JP4013157B2 - 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 rotated by a crankshaft of an internal combustion engine and a camshaft that drives an intake valve or an exhaust valve, and the camshaft rotates relative to the rotating body. Thus, the opening / closing timing of the intake valve or the exhaust valve is changed.

  For example, JP-A-1-92504 discloses a housing that rotates together with a sprocket (rotating body) rotated by a crankshaft of an internal combustion engine, a rotor that is housed in the housing and rotates together with a camshaft, A valve that protrudes in the radial direction and includes a plurality of vanes that form a plurality of hydraulic oil chambers in the housing, and the hydraulic oil is sucked into and discharged from the hydraulic oil chambers to rotate the housing and the rotor relative to each other. A timing change device is shown.

  Further, the valve timing changing device is provided with a rotation restricting means for restricting the relative rotation between the housing and the rotor, and the rotation restricting means can freely slide a knock pin (engagement member) on the housing. 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 change in valve timing, while the knock pin is By pushing out from the hole by the pressure of the hydraulic oil, 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 (engagement member) of the rotation restricting means is provided in the housing, and this knock pin is urged in the centripetal direction by the spring force of the spring member and is located in the hole provided in the rotor. It is supposed to be inserted.

  Therefore, when the rotor rotates and a centrifugal force acts on the knock pin, the knock pin comes out of the hole provided in the rotor against the spring force, and the restriction on the change of the valve timing is released unintentionally. There is a risk. That is, when the knock pin comes out of the hole provided in the rotor, the housing and the rotor, that is, the sprocket and the camshaft can be rotated relative to each other.

  The present invention has been devised in view of the above-described conventional situation, and there is no malfunction of the rotation restricting means, and the valve timing changing device for an internal combustion engine capable of reliably restricting and releasing the restriction of the valve timing. The purpose is to provide.

Accordingly, an invention according to 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 provided to the rotating body. A valve for an internal combustion engine that can be rotated to change the opening / closing timing of an intake valve or an exhaust valve, and includes a rotation restricting means for restricting relative rotation between the rotating body and the camshaft when the internal combustion engine is started. In the timing changing device, a housing member that is provided so as to rotate together with any one of the rotating body and the camshaft, and in which a protrusion forming a room is formed, and is accommodated in the housing member, the rotating body A vane member that rotates together with either the camshaft or the camshaft, and is provided to project in the radial direction of the vane member, and a plurality of hydraulic oil chambers are formed in the circumferential direction in the housing member. The number of vanes provided with a, the rotation restricting means, the engaging hole is formed so as to open facing the one of the hydraulic oil chamber a stepped portion provided in the housing member, said vane member The provided step portion is provided so as to be able to protrude and retract in the radial direction, and an engagement member whose front end crosses the hydraulic oil chamber can be engaged with the engagement hole, and urges the engagement member in the engagement hole direction. A spring member and an oil chamber for releasing the engagement member from the engagement hole when the hydraulic oil from the oil pump is guided are provided.

According to a second aspect of the present invention, in the configuration of the first aspect of the present invention, the step portion of the vane member is configured not to contact a side surface of the projection of the housing member .

  According to a third aspect of the present invention, in the configuration of the first or second aspect of the present invention, a gap is formed between the step portion of the vane member and the step portion of the housing member. The configuration is as follows.

  In such a configuration, the rotating body is rotated in synchronization with 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.

  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. This is done by relative rotation. 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 is changed, and as a result, the opening / closing timing of the intake valve or the exhaust valve is changed.

  Here, immediately after the start of the internal combustion engine, in a state where the hydraulic oil is not supplied to the hydraulic oil chamber, the engaging member of the rotation restricting means protrudes in the radial direction by the centrifugal force, and the tip thereof engages with the engaging hole. ing. 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 engagement member of the rotation restricting means in the centripetal direction, the tip of the engagement member is detached from the engagement hole, and the engagement between the engagement member and the engagement hole is released. .

  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. Therefore, the hydraulic oil 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 pushed out from the engagement hole. It will be. As a result, the tip of the engagement member is released from the engagement hole, and the engagement is released.

  When the housing member and the vane member are released from the restraint by the engaging member, the housing member and the vane member are relatively rotated by the hydraulic pressure supplied to the hydraulic oil chamber, and the rotational phase of the camshaft is changed. As a result, the opening / closing timing of the intake valve or the exhaust valve driven by the camshaft is changed.

  Here, the engaging member of the rotation restricting means is provided on the vane member so as to be able to project and retract in the radial direction, and its tip is engageable with an engaging hole provided in the housing member. 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.

  Further, the engaging member of the rotation restricting means is provided in the stepped portion of the vane member so as to be able to project and retract in the radial direction, and the tip thereof is engageable with an engaging hole provided in the stepped portion of the housing member. Therefore, when the housing member and the vane member rotate, the centrifugal force acting on the engagement member acts in a direction in which the tip of the engagement member is engaged with the engagement hole.

  Therefore, when the housing member and the vane member rotate and a centrifugal force acts on the engagement member, the engagement member does not come out of the engagement hole (a malfunction of the rotation restricting means), and the valve timing is changed. There is no risk that the regulations will be lifted unintentionally.

  Therefore, there can be obtained a valve timing changing device for an internal combustion engine that is capable of reliably regulating and releasing the regulation of the valve timing without causing malfunction of the rotation regulating means.

  In addition, the engaging member is provided in a stepped portion provided on the outer periphery of the body portion of the vane member, and the tip thereof can be engaged with an engaging hole provided in the stepped portion of the housing member. Since the engaging member and the engaging hole are arranged in the step portion of the vane member and the step portion of the housing member, the rotation restricting means can be easily arranged without increasing the size of the entire valve timing changing device. Moreover, it is not necessary to increase the diameter of the entire outer periphery of the body portion of the vane member in order to provide the engaging member. For this reason, compared with the case where the diameter of the whole outer periphery of the trunk portion of the vane member is increased, the pressure receiving area of the vane is not reduced.

  Further, the engaging member is provided in the vane member so as to be able to protrude and retract in a radial direction, and a tip of the engaging member protrudes across the hydraulic oil chamber so as to be engageable with an engaging hole through which the hydraulic oil in the hydraulic oil chamber is guided. Therefore, the hydraulic pressure of the hydraulic oil chamber can be directly applied to the engagement member, and the engagement member can be operated quickly.

  Further, since the engagement hole is formed by the engagement hole member embedded in the housing member, the engagement hole member can be easily formed into a predetermined shape from any material. The degree of freedom in design and manufacture can be increased.

  In addition, since the engagement hole member is formed of a material that is harder than the housing member, wear of the engagement hole can be suppressed and durability can be improved.

  Further, since the cylinder hole is formed by a cylinder hole member embedded in the vane member, the cylinder hole member can be easily formed into a predetermined shape from any material, and the degree of freedom in designing and manufacturing the cylinder hole. Can be increased.

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

  In addition, since the engaging member is provided with a spring member that urges the engaging member in the radial direction, the centrifugal force acting on the engaging member is at a very low speed or when the internal combustion engine is rotating. Even when the force is extremely small or zero, the engaging member can be reliably engaged with the engaging 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 showing an embodiment of the present invention, and FIG. 2 is an explanatory view including a cross-sectional view taken along the line A-O-A of FIG.

  In the figure, reference numeral 1 denotes a camshaft for driving an intake valve or an exhaust valve of an internal combustion engine, and in this embodiment, a camshaft for driving 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 rotation of 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 a plurality of (four in this embodiment) projections 28 project toward the inner peripheral side of the annular housing body 19 to form a radius. Four chambers 29 connected at the central portion are formed on the outer side in the 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.

  The fluid-tight seal between the hydraulic oil chambers 34 and 35 is achieved by pressing a seal member 36 provided at the tip of a projection 28 formed on the inner peripheral side of the housing body 19 with a spring member (not shown). This is accomplished by sliding in contact with the outer periphery of the body portion 32 of the member 30 and pressing the seal member 38 provided at the tip of the vane 33 with the spring member 39 to be in sliding contact with the inner periphery of the housing body 22.

  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.

  Reference numeral 44 denotes a rotation restricting means that is provided between the housing member 18 and the vane member 30 and restricts relative rotation between the housing member 18 and the vane member 30. The rotation restricting means 44 is accommodated in a cylinder hole 45 formed in the vane member 30, thereby forming a distal end of an engaging member 47 provided in the vane member 30 so as to be able to protrude and retract in the radial direction in the housing member 18. The engagement hole 48 can be engaged.

  The cylinder hole 45 is formed in the vane member 30, specifically, on the outer periphery of the body portion 32 of the vane member 30 so as to face one of the hydraulic oil chambers 34 and open in the radial direction. The body portion 32 in which the cylinder hole 45 is formed has a slightly larger radial dimension than the body portion 32 in which the cylinder hole 45 is not formed in order to facilitate the formation of the cylinder hole 45. . 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 trunk portion 32 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.

  Further, the inside of the cylinder hole 45 is opened to the atmosphere on the bottom side through a stepped hole-shaped passage 51 formed in the vane 33, and the passage 51 opens to the inner periphery of the cylinder hole 45. Yes.

  The engaging member 47 is formed in a stepped shape that matches the stepped shape of the cylinder hole 45, the tip end side is formed in a tapered shape, and the large-diameter body portion is on the bottom side where the diameter of the cylinder hole 45 is expanded. The small-diameter body is positioned and supported by the inner surface of the cylinder hole member 50 in the cylinder hole 45.

  When the engaging member 47 is housed in the cylinder hole 45, the distal end side of the tapered shape can protrude from the cylinder hole 45 by centrifugal force or the like. 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.

  Further, since the engaging member 47 is accommodated in the cylinder hole 45 facing one of the hydraulic oil chambers 34, the tip of the engaging member 47 protrudes in a radial direction across one of the working chambers 34. , It engages with the engagement hole 48.

  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 the protrusion 28 of the housing body 19 so as to open toward one of the hydraulic oil chambers 34. The protrusion 28 in which the engagement hole 48 is formed is radially inward compared to the protrusion 28 in which the engagement hole 48 is not formed in order to align with the body portion 32 of the vane member 30 in which the cylinder hole 45 is formed. The projecting height to is slightly smaller. 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. Further, the inside of the engagement hole 48 and the oil chamber 56 are between an oil groove 57 formed on the inner surface of the engagement hole 48 and between the outer periphery of the body 32 of the vane member 30 and the inner periphery of the protrusion 28 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.

  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 engaging member 47 of the rotation restricting means 44 protrudes in the radial direction by centrifugal force. The front end of the housing engages with the engagement hole 48 to connect the housing member 18 and the vane member 30 together. For this reason, the rotational driving force applied to the sprocket 17 as the rotating body 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.

  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, the collision between the vane 33 and the housing member 18 can be prevented, and it is advantageously prevented that a hitting sound is generated.

  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, A discharge passage 67 is connected to the discharge passage 72. As a result, the hydraulic oil from the oil pump 69 is guided from the supply / discharge passage 68 into the hydraulic oil chamber 34 via the passage 4, the radial passage 8, the circumferential groove 6, and the radial passage 40. In addition, the hydraulic oil introduced into the hydraulic oil chamber 34 passes through the gap 58 and the oil groove 57, and enters the engagement hole 48 (and the bottom of the engagement hole 48) with which the tip of the engagement member 47 is engaged. The oil chamber 56 is provided).

  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 rotation phase of the camshaft 1 is changed, the camshaft 1 is advanced, and the intake valve driven by the camshaft 1 is controlled. The opening and closing timing of the is advanced.

  When the camshaft 1 is controlled to advance, and the vane member 30 is at the most advanced position with respect 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. This 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. When connected, 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 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 is changed, the camshaft 1 is retarded, and the intake valve driven by the camshaft 1 is controlled. The opening / closing timing of the is delayed.

  When the camshaft 1 is controlled to be retarded and the vane member 30 is at the most retarded position with respect to the housing member 18, the front end of the engaging member 47 protruding into the hydraulic oil chamber 34 is engaged with the engaging hole 48. Again engaged.

  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 sprocket 17 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 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, the engaging member 47 of the rotation restricting means 44 is provided on the vane member 30 so as to be able to project and retract in the radial direction, and its tip protrudes to be engageable with an engaging hole 48 provided in the housing member 18. Therefore, when the housing member 18 and the vane member 30 rotate, the centrifugal force acting on the engaging member 47 acts in a direction in which the tip of the engaging member 47 is engaged with the engaging hole 48.

  For this reason, when the housing member 18 and the vane member 30 rotate and a centrifugal force acts on the engaging member 47, the engaging member 47 is pulled out from the engaging hole 48 (malfunction of the rotation restricting means 44). In addition, there is no possibility that the restriction on the change of the valve timing is unintentionally released.

  Therefore, there is obtained a valve timing changing device for an internal combustion engine in which the rotation restricting means 44 does not malfunction and the valve timing change can be reliably restricted and released.

  Further, the engagement member 47 is provided in the vane member 30 so as to be able to protrude and retract in the radial direction, and its tip protrudes across the hydraulic oil chamber 34 and engages with an engagement hole 48 through which the hydraulic oil in the hydraulic oil chamber 34 is guided. Accordingly, 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 operated quickly.

  Further, since the engagement hole 48 is formed by the engagement hole member 55 embedded in the housing member 18, the engagement hole member 55 can be 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 vane member 30, the cylinder hole member 50 can be easily formed into a predetermined shape from an arbitrary material. In addition, the degree of manufacturing freedom 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.

  FIG. 3 is a drawing showing another embodiment of the present invention. This embodiment is different from the above embodiment in that a cylinder hole 45 formed in the vane member 30 is formed in a step portion 49 of the vane member 30. The engagement hole 48 formed in the housing member 18 is formed in the step portion 54 of the housing member 18.

  That is, the cylinder hole 45 faces the one of the hydraulic oil chambers 34 in the radial direction in the vane member 30, more specifically, in the stepped portion 49 formed between the outer periphery of the body portion 32 of the vane member 30 and the vane 33. It is open and formed. 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 stepped portion 49 of the vane member 30. 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.

  By forming the cylinder hole 45 in the stepped portion 49, all the radial dimensions of the body portion 32 are formed to be equal. For this reason, the step portion 49 receives the oil pressure in the oil chamber 34 and constitutes a part of the pressure receiving surface of the vane 33 connected to the step portion 49, so that the pressure receiving areas of the four vanes 33 are substantially equal. It is equal to.

  The engagement hole 48 opens in the housing member 18, more specifically, in a stepped portion 54 formed between the inner periphery of the housing main body 19 and the protrusion 28 so as to face one of the hydraulic oil chambers 34. It is formed. The engagement hole 48 is made of a material harder than the housing body 19 and is formed by embedding the engagement hole member 55 in which the engagement hole 48 is formed in the step portion 54 of the housing body 19. It is.

  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. Further, in the engagement hole 48 and the oil chamber 56, there are an oil groove 57 formed on the inner surface of the engagement hole 48 and a gap 59 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 hydraulic oil chamber 34.

  By forming the engagement hole 48 in the step portion 54, the protrusion heights of the protrusions 28 are all formed equal. For this reason, the step portion 54 receives the oil pressure in the oil chamber 34 and constitutes a part of the pressure receiving surface of the projection 28 connected to the step portion 49. Therefore, the pressure receiving areas of the four protrusions 28 are substantially equal. It is equal to.

  In addition, since the other structure is the same as that of the said embodiment, the same code | symbol is attached | subjected to the same component and the overlapping description is abbreviate | omitted.

  In such a configuration, when the internal combustion engine is started, when hydraulic oil is not sufficiently supplied from an unillustrated oil pump, or when a signal for maintaining the most retarded state is input to the control device that controls the hydraulic intake / exhaust means In other words, the vane member 30 of the relative rotation means 31 is at the most retarded position with respect to the housing member 18 (see FIG. 3). 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 the vane 33 is preferably 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.

  Next, when the advance angle control is performed, hydraulic oil from an oil pump (not shown) is guided into the hydraulic oil chamber 34. In addition, the hydraulic oil introduced into the hydraulic oil chamber 34 passes through the gap 59 and the oil groove 57, and is engaged in the engagement hole 48 (and the bottom of the engagement hole 48) with which the tip of the engagement member 47 is engaged. The oil chamber 56 is provided). At the same time, the inside of the hydraulic oil chamber 35 is communicated with a discharge passage not shown.

  When the hydraulic oil is guided into the hydraulic oil chamber 34 and the oil chamber 56, the distal end of the engagement member 47 is detached from the engagement hole 48, and the housing member 18 and the vane member 30 formed by the engagement member 47 are separated. Will be released. Further, 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 with respect to the housing member 18 in the direction of the arrow in FIG. As a result, the rotational phase of the camshaft (not shown) is changed, the camshaft is advanced, and the opening / closing timing of the intake valve driven by this camshaft is advanced.

  When retarding control is performed from this state, the hydraulic oil is supplied into the hydraulic oil chamber 35 while the hydraulic oil in the hydraulic oil chamber 34 is discharged. As a result, 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 in FIG. As a result, the rotational phase of the camshaft (not shown) is changed, the camshaft is retarded, and the opening / closing timing of the intake valve driven by this camshaft is delayed.

  In addition, when the vane member 30 is rotated in the advance angle direction or the retard angle direction with respect to the housing member 18, the intake and discharge of the hydraulic oil to and from the hydraulic oil chambers 34 and 35 is blocked, thereby the vane member 30. And the housing member 18 are held at an intermediate position of relative rotation. As a result, the rotational phase of the camshaft (not shown) is held at an intermediate position, and the camshaft controls the opening / closing timing of the intake valve driven by this camshaft.

  Here, the engaging member 47 of the rotation restricting means 44 is provided on the vane member 30 so as to be able to project and retract in the radial direction, and its tip protrudes to be engageable with an engaging hole 48 provided in the housing member 18. Therefore, when the housing member 18 and the vane member 30 rotate, the centrifugal force acting on the engaging member 47 acts in a direction in which the tip of the engaging member 47 is engaged with the engaging hole 48.

  For this reason, when the housing member 18 and the vane member 30 rotate and a centrifugal force acts on the engaging member 47, the engaging member 47 is pulled out from the engaging hole 48 (malfunction of the rotation restricting means 44). In addition, there is no possibility that the restriction on the change of the valve timing is unintentionally released.

  Therefore, also in this embodiment, there is obtained a valve timing changing device for an internal combustion engine in which the rotation restricting means 44 does not malfunction and the valve timing change can be reliably restricted and released.

  In addition, the engaging member 47 is provided in the stepped portion 49 of the vane member 30, and the tip thereof is engageable with the engaging hole 48 provided in the stepped portion 54 of the housing member 18, that is, Since the engaging member 47 and the engaging hole 48 are disposed in the stepped portion 49 of the vane member 30 and the stepped portion 54 of the housing member 18, the rotation restricting means 44 can be easily performed without increasing the size of the entire valve timing changing device. Can be arranged. Further, since the engaging member 47 is provided, it is not necessary to increase the diameter of the entire outer periphery of the body portion of the vane member 30.

  Further, since the step portion 49 constitutes a part of the pressure receiving area of the vane 33 and the step portion 54 constitutes a part of the pressure receiving surface of the protrusion 28, the pressure receiving areas of all the vanes 33 and the protrusions 28 are substantially reduced. Can be the same. Therefore, it is possible to improve the operation responsiveness when changing the rotational phase of the camshaft (not shown).

  FIG. 4 is a drawing showing still another embodiment of the present invention. This embodiment differs from the above embodiment in that the engagement member 47 is radiated to the engagement member 47 of the rotation restricting means 44. This is the point of attaching a spring member 46 that biases in the direction.

  That is, the rotation restricting means 44 of the embodiment shown in FIG. 4 is accommodated in a cylinder hole 45 formed in the vane member 30, so that the engagement member 47 is provided in the vane member 30 so as to be able to protrude and retract in the radial direction. The spring member 46 is configured to be engageable with an engagement hole 48 formed in the housing member 18 and urge the engagement member 47 in the radial direction together with the engagement member 47 in the cylinder hole 45. It is set as the structure which 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 urge the engagement member 47 in the radial direction. In addition, although the coil spring is employ | adopted as the said spring member 46 in this embodiment, 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 effects and advantages similar to those of the embodiment described above, the engaging member 47 is provided with a spring member 46 that urges the engaging 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.

  FIG. 5 is a drawing showing still another embodiment of the present invention. In this embodiment, the vane member 30 of the relative rotation means 31 is at the most advanced position with respect to the housing member 18 when the internal combustion engine is started. In this way, the arrangement position of the rotation restricting means 44 is changed in order to obtain a valve timing changing device suitable for changing the opening / closing timing of the exhaust valve.

  That is, when the rotation restricting means 44 is accommodated in a cylinder hole 45 formed in the vane member 30, the tip of the engaging member 47 provided in the vane member 30 so as to be able to protrude and retract in the radial direction is provided on the housing member 18. Although it is the same as that of the above embodiment in that it is configured to be engageable with the formed engagement hole 48, this rotation restricting means 44 is arranged at a position different from that of the above embodiment.

  That is, the cylinder hole 45 and the engagement hole 48 of the rotation restricting means 44 are formed so as to face one of the hydraulic oil chambers 35 of the pair of hydraulic oil chambers 34, 35. The tip of the accommodated engagement member 47 projects radially across one of the hydraulic oil chambers 35 and can engage with the engagement hole 48.

  The vane member 30 is preferably connected to a camshaft (not shown) that drives an exhaust valve. 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, when the operating oil is not sufficiently supplied from the oil pump (not shown) at the start of the internal combustion engine, or a signal for maintaining the most retarded angle state is input to the control device (not shown). The vane member 30 of the relative rotation means 31 is at the most advanced angle position with respect to the housing member 18, and the distal end of the engagement member 47 of the rotation restricting means 44 engages with the engagement hole 48. 18 and the vane member 30 are connected. For this reason, the rotational driving force applied to the sprocket from the crankshaft (not shown) via the timing chain is transmitted to the camshaft 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 rotates, the exhaust valve of the internal combustion engine is driven and open / close controlled.

  When the hydraulic oil is introduced into the hydraulic oil chamber 35 and the oil chamber 56, the restraint between the housing member 18 and the vane member 30 by the engaging member 47 is released, and the vane member 30 is moved relative to the housing member 18. Thus, it rotates counterclockwise, that is, in the retarding direction. As a result, the camshaft is retarded, and the opening / closing timing of the exhaust valve driven by the camshaft is delayed.

  On the other hand, when the hydraulic oil is introduced into the hydraulic oil chamber 34, the vane member 30 rotates clockwise with respect to the housing member 18. As a result, the advance angle of the camshaft is controlled, and the opening / closing timing of the exhaust valve driven by the camshaft is advanced.

  In addition, when the vane member 30 is rotated in the retarding direction or the advancing direction with respect to the housing member 18, the supply and discharge of the working oil into the working oil chambers 34 and 35 is interrupted, thereby the housing. The member 18 and the vane member 30 are held at an intermediate position of relative rotation as in the above embodiment.

  Also in such a configuration, the engagement member 47 of the rotation restricting means 44 is provided on the vane member 30 so as to be able to protrude and retract in the radial direction, and its tip projects from the engagement hole 48 provided in the housing member 18. Therefore, the same operations and effects as described in the above embodiment can be obtained.

  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.

  The present invention provides a valve timing changing device for an internal combustion engine that is capable of reliably restricting and releasing the restriction of valve timing without malfunction of the rotation restricting means. It is suitable for a valve timing changing device for changing the opening / closing timing of a valve or 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. FIG. 6 is a view similar to FIG. 1 showing still another embodiment of the present invention. FIG. 6 is a view similar to FIG. 1 showing still another embodiment of the present invention.

Explanation of symbols

1 Camshaft 17 Sprocket (Rotating body)
18 Housing member 30 Vane member 31 Relative rotation means 33 Vane 44 Rotation restriction means 45 Cylinder hole 47 Engagement member 48 Engagement hole

Claims (3)

An intake valve or an exhaust valve is provided between a rotating body 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 the camshaft is rotated relative to the rotating body. In the internal combustion engine valve timing changing device comprising a rotation restricting means for restricting relative rotation between the rotating body and the camshaft when the internal combustion engine is started.
A housing member provided so as to rotate together with any one of the rotating body and the camshaft, and a protrusion forming a chamber therein is formed;
A vane member that is housed in the housing member and rotates together with either the rotating body or the camshaft;
A plurality of vanes that project in the radial direction of the vane member and that form a plurality of hydraulic oil chambers in the circumferential direction in the housing member, and
It said rotation restricting means, the engaging hole is formed so as to open facing the one of the hydraulic oil chamber step portion provided in the housing member,
An engagement member that is provided in a stepped portion provided in the vane member so as to be able to protrude and retract in a radial direction, and whose front end crosses the hydraulic oil chamber and can be engaged with an engagement hole;
A spring member for urging the engaging member toward the engaging hole;
An oil chamber for releasing the engagement member from the engagement hole by the operation oil from the oil pump being guided;
A valve timing changing device for an internal combustion engine, comprising: 2. The valve timing changing device for an internal combustion engine according to claim 1, wherein the step portion of the vane member is configured not to contact a side surface of the protrusion of the housing member . The valve timing changing device for an internal combustion engine according to claim 1 or 2, wherein a gap is formed between the step portion of the vane member and the step portion of the housing member.

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