JP4013155B2 - 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 rotating body that is rotationally driven by a crankshaft of an internal combustion engine and a camshaft that drives an intake valve or an exhaust valve, and rotates the camshaft relative to the rotating body. The opening / closing timing of the intake valve or the exhaust valve is changed by moving.

  For example, Japanese Patent Laid-Open No. 1-92504 discloses a housing that rotates with a rotating body that is rotated by a crankshaft of an internal combustion engine, a rotor that is housed in the housing and rotates with a camshaft, and a radial direction to the rotor. A valve timing changing device provided with a plurality of vanes that are provided to project and form a plurality of hydraulic oil chambers in the housing, and that allows the hydraulic oil to be sucked into and discharged from the hydraulic oil chambers to rotate the housing and the rotor relative to each other. It is shown.

Further, in the above valve timing changing apparatus, the rotation restricting means for restricting relative rotation between the housing and the rotor are the eclipsed set, the rotation restricting means is provided slidably knock pins into the housing, the The knock pin is urged in the centripetal direction by the spring force of the spring member and inserted into the hole provided in the rotor, thereby connecting the housing and the rotor to regulate the valve timing, while the knock pin is adjusted to the hydraulic pressure. By pushing out from the hole, the connection between the housing and the rotor is released, and the restriction on the change of the valve timing is released.

  In the conventional example, the knock pin of the rotation restricting means is provided at the tip of the projection formed to protrude radially inward in the housing, and this knock pin is formed in the centripetal direction by the spring force of the spring member. It is urged to be inserted into a hole provided on the outer periphery of the body of the rotor.

  For this reason, in the state before being inserted in the hole provided in the rotor, the said knock pin may contact | connect the outer periphery of the trunk | drum of a rotor, and there exists a possibility of damaging the outer periphery of this trunk | drum.

  When the outer periphery of the rotor as the sealing surface is damaged, the outer periphery of the body portion of the rotor is a sealing surface that should control sealing of the hydraulic oil chamber with the protrusion formed on the inner peripheral side of the housing. There is a possibility that the sealing of the hydraulic oil chamber is damaged, and the change of the valve timing is not smooth.

  The present invention has been devised in view of the above-described conventional situation, and provides a valve timing changing device for an internal combustion engine that can reliably change the valve timing without impairing the sealing of the hydraulic oil chamber. The purpose is to provide.

Accordingly, the invention described in claim 1 is provided between a rotating body that is rotated 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 connected to the rotating body. in the valve timing apparatus for an internal combustion engine to change the valve timing of the intake valve or the exhaust valve by relatively rotation of a housing member rotating either with one of said rotor and the camshaft, accommodated in the housing member A vane member having a vane that rotates together with one of the rotating body and the camshaft and projects in a radial direction to form a plurality of hydraulic oil chambers in a circumferential direction in the housing member; Alternatively, either one of the vane member, an engagement hole formed so as to open toward one of the hydraulic oil chambers, and either the housing member or the vane member The engagement member is provided so as to be able to protrude and retract so as to cross the hydraulic oil chamber, and the front end of the engagement member can be engaged with the engagement hole, and the engagement member is urged in the engagement direction with respect to the engagement hole. and a spring member, and a rotation restricting means for restricting the relative rotation of the rotor and the camshaft when the internal combustion engine is started, the inclined surfaces inclined from the engagement hole toward the working chamber side, And a distal end portion of the engaging member is in sliding contact with the inclined surface from the hydraulic oil chamber toward the engaging hole, and the engaging member engages with the engaging hole. and it is obtained so as to regulate the relative rotation of the vane member.

Further, an invention according to claim 2, wherein, in the configuration of the invention recited in claim 1, for said vane member is moved to the regulating position of the rotation restricting means relative to said housing member, said engaging member, It moves while being guided by the slope, and is configured to be engaged with the engagement hole.

In such a configuration, the rotating body is rotated in synchronization with the rotation of the internal combustion engine, and the camshaft is rotated via the valve timing changing device. Thus, the camshaft drive the intake valve or the exhaust valve.

  In addition, relative rotation of the camshaft with respect to the rotating body causes the hydraulic oil to be sucked into and discharged from the hydraulic oil chamber in the housing member that rotates together with either the rotating body or the camshaft, so that the housing member and the vane member are relatively This is done by turning. In this case, the intake and discharge of the hydraulic oil to and from the hydraulic oil chamber can be controlled by a hydraulic control device.

  By rotating the camshaft relative to the rotating body, the rotational 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.

  Here, immediately after the start of the internal combustion engine, when the hydraulic oil is not supplied to the hydraulic oil chamber, the engaging member of the rotation restricting means protrudes in the engaging direction due to centrifugal force, spring force, etc., and its tip is engaged. Engage with the hole. For this reason, the rotary body and the camshaft are maintained in a predetermined engagement state by the engagement member, and rotate integrally. This state is a state in which the relative rotation between the rotating body and the camshaft is restricted by the rotation restricting means, and the change in valve timing is restricted.

  Next, by moving the engaging member of the rotation restricting means in the disengaging direction opposite to the engaging direction, the tip of the engaging member is detached from the engaging hole, and the engaging member and the engaging hole Is disengaged.

  The engagement of the rotation restricting means is released by supplying the hydraulic oil to the hydraulic oil chamber that the engagement hole faces, so that the hydraulic oil is also supplied into the engagement hole. For this reason, the hydraulic pressure in the hydraulic oil chamber and the engagement hole acts on the engagement member, and the engagement member is urged in the centripetal direction against the centrifugal force and the spring force, and from the engagement hole. It will be pushed out. As a result, the tip of the engagement member is released from the engagement hole, and the engagement is released.

Thus, the because the housing member and the vane member Ru is released restraint by engaging member and the housing member and the vane member by the hydraulic pressure supplied to the hydraulic oil chamber is relative rotation, the cam for rotating the internal combustion engine By changing the rotational phase of the shaft, the opening / closing timing of the intake valve or exhaust valve driven by the camshaft is changed.

  Here, the rotation restricting means is provided in the stepped portion provided in the housing member or the vane member in the engagement hole formed in one of the stepped portion provided in the housing member or the stepped portion provided in the vane member. The tip of an engaging member provided so as to be able to protrude and retract in the radial direction on either one of the stepped portions is engageable.

  As a result, the engagement member of the rotation restricting means has an engagement hole formed at the tip of the engagement member before engaging with the engagement hole formed in the step portion of the housing member or the step portion of the vane member. Even if it contacts the stepped portion, it does not contact the inner periphery of the housing member or the outer periphery of the body portion of the vane member, which is the sealing surface of the hydraulic oil chamber.

  For this reason, since the inner periphery of the housing member and the outer periphery of the body portion of the vane member are not damaged, the sealing of the hydraulic oil chamber is not impaired, and the valve timing can be changed smoothly.

  Therefore, a valve timing changing device for an internal combustion engine that can reliably change the valve timing without losing the sealing of the hydraulic oil chamber is obtained.

  Further, in the present invention, the engagement hole of the rotation restricting means is formed in the step portion of the housing member, and the engagement member is provided in the step portion of the vane member so as to protrude in the radial direction. And when a vane member rotates, the centrifugal force which acts on an engagement member acts in the direction which makes the front-end | tip of an engagement member engage with an engagement hole. For this reason, when a centrifugal force acts on the engaging member, the engaging member does not come out of the engaging hole, and there is no possibility that the restriction on the change of the valve timing is unintentionally released.

  Further, in the present invention, the engaging member is provided in the stepped portion of the vane member so as to be able to protrude and retract in the radial direction, and a tip of the engaging member protrudes across the hydraulic oil chamber and is provided in the housing member to provide the hydraulic oil. By enabling engagement with the engagement hole through which the hydraulic oil in the chamber is guided, the hydraulic pressure in the hydraulic oil chamber can be directly applied to the engagement member, and the engagement member can be quickly operated.

  In the present invention, the engagement hole is formed of an engagement hole member embedded in the stepped portion of the vane member or the stepped portion of the housing member. It can be easily formed into a predetermined shape, and the degree of freedom in designing and manufacturing the engagement hole can be increased.

Further, in the present invention, by the cylinder bore is formed by a stepped portion or the cylinder bore member was set embedded in the stepped portion of the housing member of the vane member, a predetermined cylinder bore member of any material shape Therefore, it is possible to increase the degree of freedom in designing and manufacturing the cylinder hole.

  In the present invention, the step portion in which the engagement hole is formed is formed with an inclined surface inclined toward the hydraulic oil chamber side, so that the inclined surface is arranged so that the tip of the engagement member is formed. By guiding, the tip of the engaging member is easily engaged with the engaging hole.

  In the present invention, the engagement member is provided with a spring member for urging the engagement member in the engagement direction, so that the rotation of the internal combustion engine can be performed at an extremely low speed or at a stop. Even when the centrifugal force acting on the engagement member is extremely small or zero, the engagement member can be reliably engaged with the engagement hole.

  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 according to an embodiment of the present invention, and FIG. 2 is an explanatory view including a cross-sectional view taken along line A-0-A of FIG.

  In the figure, reference numeral 1 denotes a camshaft, and this camshaft 1 is a camshaft that drives 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 fixed to a cylinder head (not shown). Further, a cam is formed on the trunk (not shown) of the right camshaft 1 in FIG. 2 with respect to the non-illustrated bearing, and the intake valve is driven to open and close by this cam. .

Reference numeral 2 denotes a spider extending from the front cover (not shown) side of the internal combustion engine. At the end of the spider 2, axial passages 3 and 4 and circumferential grooves 5 and 6 positioned on the side close to the end face are respectively provided. It is formed. Although the passage 3 is open at the end face, it is arbitrarily possible to close the open end with a plug member.

  Of the passages 3 and 4, one end of the passage 3 communicates with the circumferential groove 5 via the radial passage 7. Further, the one end side of the passage 4 communicates with the circumferential groove 6 through the radial passage 8.

  Reference numeral 17 denotes a rotating body that rotates in synchronization with the internal combustion engine. In this embodiment, the rotating body 17 is a sprocket that is rotationally driven by a crankshaft (not shown) of the internal combustion engine. In this embodiment, the sprocket 17 can rotate together with the housing member 18 and can rotate relative to the camshaft 1 by a predetermined angle.

  That is, the sprocket 17 is connected to a housing member 18 comprising an annular housing main body 19 and plate members 20 and 21 disposed on opposite sides of the housing main body 19 by connecting bolts (not shown). . Reference numerals 22a and 22b denote positioning pins for positioning the sprocket 17, the housing body 19 and the plate members 20 and 21, respectively.

  Further, the sprocket 17 is supported on the outer periphery of a bearing member 25 fixed to the camshaft 1, and thereby can be rotated relative to the camshaft 1 by a predetermined angle.

  External teeth 26 are formed on the outer peripheral side of the sprocket 17, and a timing chain 27 driven by a crankshaft (not shown) is wound around the external teeth 26.

  The inside of the housing member 18 is hollow as a whole, and by forming a plurality (four in this embodiment) of protrusions 28 projecting radially inward of the annular housing body 19, Four chambers 29 connected at the central portion are formed on the outer side in the radial direction (see FIG. 1).

  Reference numeral 30 denotes a vane member accommodated in the housing member 18, and the relative rotation means 31, which will be described in detail later, is configured with the vane member 30 and the housing member 18 as main elements.

  The vane member 30 has a plurality (four in this embodiment) of vanes 33 projecting in the radial direction from the trunk portion 32, and the housing member in a state in which the vanes 33 are disposed in the chamber 29. 18.

By arranging the vane 33 of the vane member 30 in the chamber 29, a pair of hydraulic oil chambers 34 and 35 are defined in the chamber 29 so as to face both sides of the vane 33 in the circumferential direction.
The pair of hydraulic oil chambers 34 and 35 is formed in four sets in this embodiment.

  Sealing between the hydraulic oil chambers 34 and 35 is achieved by pressing the seal member 36 provided at the tip of the projection 28 formed on the inner peripheral side of the housing body 19 with a spring member (not shown). This is achieved by being brought into sliding contact with the outer periphery of the body portion 32 and pressing the seal member 38 provided at the tip of the vane 33 with the spring member 39 to be brought into sliding contact with the inner periphery of the housing body 19.

  The vane member 30 is formed with a radial passage 40 that communicates the circumferential groove 6 formed in the spider 2 and the hydraulic oil chamber 34, and also communicates the circumferential groove 5 and the hydraulic oil chamber 35. A radial passage 41 is formed.

  Since the circumferential grooves 6 and 5 communicating with the radial passages 40 and 41 respectively communicate with the passages 4 and 3 formed in the spider 2, the hydraulic oil chambers 34 and 35 are formed in the passage 4 formed in the spider 2. 3 to communicate with each other. For this reason, the housing member 18 and the vane member 30 can rotate relative to each other by selectively sucking and discharging the working oil into and from the working oil chambers 34 and 35 through the passages 4 and 3. .

  Here, the sprocket 17 is connected to the housing member 18 so as to be rotatable relative to the camshaft 1, whereby the relative rotating means 31 causes the sprocket 17 to move at a predetermined angle relative to the camshaft 1. Relative rotation is possible within the range. Accordingly, the relative rotation means 31 for rotating the sprocket 17 relative to the camshaft 1 is configured with the vane member 30 and the housing member 18 as main elements.

44 is provided between the housing member 18 and the vane member 30, a rotation restricting means for restricting relative rotation between the Haujin grayed member 18 and the vane member 30. In this embodiment, the rotation restricting means 44 is accommodated in a cylinder hole 45 formed in the vane member 30 so that the tip of an engagement member 47 provided in the vane member 30 so as to protrude radially is provided. The engagement hole 48 formed in the housing member 18 can be engaged.

  The cylinder hole 45 opens to the vane member 30, more specifically, a stepped portion 49 formed between the outer periphery of the body portion 32 of the vane member 30 and the vane 33, facing one of the hydraulic oil chambers 34 and opening in the radial direction. Formed. Further, in this embodiment, the cylinder hole 45 is formed by embedding a cylindrical cylinder hole member 50 made of a material harder than the vane member 30 in the step portion 49 of the vane member 30. is there. For this reason, the cylinder hole 45 has a stepped shape in which the diameter of the portion in which the cylinder hole member 50 is embedded is reduced and the diameter of the bottom portion is increased.

  The inside of the cylinder hole 45 is open to the atmosphere via a stepped hole-shaped passage 51 formed in the vane 33 on the bottom side.

  The engagement member 47 is formed in a stepped shape, the tip end side is formed in a taper shape, the large-diameter body portion is located on the bottom side where the diameter of the cylinder hole 45 is increased, and the small-diameter body portion is a cylinder hole member. It is accommodated in the cylinder hole 45 in a state supported by the inner surface of the cylinder 50, and the tapered tip end side can protrude from the cylinder hole 45. When the front end of the engaging member 47 protrudes from the cylinder hole 45, the large diameter body portion of the engaging member 47 is positioned on the bottom side where the diameter of the cylinder hole 45 is increased, so that the step of the engaging member 47 is performed. The attached portion abuts on the cylinder hole member 50 of the cylinder hole 45 and can prevent the engaging member 47 from being pulled out of the cylinder hole 45.

  Since the engaging member 47 is accommodated in the cylinder hole 45 facing one of the hydraulic oil chambers 34, the distal end of the engaging member 47 protrudes in a radial direction across one of the working chambers 34. The joint hole 48 is engaged.

  The engaging member 47 has a recess 52 formed at the tip thereof, and a blind hole 53 that opens to the end surface on the large diameter body side. Thereby, the engaging member 47 is reduced in weight.

  The engagement hole 48 is formed in the housing member 18, specifically, in a step portion 54 formed between the inner periphery of the housing main body 19 and the projection 28 so as to open to face one of the hydraulic oil chambers 34. It is. Further, in this embodiment, the engagement hole 48 is made of a material harder than the housing body 19, and the engagement hole member 55 formed with the engagement hole 48 is replaced with the step 54 of the housing body 19. It is formed by embedding in.

  The shape of the engagement hole 48 is a cup shape having a large diameter on the opening end side, and an oil chamber 56 is formed at the bottom of the engagement hole 48 in a state where the engagement member 47 is engaged. Yes. The engagement hole 48 and the oil chamber 56 have an oil groove 57 formed on the inner surface of the engagement hole 48 and an arc shape between the step portion 49 of the vane member 30 and the step portion 54 of the housing member 18. The hydraulic fluid chamber 34 communicates with the gap 58.

  It is sufficient that the oil groove 57 is formed in a state where the engaging member 47 is engaged. Therefore, the depth at which the tapered tip of the engaging member 47 enters the engaging hole 48 is adjusted. Thus, it is possible to form between the inner surface of the engagement hole 48 and the outer surface of the engagement member 47.

  Further, an inclined surface 59 that is inclined toward the hydraulic oil chamber 34 is formed in the step portion 54 in which the engagement hole 48 is formed, that is, the step portion 54 formed in the housing member 18 in this embodiment. It is.

  66 is a hydraulic supply / discharge means. The hydraulic supply / discharge means 66 includes supply / discharge passages 67, 68 communicating with the passages 3, 4, and a discharge passage 72 communicating these supply / discharge passages 67, 68 with the supply passage 70 from the oil pump 69 and the oil storage tank 71. A switching valve 73 for selectively switching to or disconnecting from each other and a control device 74 for controlling the switching valve 73 are configured as main elements. The switching valve 73 is a four-port valve in this embodiment, and 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 30 of the means 31 is at the most retarded position with respect to the housing member 18 (see FIG. 1), and the distal end of the engaging member 47 of the rotation restricting means 44 engages with the engaging hole 48, and the housing member 18 and the vane member 30 are connected. Therefore, the rotational driving force applied to the sprocket 17 from the crankshaft (not shown) via the timing chain 27 is transmitted to the camshaft 1 via the housing member 18 and the vane member 30. In this case, the stepped portion 49 of the vane member 30 can be brought into contact with the side surface of the projection 28 forming the chamber 29 in the housing member 18, but preferably, the vane 33 is not in contact with the projection 28. .

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

  When the vane member 30 is at the most retarded position with respect to the housing member 18, the engagement member 47 of the rotation restricting means 44 is pressed by the centrifugal force, and the tip thereof engages with the engagement hole 48. The relative rotation between the housing member 18 and the vane member 30 is restricted. Therefore, when the camshaft 1 drives an intake valve (not shown), the vane member 30 rotates relative to the housing member 18 even if a positive or negative reversal torque acts on the camshaft 1. Therefore, it is advantageously prevented that the stepped portion 49 or the vane 33 of the vane member 30 abuts against the side surface of the protrusion 28 to generate a hitting sound or the like.

Next, when the advance angle control is performed, the switching valve 73 of the hydraulic supply / exhaust 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, By connecting the discharge passage 67 to the discharge passage 72, the hydraulic oil from the oil pump 69 is supplied from the supply / discharge passage 68 through the passage 4, the radial passage 8, the circumferential groove 6, and the radial passage 40. 34 is led. Further, the hydraulic oil introduced into the working oil chamber 34 via a circular arc shape gap 58, and the oil groove 57, engaging hole within 48 the tip of the engaging member 47 is engaged (and the engagement hole 4 8 In the oil chamber 56 provided at the bottom of the oil.

  At the same time, the inside of the hydraulic oil chamber 35 communicates with the discharge passage 72 through the radial passage 41, the circumferential groove 5, the radial passage 7, the passage 3, and the supply / discharge passage 67.

  When the hydraulic oil is introduced into the hydraulic oil chamber 34 and into the engagement hole 48 (oil chamber 56) of the rotation restricting means 44, the hydraulic oil in the hydraulic oil chamber 34 and the engagement hole 48 is supplied to the engagement member 47. Pressure is applied, and the engaging member 47 is urged in the centripetal direction against the centrifugal force and pushed back into the cylinder hole 45. For this reason, the front end of the engagement member 47 is released from the engagement hole 48 and the engagement is released, whereby the housing member 18 and the vane member 30 are released from the restraint by the engagement member 47.

  While the hydraulic oil is supplied into the hydraulic oil chamber 34, the hydraulic oil chamber 35 communicates with the discharge passage 72, whereby the hydraulic pressure in the hydraulic oil chamber 34 acts on the side surface of the vane 33, and the vane member 30. Is rotated in the direction of the arrow in FIG. As a result, the sprocket 17 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 advanced and the vane member 30 is at the most advanced position relative to the housing member 18, the engaging member 47 is pushed back into the cylinder hole 45 by the hydraulic pressure in the hydraulic oil chamber 34. The state continues, and the tip of the engagement member 47 does not contact the inner periphery of the housing member 18.

  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 67, and the supply / discharge passage 68 is connected to the discharge passage 72. Then, the hydraulic oil from the oil pump 69 is guided to the hydraulic oil chamber 35. The hydraulic oil in the hydraulic oil chamber 34 is discharged to the oil storage tank 71 through the intake / exhaust passage 68 and the discharge passage 72.

When the hydraulic oil in the hydraulic oil chamber 34 is discharged, the engaging member 47 protrudes in the radial direction by the centrifugal force acting on the engaging member 47, but the distal end of the engaging member 47 is the housing member 18. No contact with the inner circumference of Further, when the engaging member 47 is closer to the hydraulic oil chamber 34 than the stepped portion 54 of the housing main body 19, the engaging member 47 does not engage with the engaging hole 48. The state where the restriction by the rotation restricting means 44 is released is continued.

  While the hydraulic oil is supplied into the hydraulic oil chamber 35 and the hydraulic oil chamber 34 communicates with the discharge passage 72, the hydraulic pressure in the hydraulic oil chamber 35 acts on the side surface of the vane 33, and the vane member 30. Is rotated counterclockwise, that is, retarded in FIG. As a result, the sprocket 17 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 and driven by the camshaft 1. The timing of opening and closing the intake valve is delayed.

Wherein the cam shaft 1 is retarded angle control, when the vane member 30 is most retarded position relative to the housing member 18, the distal end of the engaging member 47 which has been projected to the hydraulic oil chamber 34, the housing member 18 It moves while being guided by the inclined surface 59 formed in the stepped portion 54, and is engaged again in the engagement hole 48.

  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 30 is rotated in the advance direction or the retard direction with respect to the housing member 18, so that the supply / discharge passage is provided. 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 18 and the vane member 30 are held at an intermediate position of relative rotation. As a result, the first sprocket 17 and the camshaft 1 are held at an intermediate position of relative rotation, and the camshaft 1 moves the intake valve driven by the camshaft 1 at a desired timing. To control.

  In this case, the inside of the hydraulic oil chamber 34 is maintained in a predetermined pressure state and is in a sealed state, so that centrifugal force acts on the engagement member 47. Since the member 47 does not protrude in the radial direction and does not engage with the engagement hole 48, the housing member 18 and the vane member 30 continue to be released from the restraint by the rotation restricting means 44. The

  Here, in this embodiment, the rotation restricting means 44 is provided in the engagement hole 48 formed in the step portion 54 of the housing member 18 so as to protrude in the radial direction at the step portion 49 of the vane member 30. The tip of the joint member 47 can be engaged.

  As a result, the engagement member 47 of the rotation restricting means 44 is formed with an engagement hole 48 at its tip before engaging with the engagement hole 48 formed in the step portion 54 of the housing member 18. Even if it contacts the stepped portion 54, it does not contact the inner periphery of the housing member 18 or the outer periphery of the trunk portion 32 of the vane member 30, which is the sealing surface of the hydraulic oil chambers 34 and 35.

  For this reason, since the inner periphery of the housing member 18 and the outer periphery of the body portion 32 of the vane member 30 are not damaged, the sealing of the hydraulic oil chambers 34 and 35 is not impaired, and the valve timing can be changed smoothly. Will be done.

  Therefore, a valve timing changing device for an internal combustion engine that can reliably change the valve timing without losing the sealing of the hydraulic oil chambers 34 and 35 is obtained.

Further, the engaging hole 48 of the rotation restricting means 44 is formed in the stepped portion 54 of the housing member 18, since the engagement member 47 is kicked set to be projected in a radial direction in the stepped portion 49 of the vane member 30 When the housing member 18 and the vane member 30 rotate, the centrifugal force acting on the engagement member 47 acts in a direction in which the tip of the engagement member 47 is engaged with the engagement hole 48. For this reason, when a centrifugal force acts on the engaging member 47, the engaging member 47 does not come out of the engaging hole 48, and there is no possibility that the restriction on the change of the valve timing is unintentionally released.

  Further, the engaging member 47 is provided on the stepped portion 49 of the vane member 30 so as to project radially, and the tip of the engaging member 47 projects across the hydraulic oil chamber 34 and is provided on the stepped portion 54 of the housing member 18. Since the hydraulic oil can be engaged with the engagement hole 48 through which the hydraulic oil is guided, the hydraulic pressure of the hydraulic oil chamber 34 can be directly applied to the engagement member 47, and the engagement member 47 can be quickly operated. Become.

  Further, since the engagement hole 48 is formed by the engagement hole member 55 embedded in the stepped portion 54 of the housing member 18, the engagement hole member 55 is easily formed into a predetermined shape from any material. The degree of freedom in designing and manufacturing the engagement hole 48 can be increased.

  Further, since the engagement hole member 55 is formed of a material whose hardness is harder than that of the housing member 18, wear of the engagement hole 48 can be suppressed and durability can be improved.

  Further, since the cylinder hole 45 is formed by the cylinder hole member 50 embedded in the stepped portion 49 of the vane member 30, the cylinder hole member 50 can be easily formed from an arbitrary material into a predetermined shape. The degree of freedom in designing and manufacturing the hole 45 can be increased.

  In addition, since the cylinder hole member 50 is formed of a material that is harder than the vane member 30, wear of the cylinder hole 45 can be suppressed and durability can be improved.

  Further, since the stepped portion 54 in which the engagement hole 48 is formed has an inclined surface 59 inclined toward the hydraulic oil chamber 34 side, the inclined surface 59 guides the tip of the engagement member 47. Thus, the tip of the engagement member 47 is easily engaged with the engagement hole 48.

  FIG. 3 is a drawing showing another embodiment of the present invention. This embodiment is different from the above embodiment in that the engagement member 47 is disposed on the engagement member 47 of the rotation restricting means 44 in the radial direction. This is the point that the spring member 46 for biasing is attached.

  That is, the rotation restricting means 44 of the embodiment shown in FIG. 3 is provided in the stepped portion 49 of the vane member 30 so as to protrude in the radial direction by being accommodated in the cylinder hole 45 formed in the vane member 30. The distal end of the engagement member 47 is configured to be engageable with an engagement hole 48 formed in the step portion 54 of the housing member 18, and the engagement member 47 is radiated into the cylinder hole 45 together with the engagement member 47. The spring member 46 that biases in the direction is accommodated.

  The spring member 46 is in contact with the bottom portion of the cylinder hole 45 and the other end is in contact with the bottom portion of the blind hole 53 formed in the engagement member 47 so as to constantly bias the engagement member 47 in the radial direction. In addition, although the coil spring is employ | adopted in this embodiment as the said spring member 46, not only this but various spring members are employable.

  Since other configurations are the same as those in the above-described embodiment, the same components are denoted by the same reference numerals, and redundant description thereof is omitted.

  In such a configuration, the engaging member 47 of the rotation restricting means 44 is always urged in the radial direction by the spring force of the spring member 46. In other words, the spring force of the spring member 46 acts on the engagement member 47 in addition to the centrifugal force.

  Therefore, in such a configuration, in addition to the same operation and effect as the above-described embodiment, the engagement member 47 is attached with a spring member 46 that urges the engagement member 47 in the radial direction. Therefore, even when the rotation of the internal combustion engine is at an extremely low speed or when the engine is stopped and the centrifugal force acting on the engagement member 47 is extremely small or zero, the engagement member 47 is inserted into the engagement hole 48. Can be reliably engaged.

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 rotation restricting means 44 is engaged with the engaging hole 48 formed in the stepped portion 54 of the housing member 18 and the tip of the engaging member 47 provided in the stepped portion 49 of the vane member 30 so as to be able to protrude and retract in the radial direction. Although the configuration that can be combined has been described, the engagement hole 48 may be formed in the step portion 49 of the vane member 30 and the engagement member 47 may be provided in the step portion 54 of the housing member 18.

  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.

  The present invention provides a valve timing changing device for an internal combustion engine that can reliably change the valve timing without impairing the sealing of the hydraulic oil chamber. Or it is suitable for the valve timing change apparatus etc. for changing the opening / closing timing of an exhaust valve.

It is 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. It is explanatory drawing containing the AOA line sectional drawing of FIG. It is drawing similar to FIG. 1 which shows another embodiment of this invention.

Explanation of symbols

1 Camshaft 17 Sprocket (Rotating body)
18 housing member 28 projection 30 vane member 31 relative rotation means 33 vanes 44 turn restricting means 47 engaging member 48 engaging hole 49 step portion 54 step portion

Claims (2)

A rotating body which is rotated in synchronism with the rotation of the internal combustion engine, provided between the cam shaft for driving the intake valves or the exhaust valves, the intake valve or the exhaust by relatively Rotation of the cam shaft relative to the rotary member In a valve timing changing device for an internal combustion engine that changes the opening / closing timing of a valve,
A housing member that rotates together with either the rotating body or the camshaft;
The vane is housed in the housing member, rotates with any one of the rotating body and the camshaft, and protrudes in the radial direction to form a plurality of hydraulic oil chambers in the circumferential direction in the housing member. A vane member;
Either the housing member or the vane member has an engagement hole formed so as to open toward one of the hydraulic oil chambers, and either the housing member or the vane member crosses the hydraulic oil chamber. An engagement member which is provided so as to be able to protrude and retract and whose front end is engageable with an engagement hole; and a spring member which urges the engagement member in an engagement direction with respect to the engagement hole. a rotation restricting means for restricting the relative rotation of the rotor and the camshaft at starting,
An inclined surface inclined from the engagement hole toward the working chamber side,
The distal end portion of the engagement member is in sliding contact with the inclined surface from the hydraulic oil chamber toward the engagement hole, and the engagement member engages with the engagement hole, whereby the housing member and the vane member characterized in that the the to regulate the relative rotation of the valve timing apparatus for an internal combustion engine. While the vane member moves to the restriction position of the rotation restriction means with respect to the housing member, the engagement member moves while being guided by the slope and is engaged with the engagement hole. valve timing apparatus for an internal combustion engine 請 Motomeko 1, wherein.

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