lubricating oil.

  For this reason, there is a risk that the sprocket may cause poor lubrication at the meshing portion with the timing chain.

  The present invention has been devised in view of the above-described conventional situation, and an object thereof is to provide a valve timing changing device that can effectively prevent the occurrence of poor lubrication of a sprocket.

Accordingly, a first aspect of the present invention, provided between the cam shaft for driving the in synchronization with the rotation of the internal combustion engine sprocket and the intake valve or an exhaust valve that is rotating relative to the camshaft relative to the sprocket In 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 rotating, a substantially cylindrical housing body that rotates together with the sprocket and has a plurality of protrusions on the inner periphery , and the housing body a first plate member sealing the said camshaft seals the opposite side to the cam shaft of the housing body, a thin second plate member than the plate thickness of the first plate member, the housing body and the first and a housing member formed by connecting the axial direction by a second plate member bolt, the housing member relative times to the interior of the housing member Mounted for, and a vane forming a plurality of working chambers between said protrusions, said housing body so as to form a porous material, wherein the predetermined position of the outer peripheral portion of the first plate member A female screw hole into which the tip of the bolt is screwed is formed.

  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.

  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 together with the sprocket and a vane that rotates together with the camshaft. This is done by relative rotation of the vane. In this case, supply and discharge of the hydraulic oil to and from the hydraulic oil chamber are performed by a hydraulic intake / exhaust means.

By rotating the camshaft relative to the sprocket, the rotation phase of the camshaft relative 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.
According to a second aspect of the present invention, the sprocket is integrally formed on the outer periphery of the housing body, the sprocket is formed of a porous material, and the second plate member is formed of a non-porous material. It is characterized by that.
The invention described in claim 3 is characterized in that the second plate member is formed of a steel plate .
The invention according to claim 4 is provided between a sprocket that rotates in synchronization with the rotation of the internal combustion engine and a camshaft that drives an intake valve or an exhaust valve, and rotates the camshaft relative to the sprocket. In the valve timing change device for an internal combustion engine that can change the opening and closing timing of the intake valve or the exhaust valve,
A housing formed of a porous material, comprising a substantially cylindrical housing body that rotates together with the sprocket and has a plurality of protrusions on the inner periphery, and a first plate member that seals the camshaft side of the housing body A member, a second plate member sealing the opposite side of the housing body from the camshaft, and having a plate thickness thinner than the first plate member, the housing body, and the first and second plate members. A housing member connected from the axial direction by a bolt, and a vane provided inside the housing member so as to be relatively rotatable with the housing member and forming a plurality of working chambers between the protrusions, An engagement member that is housed in the vane and is urged by a spring member to protrude in the axial direction, and a first plate member that is embedded in the first plate member and locks the engagement member. Hard The engagement hole member is provided with a locking hole that is provided in the engagement hole member and can be locked by the engagement member, and the engagement member engages with or releases the engagement hole. And a rotation restricting means for restricting or releasing the relative rotation between the housing member and the vane, and a female screw hole into which the tip of the bolt is screwed is formed in the first plate member. It is said.
The invention according to claim 5 is characterized in that the porous material is formed of a sintered metal that permeates and holds hydraulic oil under pressure and centrifugal force in the hydraulic oil.

  Here, in the present invention, the housing main body of the housing member is formed by integrally forming a sprocket having external teeth with a porous material, and the sprocket provided in the housing main body has an axial range of the hydraulic oil chamber and You may make it arrange | position to the outer peripheral side. In this case, the hydraulic oil guided to the hydraulic oil chamber is infiltrated and held in the gap of the porous material under pressure and centrifugal force in the hydraulic oil chamber, and lubricates the meshed portion of the sprocket and the timing chain. To do.

  This advantageously prevents the sprocket from causing poor lubrication at the meshing portion with the timing chain.

  Therefore, a valve timing changing device that can effectively prevent the occurrence of poor lubrication of the sprocket is 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 section of a valve timing changing device for an internal combustion engine according to an embodiment of the present invention, and FIG. 2 is a sectional view taken along line AA of FIG. FIG. 3 is an enlarged cross-sectional view showing a main part of FIG.

  In the figure, a camshaft indicated by reference numeral 1 can drive an intake valve or an exhaust valve of an internal combustion engine. In this embodiment, the camshaft drives the 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 the trunk portion (not shown) of the right camshaft 1 in FIG. 1 with respect to the bearing 2, and the intake valve is driven to open and close by this cam.

  The camshaft 1 is rotationally driven by a sprocket 3 that is rotated in synchronism with the internal combustion engine. The sprocket 3 can be rotated together with a housing member 4. Thus, relative rotation is possible at a predetermined angle.

That is, the housing member 4 has a substantially cylindrical housing body 5, the first plate member 6 for sealing the front end side of the housing body 5, the second plate member 7 which seals the rear end The sprocket 3 is integrally formed on the outer peripheral side of the housing body 5. The housing body 5 of the housing member 4 and the first and second plate members 6 and 7 are integrally connected by a plurality of connecting bolts 8.

  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 axial center of the housing body 5 (leftward in FIG. 1), and the thickness of the first plate member 6 is the second plate member 7. It is formed thinner than the thickness. For this reason, 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). Further, the sprocket 3 can be provided at a substantially central position in the axial direction of the housing body 5. In this case, the sprocket 3 can be mounted on the housing by adjusting the thicknesses of the first and second plate members 6 and 7. The member 4 can be provided at a position farther from the camshaft 1 than the center position in the axial direction.
Further, a female screw hole into which the tip of the connecting bolt 8 is screwed is formed on the outer peripheral portion of the second plate member 7 having a plate thickness larger than that of the first plate member 6.

  In the housing member 4, the sprocket 3 and the housing body 5 are formed of sintered metal, and the plate members 6 and 7 are formed of a steel plate or the like. That is, the sprocket 3 and the housing body 5 are made of a porous material, and the plate members 6 and 7 are made 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 chambers 13 connected at the central portion are formed on the outer side in the radial direction (see FIG. 2).

  A vane member 15 is accommodated in the housing member 4 so as to be relatively rotatable at a predetermined angle. A relative rotating means 16 described later in detail is configured with the vane member 15 and the housing member 4 as main elements. Yes. 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 projecting in a radial direction from the trunk portion 17, and the housing member is arranged in a state where the vanes 18 are disposed in the chamber 13. 4 is accommodated.

  By arranging the vane 18 of the vane member 15 in the chamber 13, a pair of hydraulic oil chambers 19, 20 are defined in the chamber 13 so as to face both sides of the vane 18 in the circumferential direction. 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.

  Sealing between the hydraulic oil chambers 19 and 20 is performed by pressing the sealing member 21 provided at the tip of the protrusion 12 formed on the inner peripheral side of the housing body 5 with the spring member 22 and the outer periphery of the trunk portion 17 of the vane member 15. This is accomplished by pressing the seal member 23 provided at the tip of the vane 18 with the spring member 24 and slidingly contacting the inner periphery of the housing body 5.

  The vane member 15 is formed with 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, and these oil chamber side passages. A hole 27 having one end opened to open 25 and 26 is formed in the axial direction. The oil chamber side passages 25 and 26 are opened 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 the hydraulic oil to and from the hydraulic oil chambers 19 and 20 via the oil chamber side passages 25 and 26. It is like that.

  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 the bolt 29 that passes through the body portion 17 of the vane member 15 in the axial direction.

  Here, since 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. By selectively supplying and discharging the hydraulic oil to and from the hydraulic oil chambers 19 and 20, the housing member 4 and the vane member 15 can be relatively rotated within a predetermined angle range. Accordingly, relative rotation means 16 for rotating the sprocket 3 relative to the camshaft 1 is configured with the housing member 4 and the vane member 15 as main elements.

Between the housing member 4 and the vane member 15, a rotation restricting means 34 for restricting relative rotation between the housing member 4 and the vane member 15 is provided. In this embodiment, the rotation restricting means 34 is an engagement member provided so as to protrude in the axial direction of the vane member 15 by being housed together with a spring member 36 in a cylinder hole 35 formed in the vane member 15. The tip of 37 is configured to be engageable with an engagement hole 38 provided in the housing member 4 (the plate member 7 ).

  The cylinder hole 35 is formed through the vane member 15, specifically, one of the vanes 18 having a larger circumferential width of the vane member 15 in the axial direction. A spring receiver 39 for the spring member 36 is press-fitted and fixed to one open end of the cylinder hole 35, and the spring receiver 39 is preferably made of a material harder than the vane 18. Further, a notch groove 40 for venting air is provided at a predetermined position on the outer peripheral side of the spring receiver 39, and this notch groove 40 is a radial groove provided on the side surface of the trunk portion 17 of the vane member 15. 41 is communicated. As a result, the inside of the cylinder hole 35 located on the rear end side of the engagement member 37 is opened to the atmosphere via the notch groove 40 and the groove 41 on the opening end side.

  The engaging member 37 has a tapered tip end, and the tapered leading end can protrude from the cylinder hole 35. Further, the engaging member 37 has a recess 42 formed at the tip thereof, and a blind hole 43 opened at the end face on the rear end side, thereby reducing the weight.

  In this embodiment, the engagement hole 38 is made of a material harder than the housing member 4 (the plate member 7), and the engagement hole member 44 in which the engagement hole 38 is formed is replaced with the housing member 4. It is formed by being embedded in (the plate member 7).

  The shape of the engagement hole 38 is formed in a cup shape having a large diameter on the opening end side, 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 is like that. The engagement hole 38 and the oil chamber 45 communicate with the hydraulic oil chamber 19 through oil holes 46 formed in the plate member 7 and the engagement hole member 44.

  The camshaft 1 inserted into the hole 27 formed in the vane member 15 has hydraulic side passages 51 and 52 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 communicate with hydraulic pressure suction / discharge means described later.

  That is, the hydraulic-side passage 51 is formed in a blind hole shape in which the tip end side does not open in the axial direction from the end surface 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 communicating with the radial passage 53 on the opening end side. Further, the hydraulic side passage 51 communicates with a hydraulic intake / exhaust means, which will be described later, via a radial passage 55 branched from the hydraulic side passage 51 and a circumferential groove 56 through which the radial passage 55 communicates. (See FIG. 3).

  Further, the hydraulic side passage 52 is formed in a blind hole shape in which the tip end side does not open in the axial direction from the end face of the camshaft 1, 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 thereof and a circumferential groove 59 through which the radial passage 58 communicates. . Further, the hydraulic side passage 52 communicates with a hydraulic intake / exhaust means, which will be described later, through a radial passage 60 branched from the hydraulic passage 52 and a circumferential groove 61 with which the radial passage 60 communicates at the distal end side. (See FIG. 3).

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

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

  In such a configuration, when the internal combustion engine is started, when the 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, the 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). 4 and the vane member 15 are connected. For this reason, the rotational driving force applied to the sprocket 3 from the crankshaft (not shown) 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 is not in contact with the side surface of the protrusion 12 that forms the chamber 13 in the housing member 4.

  As the camshaft 1 rotates, the intake valve of the internal combustion engine is driven and open / close controlled.

  When the vane member 15 is at the most retarded position with respect to the housing member 4, the engaging member 37 of the rotation restricting means 34 is pressed by the spring member 36, and the tip thereof engages with the engaging 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 reversal torque acts on the camshaft 1. Therefore, it is advantageously prevented that the vane 18 of the vane member 15 abuts against the side surface of the protrusion 12 to generate a hitting 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, and the supply passage 70 from the oil pump 69 is connected to the supply / discharge passage 67 and the supply / discharge passage 67 is connected. By connecting the discharge passage 68 to the discharge passage 72, hydraulic oil from the oil pump 69 passes from the supply / discharge passage 67 to the circumferential groove 56, the radial direction passage 55, the hydraulic side passage 51, the radial direction passage 53, and the circumferential groove 54. And it is led into the hydraulic oil chamber 19 through the oil chamber side passage 25. Further, the hydraulic oil introduced into the hydraulic oil chamber 19 passes through the oil holes 46 formed in the plate member 7 and the engagement hole member 44, and the engagement oil 37 is engaged in the engagement holes 38. And it is led into an oil chamber 45 formed at the bottom of the engagement hole 38.

  At the same time, the inside of the hydraulic oil chamber 20 enters the discharge passage 72 via the oil chamber side passage 26, the circumferential groove 59, the radial direction passage 58, the hydraulic pressure side passage 52, the radial direction passage 60, the circumferential groove 61 and the supply / discharge passage 68. You will communicate.

  When the hydraulic oil is introduced into the hydraulic oil chamber 19 and the engagement hole 38 (and the oil chamber 45) of the rotation restricting means 34, 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 biased toward the spring receiver 39 against the spring force of the spring member 36 and is pushed back into the cylinder hole 35. For this reason, the front end of the engagement member 37 is released from the engagement hole 38 and the engagement is released, whereby the housing member 4 and the vane member 15 are released from the restraint by the engagement member 37.

  While the hydraulic oil is supplied into the hydraulic oil chamber 19 and the hydraulic oil chamber 20 communicates with the discharge passage 72, the hydraulic pressure in the hydraulic oil chamber 19 acts on the side surface of the vane 18, 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 relative to each other, the rotational phase of the camshaft 1 with respect to the crankshaft is changed, and the camshaft 1 is controlled to advance and driven by the camshaft 1. The opening and closing timing of the intake valve is advanced.

  When the camshaft 1 is controlled to advance, and the vane member 15 rotates relative to the housing member 4 and is at the most advanced position, the engagement member 37 is cylinder bore 35 by the hydraulic pressure in the hydraulic oil chamber 19. The state of being pushed back in continues, and the tip of the engaging 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 to be switched by the control device 74, the supply passage 70 from the oil pump 69 is connected to the supply / discharge passage 68, and the supply / discharge passage 67 is connected 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 side 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 direction passage 53, the hydraulic pressure side passage 51, the radial direction passage 55, the circumferential groove 56, the intake / exhaust passage 67 and the discharge passage 72. It 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, but the tip of the engaging member 37 is In a state where the engagement hole 38 is not engaged, the housing member 4 and the vane member 15 are continuously released from the restraint by the rotation restricting means 34.

  While hydraulic fluid is supplied into the hydraulic fluid chamber 20, the hydraulic fluid chamber 19 communicates with the discharge passage 72, whereby the hydraulic pressure in the hydraulic fluid chamber 20 acts on the side surface of the vane 18, and the vane member 15. 2 is rotated counterclockwise in FIG. As a result, the sprocket 3 and the camshaft 1 rotate relative to each other, the rotational phase of the camshaft 1 relative to the crankshaft is changed, and the camshaft 1 is retarded again and driven by the camshaft 1. The timing of opening and closing the intake valve is delayed.

  When the camshaft 1 is retarded and the vane member 15 rotates relative 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. Re-engaged in the hole 38.

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

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

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

  For this reason, the possibility that the sprocket 3 may cause poor lubrication at the meshing portion with the timing chain 10 is advantageously prevented.

  Therefore, a valve timing device that can effectively prevent poor lubrication of the sprocket 3 is obtained.

  Further, since the sprocket 3 is provided at a position farther from the camshaft 1 than the axial center of the housing member 4, it is possible to prevent the valve timing device from swinging due to misalignment or imbalance. That is, since the vane member 15 is attached to the end portion of the camshaft 1 in the valve timing device, there is a risk of swinging if there is a misalignment or imbalance in the attachment, but in this embodiment the sprocket 3 The timing chain 10 wound around the valve shaft 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 swinging. As a result, swinging can be prevented.

  The housing member 4 includes a substantially cylindrical housing main body 5 provided with the sprocket 3, and plate members 6 and 7 that seal both end sides of the housing main body 5. The sprocket 3 is the housing main body 5. The housing body 5 can be easily formed by being provided at substantially the center position in the axial direction. That is, since the housing body 5 provided with the sprocket 3 has a symmetrical shape with respect to the axial center line, the mold shape is simplified during the sintering process, and the density variation 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 main body 5 provided with the sprocket 3 and plate members 6 and 7 for sealing both end sides of the housing main body 5. The sprocket 3 and the housing main body 5 Since only the sintered metal is formed, the hydraulic oil guided to the hydraulic 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 hydraulic oil does not penetrate into the plate members 6 and 7 and effectively penetrates into the sprocket 3 and the housing body 5. is there.

  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 end sides of the housing main body 5. Since the inside of the member 4 is accommodated so as to be relatively rotatable and the vane 18 is formed inside the housing member 4 to form a plurality of hydraulic oil chambers 19 and 20 in the circumferential direction, the hydraulic oil chambers 19 and 20 are shafts. It is formed relatively long in the direction, and the degree of freedom of arrangement of the sprocket 3, that is, the degree of freedom of 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 gist of the invention. For example, the first rotating body is the housing member 4, the second rotating body is accommodated in the housing member 4 so as to be relatively rotatable, and a plurality of hydraulic oil chambers 19 are arranged in the circumferential direction inside the housing member 4. Although the embodiment of the housing member 4 having the vane 18 forming 20 has been described, the first rotating body and the second rotating body are connected by a helical gear, and the helical gear is connected to the first rotating gear. It is good also as a structure which makes a 1st rotary body and a 2nd rotary body rotate relatively by act | operating with the hydraulic fluid guide | induced to the hydraulic oil chamber formed between the 1st rotary body and the 2nd rotary body.

  Moreover, although the embodiment for controlling the advance angle of the camshaft 1 has been described, it can also be adopted in a valve timing changing device for controlling the retard angle.

BRIEF DESCRIPTION OF THE DRAWINGS Explanatory drawing which shows the principal part of the valve timing apparatus of the internal combustion engine which shows embodiment of this invention in cross section. FIG. 2 is a cross-sectional view taken along line AA in FIG. 1 and showing a bolt removed. Sectional drawing which expands and shows the principal part of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Cam shaft 3 ... Sprocket 4 ... Housing member (1st rotary 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 intake / exhaust means

Claims (5)

It is provided between the camshaft driving sprocket and the intake valve or an exhaust valve which is in synchronization with rotation to the rotation of the internal combustion engine, the intake valve or the exhaust valve by relatively rotating the camshaft relative to the sprocket A valve timing changing device for an internal combustion engine capable of changing the opening and closing timing,
A substantially cylindrical housing body that rotates with the sprocket and has a plurality of protrusions on the inner periphery ;
A first plate member for sealing the camshaft side of the housing body;
Sealing the opposite side of the housing body from the camshaft, and a second plate member having a plate thickness thinner than the first plate member ;
A housing member formed by connecting the housing body and the first and second plate members from the axial direction with bolts ;
A vane provided inside the housing member so as to be rotatable relative to the housing member, and forming a plurality of working chambers between the protrusions ,
Forming the housing body from a porous material;
A valve timing control device for an internal combustion engine , wherein a female screw hole into which a tip of the bolt is screwed is formed at a predetermined position on an outer peripheral portion of the first plate member . The sprocket is integrally formed on the outer periphery of the housing body, the sprocket is formed of a porous material, and the second plate member is formed of a non-porous material. A valve timing control device for an internal combustion engine as described. The valve timing control device for an internal combustion engine according to claim 2, wherein the second plate member is formed of a steel plate . Provided between a sprocket that rotates in synchronization with the rotation of the internal combustion engine and a camshaft that drives an intake valve or an exhaust valve, and opens and closes the intake valve or exhaust valve by rotating the camshaft relative to the sprocket. In the internal combustion engine valve timing changing device capable of changing the timing,
A housing body that rotates with the sprocket and is formed of a substantially cylindrical porous material having a plurality of protrusions on the inner periphery;
A first plate member for sealing the camshaft side of the housing body;
Sealing the opposite side of the housing body from the camshaft, and a second plate member having a plate thickness thinner than the first plate member;
A housing member formed by connecting the housing body and the first and second plate members from the axial direction with bolts;
A vane provided in the housing member so as to be rotatable relative to the housing member, and forming a plurality of working chambers between the protrusions;
An engagement member housed in the vane and urged by a spring member to protrude in the axial direction, and the first plate member embedded in the first plate member and locking the engagement member A harder engagement hole member, and the engagement member is engaged with or released from the engagement hole member to restrict or restrict relative rotation between the housing member and the vane. A rotation restricting means for releasing,
A valve timing control device for an internal combustion engine , wherein a female screw hole into which a tip of the bolt is screwed is formed in the first plate member . The internal combustion engine according to any one of claims 1 to 4, wherein the porous material is formed of a sintered metal that permeates and holds the hydraulic oil under pressure and centrifugal force in the hydraulic oil. Valve timing control device.

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