JP5870838B2 - Spool built-in bolt - Google Patents

Description

  The present invention relates to a spool built-in bolt, and more particularly to a spool built-in bolt including a cylindrical housing and a spool movable in the axial direction in the housing.

  2. Description of the Related Art Conventionally, an internal combustion engine mounted on a vehicle such as an automobile is provided with a valve timing variable mechanism that varies valve timing such as an intake valve and an exhaust valve in order to improve fuel consumption and output. In such an internal combustion engine, the relative rotation phase of the camshaft with respect to the crankshaft is changed by operating a movable member of the variable valve timing mechanism that is fixed to the end of the camshaft through supply and discharge of oil to and from the variable valve timing mechanism. Is configured to do. Thus, by changing the relative rotation phase of the camshaft with respect to the crankshaft, the valve timing is varied in the internal combustion engine.

  Oil supply / discharge of the variable valve timing mechanism is controlled through driving of an oil control valve (OCV) provided in a hydraulic circuit connecting the variable valve timing mechanism and the oil pump. This oil control valve includes an oil pump and a discharge passage in a hydraulic circuit, and a rod-shaped spool for switching the oil supply / discharge route between the variable valve timing mechanism.

  Then, by moving the spool of the oil control valve to an arbitrary position with respect to the axial direction, the connection state of the various ports formed in the oil control valve by the spool to the oil pump and the discharge passage is switched. Opening adjustment is performed. As a result, the oil supply / discharge path to the variable valve timing mechanism is switched, and the amount of oil supplied to the variable valve timing mechanism and the amount of oil discharged from the variable valve timing mechanism are adjusted. Then, the movable member of the variable valve timing mechanism is operated to change the relative rotation phase of the camshaft with respect to the crankshaft through switching of the oil supply / discharge path and adjustment of the oil supply and discharge amounts.

  By the way, in the variable valve timing mechanism, responsiveness when operating the variable valve timing mechanism is improved, and oil leakage on the oil supply / discharge route between the variable valve timing mechanism and the oil control valve is prevented. There is a demand for suppression. In order to meet these requirements, it is desirable to shorten the length of the oil supply / discharge path in the portion between the oil control valve and the variable valve timing mechanism in the hydraulic circuit. As a specific method for shortening the path, a configuration in which the function of the oil control valve is added to a bolt for fixing the movable member of the variable valve timing mechanism to the camshaft has been proposed. (For example, refer to Patent Document 1).

  The bolt (spool built-in bolt) disclosed in Patent Document 1 includes a cylindrical housing that fixes the movable member of the variable valve timing mechanism to the camshaft by being screwed to the end of the camshaft. . A spool is accommodated in the housing so as to be capable of reciprocating in the axial direction. Various ports for supplying and discharging oil to and from the valve timing variable mechanism are formed in the housing of the spool built-in bolt. Then, by moving the spool in the housing to an arbitrary position in the axial direction, the connection state of the various ports formed in the housing by the spool to the oil pump and the discharge passage is switched, and the opening degree of the various ports is adjusted. Is called. As a result, switching of the oil supply / discharge path to the variable valve timing mechanism for operating the movable member in the variable valve timing mechanism and adjustment of the oil supply amount and discharge amount are performed.

  By the way, when the housing of the spool built-in bolt is screwed to the end of the camshaft and the movable member of the variable valve timing mechanism is fixed to the camshaft, the manufacturing error or assembly error of the movable member, the housing or the camshaft In some cases, the flange portion of the housing is attached in an inclined state with respect to the camshaft due to manufacturing errors. In this case, there exists a possibility that a housing may deform | transform so that it may curve with respect to the axial direction of a camshaft. In addition, when the spool is bent in the axial direction as the housing is deformed, there is a possibility that an operation failure related to the movement of the spool in the axial direction may occur.

  Therefore, various measures are taken to suppress the occurrence of the above-described malfunction. Patent Document 1 discloses a configuration in which the flange portion of the housing is disposed at a position overlapping the spool sliding portion with respect to the axial direction of the housing. A deformable washer is provided between the flange portion of the housing and the front bush arranged on the movable member side. When the housing of the spool built-in bolt is screwed to the end portion of the camshaft, the washer is pushed by the flange portion and deformed, thereby preventing the housing from being bent in the axial direction. As a result, the bending of the housing in the axial direction is prevented, so that the bending of the spool in the axial direction is prevented. As a result, it is possible to suppress the occurrence of malfunctions related to the movement of the spool in the axial direction due to bending.

  Moreover, in the said patent document 1, the thickness removal part formed by carrying out the thickness reduction in the part connected with the spool sliding part in the flange part of a spool built-in volt | bolt (housing) is provided. By providing the thinning portion in the flange portion in this way, the housing is more easily bent than the other portions in the thinning portion. As a result, when the spool built-in bolt (housing) is curved with respect to the axial direction so that the flange portion is inclined with respect to the axis of the camshaft, the flange portion becomes the spool sliding portion in the wall removal portion. It will bend against it. The bending of the flange portion prevents bending of the spool sliding portion in the axial direction. In this way, since the bending of the spool sliding portion in the axial direction is prevented, the bending of the spool in the axial direction is also prevented. As a result, it is possible to suppress the occurrence of malfunctions related to the movement of the spool in the axial direction due to bending.

Japanese Unexamined Patent Publication No. 2011-241711

  However, in the configuration disclosed in Patent Document 1, since it is necessary to provide a deformable washer between the flange portion of the housing and the front bush arranged on the movable member side, there is a disadvantage that the number of parts increases. is there.

  Further, in the configuration disclosed in the above-mentioned Patent Document 1, by providing a thinned portion at a portion of the flange portion of the spool built-in bolt (housing) connected to the spool sliding portion, the spool sliding portion is curved in the axial direction. On the other hand, since there is a limit to the range in which the thickness can be removed, there is a concern that the bending of the spool sliding portion in the axial direction cannot be sufficiently prevented.

  Further, in the configuration disclosed in Patent Document 1, the flange portion of the housing is disposed at a position overlapping the spool sliding portion with respect to the axial direction of the housing. When a reaction force is applied to the flange portion from the mounting surface when fastening to the mounting surface, a force acting on the spool side is applied to the flange portion (spool sliding portion), and the spool sliding portion is It is deformed so as to be extended in the axial direction. As a result, the spool sliding portion is deformed so as to be contracted inward (in a direction approaching the housing axis), so that there is a malfunction in the axial movement of the spool between the contracted spool sliding portion and the spool. It is thought that it may occur.

  From these viewpoints, it is desired to suppress bending (distortion) in the spool sliding portion while suppressing an increase in the number of parts.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to suppress the bending of the spool sliding portion while suppressing an increase in the number of parts. It is to provide a spool built-in bolt.

  As means for solving the above-described problems, the spool built-in bolt according to the present invention is configured as follows.

  That is, the spool built-in bolt according to the present invention is premised on a configuration including a cylindrical housing and a spool movable in the axial direction in the housing. Further, in the spool built-in bolt according to the present invention, the housing includes a spool sliding portion that accommodates the spool so as to be capable of reciprocating in the axial direction, and a bolt formed on one end side of the housing with respect to the spool sliding portion. And a flange portion formed on the other end side of the housing with respect to the spool sliding portion, and the flange portion is separated from the spool sliding portion on the other end side of the housing. It is arrange | positioned and the clearance gap is provided between the internal peripheral surface of the said flange part, and the outer peripheral surface of the said spool, It is characterized by the above-mentioned.

  According to the bolt with a built-in spool having such a configuration, when a reaction force is applied to the flange portion when the flange portion is fastened to the mounting surface by applying an axial force to the housing, the flange portion is It is deformed (bends) into a gap (a direction approaching the axis of the housing) provided between the inner peripheral surface and the outer peripheral surface of the spool, and the vicinity of the end on the flange side of the spool sliding portion is outside ( It is deformed so as to be enlarged in a direction away from the axis of the housing. As a result, unlike the case where the flange portion is arranged at a position overlapping the spool sliding portion with respect to the axial direction of the housing, the flange portion side end portion of the spool sliding portion is deformed so as to expand outward. Accordingly, it is possible to absorb (cancel) that the vicinity of the end of the spool sliding portion on the flange side contracts inward. As a result, bending (distortion) in the spool sliding portion can be suppressed. Further, since it is not necessary to separately provide a member for suppressing the bending (distortion) of the spool sliding portion, it is possible to suppress an increase in the number of parts.

  As specific configurations of the present invention, the following plural ones are listed.

  In the spool built-in bolt according to the present invention, preferably, the flange portion is disposed to be spaced apart from the other end side of the housing with respect to a portion where the spool sliding portion and the spool are opposed to each other. Features. With this configuration, when the axial force is applied to the housing and the flange portion is fastened to the mounting surface, when the reaction force acts on the flange portion from the mounting surface, the spool sliding portion and the spool face each other. The flange portion can be easily bent to the region on the other end side of the housing with respect to the portion being provided. Thereby, it can deform | transform so that the edge part vicinity of the flange part side of a spool sliding part may be expanded outside.

  Further, in the spool built-in bolt according to the present invention, preferably, the mounting surface of the mounting member to which the flange portion is mounted is disposed so as to be separated from the spool sliding portion on the other end side of the housing. Features. If comprised in this way, while being able to bend a flange part inside a housing (direction which approaches an axis line) by using the attachment surface of the attachment member to which a flange part is attached as a fulcrum, on the flange part side of a spool sliding part The vicinity of the end can be deformed so as to expand outward (in a direction away from the axis).

  In this case, preferably, when the flange portion is attached to the attachment member when the attachment surface of the attachment member is inclined with respect to a direction substantially orthogonal to the axial direction of the housing, the flange portion The flange portion is bent with a contact portion between the mounting portion and the mounting surface of the mounting member as a fulcrum, and the spool sliding portion is deformed so that the vicinity of the end portion on the other end side of the housing expands outward. And If comprised in this way, when the attachment surface of an attachment member inclines with respect to the direction substantially orthogonal to the axial direction of a housing, it uses an attachment surface of the attachment member to which a flange part is attached as a fulcrum, inside a flange part A reaction force (moment) is applied to bend toward the flange portion, and a force (moment) is applied to the outside in the vicinity of the end of the spool sliding portion on the flange portion side. As a result, the flange portion can be bent toward the inside of the housing (in the direction approaching the axis), and the vicinity of the end of the spool sliding portion on the flange side can be deformed to expand outward (in the direction away from the axis). be able to. Thereby, when the mounting surface of the mounting member is inclined with respect to a direction substantially orthogonal to the axial direction of the housing, it is possible to avoid occurrence of a malfunction of the spool (spool lock).

  Further, in the spool built-in bolt according to the present invention, preferably, the spool built-in bolt is provided with a variable valve timing mechanism that varies the relative rotation phase of the camshaft with respect to the crankshaft by operating the movable member by supplying and discharging oil. Applied to an internal combustion engine, the spool is movable in an axial direction in the housing to supply and discharge the oil to and from the valve timing variable mechanism, and the bolt portion is attached to the camshaft, The flange portion is fixed by sandwiching the movable member between the bolt portion and the cam shaft when the bolt portion is attached to the cam shaft. If comprised in this way, since the variable valve timing mechanism provided with the spool built-in bolt which can suppress the curvature (distortion) in a spool sliding part can be comprised, the reliability of the variable valve timing mechanism is further improved. Can be made.

  According to the present invention, it is possible to suppress bending (distortion) in the spool sliding portion while suppressing an increase in the number of parts.

It is the schematic which shows the hydraulic circuit for operating the valve timing variable mechanism with which the spool built-in bolt by one Embodiment of this invention is applied, and this mechanism. Sectional drawing which shows the state which fixed the movable member of the valve timing variable mechanism by one Embodiment of this invention with the said spool built-in volt | bolt, and attaches a spool built-in volt | bolt to the inclined mounting surface (seat surface) of a front bush. It is. It is sectional drawing which shows the case where the spool built-in volt | bolt by one Embodiment of this invention is attached to the attachment surface (seat surface) which is not inclined of a front bush. It is sectional drawing which shows the case where the spool built-in bolt by a comparative example is attached to the attachment surface (seat surface) which inclined the front bush. It is a calculation result for demonstrating the deformation | transformation mechanism of the bolt with a built-in spool by one Embodiment of this invention.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

  Hereinafter, an embodiment in which a spool built-in bolt according to the present invention is applied to a variable valve timing mechanism of an internal combustion engine will be described with reference to FIGS.

  As shown in FIG. 1, the variable valve timing mechanism 1 includes a movable member 3 fixed to a camshaft 2 (for example, an intake camshaft) of an internal combustion engine by a fastening member such as a bolt, and the same axis as the camshaft 2. And a case 4 that transmits rotation of the crankshaft of the internal combustion engine provided on the line so as to surround the movable member 3.

  A plurality of protrusions 5 projecting toward the axis of the camshaft 2 are formed on the inner peripheral surface of the case 4 at a predetermined interval in the circumferential direction. A plurality of vanes 6 are formed between the protrusions 5 on the outer peripheral surface of the movable member 3 so as to protrude in the direction away from the axis of the camshaft 2. As a result, the portion located between the protrusions 5 in the case 4 is partitioned into the advance side hydraulic chamber 7 and the retard side hydraulic chamber 8 by the vane 6.

  When oil is supplied to the advance side hydraulic chamber 7 and oil is discharged from the retard side hydraulic chamber 8, the movable member 3 is relative to the case 4 in the clockwise direction (clockwise direction) in the figure. By rotating, the relative rotation phase of the camshaft 2 with respect to the crankshaft changes to the advance side. Thereby, the valve timing of the engine valve (in this example, the intake valve) of the internal combustion engine changes to the advance side.

  When oil is supplied to the retarded hydraulic chamber 8 and oil is discharged from the advanced hydraulic chamber 7, the movable member 3 is relative to the case 4 in the counterclockwise direction (counterclockwise direction) in the figure. By rotating, the relative rotation phase of the camshaft 2 with respect to the crankshaft changes to the retard side. As a result, the valve timing of the engine valve of the internal combustion engine changes to the retard side.

  With respect to oil supply / discharge of the advance side hydraulic chamber 7 and the retard side hydraulic chamber 8 of the variable valve timing mechanism 1, an oil control valve is provided in the hydraulic circuit connecting the variable valve timing mechanism 1 and the oil pump 9. It is controlled through the drive of the oil control valve. The movable member 3 is connected to the camshaft for the purpose of improving the response when operating the variable valve timing mechanism 1 and suppressing oil leakage on the oil path between the variable valve timing mechanism 1 and the oil control valve. As a bolt for fixing to 2, a spool built-in bolt 10 having not only a fixing function but also an oil control valve function is used.

  The spool built-in bolt 10 is connected to the oil pump 9 via the supply passage 11. The spool built-in bolt 10 is connected to an oil pan 12 for storing oil pumped up by the oil pump 9 via a discharge passage 13. The spool built-in bolt 10 is connected to the advance side hydraulic chamber 7 of the variable valve timing mechanism 1 via the advance side oil passage 14, and the retard side hydraulic chamber 8 of the variable valve timing mechanism 1. Are connected via a retarded angle oil passage 15.

  The spool built-in bolt 10 includes a cylindrical housing 16 that is screwed to the end of the camshaft 2 to fix the movable member 3 to the camshaft 2, the advance side hydraulic chamber 7 of the variable valve timing mechanism 1, and the delay time. A rod-shaped spool 17 that is movable in the axial direction in the housing 16 is provided to supply and discharge oil to and from the corner-side hydraulic chamber 8.

  The housing 16 includes a first port 18 connected to the advance side oil passage 14 and a second port 19 connected to the retard side oil passage 15. The spool 17 switches the connection state between the first port 18 and the second port 19 and the supply passage 11 and the discharge passage 13 through position adjustment of the spool 17 in the axial direction, and the first port 18 and the second port. 19 opening adjustments are performed.

  The spool 17 is provided in the housing 16 and can urge the spool 17 in the axial direction (arrow X2 direction) and the spool 17 against the urging force of the coil spring. The actuator 20 that presses in the axial direction (arrow X1 direction) is configured to be movable in the axial direction (X direction). That is, by adjusting the pressing force of the actuator 20 against the spool 17, the spool 17 moves in the axial direction so that the pressing force against the spool 17 and the biasing force of the coil spring are balanced. As a result, the position of the spool 17 in the axial direction is adjusted. Then, by moving the spool 17 to an arbitrary position in the axial direction, the connection state of the first port 18 and the second port 19 formed in the housing 16 by the spool 17 to the supply passage 11 and the discharge passage 13 is switched. The opening degree of the first port 18 and the second port 19 is adjusted.

  Specifically, when the pressing force of the actuator 20 is increased and the spool 17 is displaced in the direction of the arrow X1, the first port 18 is connected to the supply passage 11 and the second port 19 is connected to the discharge passage. 13 is connected. Thereby, in the variable valve timing mechanism 1, oil is supplied to the advance side hydraulic chamber 7 and oil is discharged from the retard side hydraulic chamber 8. As a result, the movable member 3 of the variable valve timing mechanism 1 rotates relative to the case 4 in the clockwise direction in the drawing, whereby the valve timing of the internal combustion engine changes to the advance side. At this time, the opening degree of the first port 18 and the second port 19 is adjusted by finely adjusting the position of the spool 17 in the axial direction. Thereby, the oil supply amount to the advance side hydraulic chamber 7 and the oil discharge amount from the retard side hydraulic chamber 8 are finely adjusted. By performing such fine adjustment of the oil supply amount and oil discharge amount, the relative rotational position of the movable member 3 with respect to the case 4 can be determined so that the valve timing of the internal combustion engine becomes an arbitrary timing on the advance side. It becomes possible.

  On the other hand, when the pressure of the actuator 20 is reduced and the spool 17 is displaced in the direction of the arrow X2, the first port 18 is connected to the discharge passage 13 and the second port 19 is connected to the supply passage 11. Is done. As a result, oil is supplied to the retarded-side hydraulic chamber 8 to the variable valve timing mechanism 1 and oil is discharged from the advanced-side hydraulic chamber 7. As a result, the movable member 3 of the variable valve timing mechanism 1 rotates relative to the case 4 in the counterclockwise direction in the drawing, so that the valve timing of the internal combustion engine changes to the retard side. At this time, the opening degree of the first port 18 and the second port 19 is adjusted by finely adjusting the position of the spool 17 in the axial direction. Thereby, the oil supply amount to the retard side hydraulic chamber 8 and the oil discharge amount from the advance side hydraulic chamber 7 are finely adjusted. By performing such fine adjustment of the oil supply amount and oil discharge amount, the relative rotational position of the movable member 3 with respect to the case 4 can be determined so that the valve timing of the internal combustion engine becomes an arbitrary timing on the retard side. It becomes possible.

  Next, with reference to FIG. 1 and FIG. 2, fixation of the movable member 3 to the camshaft 2 using the spool built-in bolt 10 will be described.

  As shown in FIG. 2, the housing 16 of the spool built-in bolt 10 penetrates the movable member 3 of the variable valve timing mechanism 1 and is housed so that the spool 17 can be reciprocated in the axial direction. 16b. Specifically, the spool sliding portion 16b is a range A portion of the housing 16, as shown in FIG.

  As shown in FIG. 2, in the housing 16, a bolt portion 16 a that is screwed to the end portion of the camshaft 2 is provided on one end side (arrow X1 direction side) of the housing 16 with respect to the spool sliding portion 16 b. Is formed. In the housing 16, a flange portion 16c is formed on the other end side (arrow X2 direction side) of the housing 16 with respect to the spool sliding portion 16b. The flange portion 16 c is provided for sandwiching and fixing the movable member 3 between the end portion of the camshaft 2 when the bolt portion 16 a is screwed to the end portion of the camshaft 2. The flange portion 16c has an inner peripheral surface 16d on the other end side (arrow X2 direction side) of the housing 16.

  In a state where the bolt portion 16 a of the spool built-in bolt 10 is screwed to the end portion of the camshaft 2, the front portion of the camshaft 2 and the flange portion 16 c of the spool built-in bolt 10 are arranged in addition to the movable member 3. A bush 30, a rear bush 31, and a support body 32 are provided. Among these front bush 30, rear bush 31, and support body 32, the front bush 30 is provided between the movable member 3 and the flange portion 16c, and the rear bush 31 and the support body 32 are movable members. 3 and the end surface of the camshaft 2. The front bush 30 is an example of the “mounting member” in the present invention.

  Here, in this embodiment, the flange part 16c is arrange | positioned so that it may be located in the outer side (arrow X2 direction side) of the spool sliding part 16b. That is, the surface 30b of the front bush 30 to which the flange portion 16c is attached is disposed so as to be located on the other end side (arrow X2 direction side) of the housing 16 with respect to the spool sliding portion 16b. In other words, the contact surface between the flange portion 16c and the surface 30b of the front bush 30 does not overlap with the spool sliding portion 16b when viewed from the direction (Y direction) substantially orthogonal to the axial direction (X direction) of the housing 16. Is arranged. Further, the contact surface between the flange portion 16c and the surface 30b of the front bush 30 is disposed with a distance L1 from the portion 161b on the other end side (arrow X2 direction side) of the housing 16 of the spool sliding portion 16b. Further, the inner peripheral surface 16d of the flange portion 16c is arranged with a distance L2 from the outer peripheral surface 17a of the spool 17. The surface 30b is an example of the “mounting surface” in the present invention.

  Further, the movable member 3, the front bush 30, the rear bush 31, and the support body 32 are formed with a hole 3a, a hole 30a, a hole 31a, and a hole 32a, respectively. The spool sliding portion 16b of the spool built-in bolt 10 is disposed so as to penetrate the hole 3a, the hole 30a, the hole 31a, and the hole 32a. The movable member 3, the front bush 30, the rear bush 31, and the support body 32 are arranged so that the end surface of the camshaft 2 and the spool when the bolt portion 16 a of the spool built-in bolt 10 is screwed to the end portion of the camshaft 2. It is sandwiched between the flange portion 16c of the built-in bolt 10. With the above configuration, the movable member 3, the front bush 30, the rear bush 31, and the support body 32 are fixed to the camshaft 2 so as to be integrally rotatable, and are fixed in the axial direction of the camshaft 2. The

  The support 32 supports a sprocket 33 that receives rotation transmission from the crankshaft of the internal combustion engine so as to be able to rotate relative to the camshaft 2. Further, the case 4 of the variable valve timing mechanism 1 is fixed to the sprocket 33. When the rotation of the crankshaft of the internal combustion engine is transmitted to the sprocket 33, the sprocket 33 and the case 4 rotate about the axis of the camshaft 2. The rotation of the sprocket 33 and the case 4 is transmitted to the movable member 3 via the oil in the case 4 and then transmitted to the camshaft 2. Accordingly, by rotating the movable member 3 of the variable valve timing mechanism 1 relative to the case 4, the relative rotational phase of the camshaft 2 with respect to the crankshaft changes, so that the valve timing of the internal combustion engine corresponds to the change. Change.

  By the way, when fixing the movable member 3 of the variable valve timing mechanism 1 to the camshaft 2 by screw-fastening the spool built-in bolt 10 (specifically, the bolt portion 16a of the housing 16) to the end of the camshaft 2, The following problems may occur. That is, due to manufacturing errors and assembly errors of the movable member 3, the front bush 30, the rear bush 31, and the support body 32, manufacturing errors of the housing 16 and the camshaft 2, the housing 16 (flange portion 16c). ) Of the fastening seat surface (surface 30b on the arrow X2 direction side of the front bush 30) is inclined with respect to a direction (Y direction) substantially orthogonal to the axial direction (X direction) of the housing 16 so that the housing 16 is camshaft 2. There is a risk of deformation so as to bend (bend) in the axial direction. In the present embodiment, as shown in FIG. 2, the fastening seat surface (surface 30 b on the arrow X2 direction side of the front bush 30) of the housing 16 (flange portion 16 c) is substantially orthogonal to the axial direction of the housing 16. Is inclined by an angle α.

  Further, when the spool 17 is curved in the axial direction as the housing 16 is deformed, there is a possibility that a malfunction (so-called spool lock) may occur with respect to the movement of the spool 17 in the axial direction. In order to cope with such a problem, in the spool built-in bolt 10 according to the present embodiment, the flange portion 16c is disposed so as to be located on the outer side (arrow X2 direction side) of the spool sliding portion 16b. Thus, when the housing 16 is deformed, the spool 17 is not curved with respect to the axial direction, and it is possible to prevent malfunctions with respect to the movement of the spool 17 in the axial direction. This point will be described in detail below.

  First, referring to FIG. 3, when an axial force is applied to the spool built-in bolt 10 (housing 16) when the surface to which the flange portion 16 c of the housing 16 is attached (the surface 30 b of the front bush 30) is not inclined. Will be described.

  In FIG. 3, the surface 30b of the front bush 30 which is a surface to which the flange portion 16c of the housing 16 is attached is not inclined. In this state, by applying an axial force in the direction of the arrow X1 to the housing 16, the bolt portion 16a of the housing 16 is screwed to the end portion of the camshaft 2, and the surfaces of the flange portion 16c and the front bush 30 are fixed. 30b contacts. Further, when an axial force is further applied to the housing 16, a portion near the bolt portion 16 a of the housing 16 contracts in a direction approaching the axis of the housing 16. On the other hand, a reaction force (moment) from the front bush 30 in the direction of the arrow X2 is applied to the flange portion 16c with the surface where the flange portion 16c and the surface 30b of the front bush 30 contact each other as a fulcrum.

  Specifically, a reaction force that deforms (bends) in the counterclockwise direction from the front bush 30 toward the axis of the housing 16 is applied to the portion on the arrow Y1 direction side (upper portion) of the flange portion 16c. (Moment) is added. A portion on the arrow Y1 direction side (upper portion) of the flange portion 16c is a portion of an interval L2 (an axis of the housing 16) provided between the inner peripheral surface 16d of the flange portion 16c and the outer peripheral surface 17a of the spool 17. (Direction to approach)).

  Further, a reaction force (moment) that deforms (bends) in the clockwise direction from the front bush 30 toward the axis of the housing 16 is applied to the portion on the arrow Y2 direction side (lower portion) of the flange portion 16c. Is added. A portion on the arrow Y2 direction side (lower portion) of the flange portion 16c is a portion of the interval L2 (the housing 16 of the housing 16) provided between the inner peripheral surface 16d of the flange portion 16c and the outer peripheral surface 17a of the spool 17. Deforms (bends) in a direction approaching the axis).

  At this time, when a reaction force is applied to the flange portion 16 c from the front bush 30, the spool sliding portion 16 b (in the vicinity of the inlet portion 16 e) of the housing 16 has an inner diameter and an outer diameter away from the axis of the housing 16 ( A force that is expanded outward) is applied. That is, a force (moment) that expands outward is applied to the inlet portion 16e of the spool sliding portion 16b with the surface where the flange portion 16c and the surface 30b of the front bush 30 are in contact as a fulcrum.

  Thereby, when an axial force is applied to the housing 16, the inlet portion 16 e of the spool sliding portion 16 b expands in a direction (outside) away from the axis of the housing 16. As a result, in the vicinity of the inlet portion 16e of the spool sliding portion 16b, it is possible to suppress the occurrence of malfunction (spool lock) with respect to the movement of the spool 17 in the axial direction.

  Here, in general, when an axial force is applied to the housing 16, the flange portion 16c comes into contact with the surface 30b of the front bush 30 so that the flange portion 16c or the spool sliding portion 16b is close to the inlet portion 16e. A force is applied to extend in the direction of the arrow X1. As a result, the inner and outer diameters of the flange portion 16c and the spool sliding portion 16b in the vicinity of the inlet portion 16e are deformed so as to contract inwardly (in a direction approaching the axis of the housing 16). As a result, the vicinity of the inlet portion 16e of the spool sliding portion 16b and the spool 17 come into contact with each other, causing a malfunction of the spool 17. In this regard, in this embodiment, since the inlet portion 16e of the spool sliding portion 16b is enlarged, it is possible to absorb (cancel) the contraction generated in the vicinity of the inlet portion 16e of the spool sliding portion 16b. Thus, it is possible to suppress the occurrence of malfunction (spool lock) regarding the movement of the spool 17 in the axial direction.

  Next, referring to FIG. 2, when the surface (surface 30b of the front bush 30) to which the flange portion 16c of the housing 16 is attached is inclined, an axial force is applied to the spool built-in bolt 10 (housing 16). The case will be described.

  In FIG. 2, the surface 30b of the front bush 30 which is a surface to which the flange portion 16c of the housing 16 is attached is in an inclined state. That is, due to manufacturing errors and assembly errors of the movable member 3, the front bush 30, the rear bush 31, and the support 32, manufacturing errors of the housing 16 and the camshaft 2, the flange portion 16 c of the housing 16. Is a state in which the surface to which is attached is inclined.

  In this state, by applying an axial force to the housing 16 of the spool built-in bolt 10, the bolt portion 16 a of the housing 16 is screwed to the end portion of the camshaft 2. At this time, the portion on the arrow Y1 direction side (upper portion) of the flange portion 16c first comes into surface contact with the upper portion of the surface 30b of the front bush 30, and further, axial force is applied to the housing 16, Next, the portion on the arrow Y2 direction side (lower portion) of the flange portion 16c is in surface contact with the lower portion of the surface 30b of the front bush 30 while being deformed (bent) in the arrow Y2 direction side. That is, the flange portion 16c is generally deformed (flexed) in the counterclockwise direction with a surface (surface on the arrow Y1 direction side) where the flange portion 16c and the surface 30b of the front bush 30 first contact each other as a fulcrum. .

  At this time, the outer diameter and the inner diameter of the bolt portion 16 a of the housing 16, particularly the portion on the arrow Y2 direction side, contract in a direction approaching the axis of the housing 16. Further, a reaction force from the front bush 30 in the direction of the arrow X2 is applied to the flange portion 16c with the surface where the flange portion 16c and the surface 30b of the front bush 30 contact each other as a fulcrum.

  Specifically, a reaction force that deforms (bends) the flange portion 16c in the counterclockwise direction from the front bush 30 in a direction approaching the axis of the housing 16 on the arrow Y1 direction side portion (upper portion). (Moment) is added. A portion on the arrow Y1 direction side (upper portion) of the flange portion 16c is a portion of an interval L2 (an axis of the housing 16) provided between the inner peripheral surface 16d of the flange portion 16c and the outer peripheral surface 17a of the spool 17. (Direction to approach)).

  Further, a reaction force (moment) that deforms (bends) the flange 16c in the clockwise direction from the front bush 30 in a direction approaching the axis of the housing 16 on the portion on the arrow Y2 direction side (lower portion). Is added. A portion on the arrow Y2 direction side (lower portion) of the flange portion 16c is a portion of the interval L2 (the housing 16 of the housing 16) provided between the inner peripheral surface 16d of the flange portion 16c and the outer peripheral surface 17a of the spool 17. Deforms (bends) in a direction approaching the axis).

  The reaction force applied to the portion on the arrow Y2 direction side (lower portion) of the flange portion 16c is relatively smaller than the reaction force applied to the portion on the arrow Y1 direction side (upper portion) of the flange portion 16c. .

  At this time, when a reaction force is applied to the flange portion 16 c from the front bush 30, the spool sliding portion 16 b (in the vicinity of the inlet portion 16 e) of the housing 16 has an inner diameter and an outer diameter away from the axis of the housing 16 ( A force that is expanded outward) is applied. That is, a force (moment) that expands outward is applied to the inlet portion 16e of the spool sliding portion 16b with the surface where the flange portion 16c and the surface 30b of the front bush 30 are in contact as a fulcrum.

  Thereby, when an axial force is applied to the housing 16, the inlet portion 16 e of the spool sliding portion 16 b expands in a direction (outside) away from the axis of the housing 16. As a result, it is possible to absorb (cancel) the contraction generated in the vicinity of the inlet portion 16e of the spool sliding portion 16b, thereby suppressing the occurrence of malfunction (spool lock) regarding the movement of the spool 17 in the axial direction. It becomes possible to do.

  Next, when the surface 30b of the front bush 30 is inclined by disposing the flange portion 16c of the housing 16 so as to be positioned outside the spool sliding portion 16b (arrow X2 direction side) as described above. The point that it is possible to suppress the occurrence of spool lock will be described below with reference to a comparative example.

  As shown in FIG. 4, in the spool built-in bolt 110 of the variable valve timing mechanism 1a according to the comparative example, unlike the present embodiment, the flange portion 116c is positioned inside the spool sliding portion 116b (arrow X1 direction side). Are arranged as follows. That is, the contact surface between the flange portion 116c and the front surface 130b of the front bush 130 is positioned on one end side (arrow X1 direction side) of the housing 116 with respect to the end portion 116d of the spool sliding portion 116b on the arrow X2 direction side. Is arranged. The front bush 130 is an example of the “mounting member” in the present invention, and the surface 130b is an example of the “mounting surface” in the present invention.

  In this state, when an axial force is applied to the housing 116 of the spool built-in bolt 110, the bolt portion 116 a of the housing 116 is screwed to the end portion of the camshaft 2 and the flange portion 116 c and the front bush 130. The surface 130b comes into contact. Then, a reaction force is applied to the flange portion 116c from the front bush 130 with the surface where the flange portion 116c and the surface 130b of the front bush 130 contact each other as a fulcrum.

  More specifically, a reaction force that deforms (bends) the front portion of the flange portion 116c in the counterclockwise direction from the front bush 130 in a direction approaching the axis of the housing 116 on the portion on the arrow Y1 direction side (upper portion). (Moment) is added. In addition, a reaction force (moment) that deforms (bends) the front portion of the flange portion 116c in the clockwise direction from the front bush 130 in a direction approaching the axis of the housing 116 at the portion on the arrow Y2 direction side (lower portion). Is added.

  Here, in the comparative example, unlike the present embodiment, when a reaction force is applied to the flange portion 116c from the front bush 130, the inlet portion where the spool 117 and the end portion 116d of the spool sliding portion 116b are in contact with each other. A force that can be bent in the direction of arrow Y2 is applied in the vicinity of 116e. As a result, the contact resistance between the spool sliding portion 116b and the spool 117 increases, and therefore, in the comparative example, a malfunction occurs in the spool 117 with respect to movement in the axial direction.

  In the present embodiment (see FIG. 2), unlike the configuration shown in the comparative example in which the flange portion 116c is disposed on the inner side (arrow X1 direction side) of the spool sliding portion 116b, the flange portion 16c is replaced with the spool sliding portion 16b. Since the fulcrum to which a force that deforms the housing 16 (particularly the flange portion 16c) is applied is arranged outside the spool sliding portion 16b (arrow X2 direction side). When the housing 16 is deformed, the inlet portion 16e of the spool sliding portion 16b can be enlarged. Accordingly, since the spool 17 is not curved with respect to the axial direction, it is possible to prevent an operation failure with respect to the movement of the spool 17 in the axial direction between the spool 17 and the spool sliding portion 16b. .

  Next, referring to FIG. 2 and FIG. 5, when the housing 16 is deformed, the spool 17 is not curved with respect to the axial direction so that no malfunction occurs with respect to the movement of the spool 17 in the axial direction. The calculation result about the point which can be made is demonstrated.

  The calculation result shown in FIG. 5 is a calculation result corresponding to the configuration in which the housing 16 according to the present embodiment shown in FIG. 2 is attached to the surface 30b of the front bush 30 whose surface is inclined. This calculation result shows the size of the inner diameter from the axis of the housing 16 to the upper ridge line (upper ridge line shape) and the size of the inner diameter from the axis of the housing 16 to the lower ridge line (lower ridge line shape).

  In FIG. 5, the left side of the vertical axis shows the amount of strain (%) based on the inner diameter (radius) r of the upper ridge line (the upper shape of the inner peripheral surface) of the spool built-in bolt 10 (housing 16). The inner diameter before deformation (0 (%)) is indicated by a white rhombus, and the inner diameter after deformation is indicated by a black rhombus. The right side of the vertical axis shows the amount of strain (%) based on the inner diameter (radius) r of the lower ridge line shape (the lower shape of the inner peripheral surface) of the spool built-in bolt 10 (housing 16). The inner diameter before deformation (0 (%)) is indicated by a white square, and the inner diameter after deformation is indicated by a black square. Further, the axial position x in the arrow X1 direction of the housing 16 when the end surface on the flange portion 16c side of the housing 16 is used as a reference is shown on the horizontal axis. A connection line connecting each point (white rhombus, black rhombus, white square, black square) represents the shape of the inner diameter (inner surface) of the housing 16.

  As shown in FIG. 5, before the deformation, the inner diameter of the upper ridge line shape (white rhombus) of the housing 16 is constant r regardless of the axial position. The inner diameter of the lower ridge line shape (white square) of the housing 16 is constant r regardless of the position in the axial direction. That is, it can be seen that before the deformation, the size of the inner diameter of the housing 16 is not deformed and extends straight in the axial direction. The inner diameter (diameter) of the housing 16 is 2r. Further, before the deformation, the spool 17 is located between the white rhombus connection line indicating the upper ridge line shape of the housing 16 and the white square connection line indicating the lower ridge line shape of the housing 16 (broken line in FIG. 5). Therefore, it can be seen that the spool 17 can slide in the housing 16 in the axial direction.

  Next, the shape of the upper ridge line of the housing 16 after deformation will be described. After deformation, it was found that the upper ridge line shape (black rhombus) of the housing 16 is larger on the upper side (outer side) than before deformation (white rhombus) in the range where the axial position is a part. That is, it was found that the inner diameter (upper side) in the vicinity of the inlet 16e (see FIG. 2) of the housing 16 was enlarged. Further, since the shape of the upper ridge line increases as the axial position increases in the range where the axial position is a part, the vicinity of the inlet 16e of the housing 16 shown in FIG. It was found that the image was enlarged from a direction (Y direction) substantially orthogonal to (direction) to a direction inclined to the arrow X2 direction side.

  Further, it was found that the upper ridge line shape (black rhombus) of the housing 16 is substantially the same size as that before deformation (white rhombus) in the range where the axial position is b part. That is, in this range, it was found that the size of the inner diameter (upper side) in the vicinity of the inlet portion 16e of the housing 16 hardly changed before and after the deformation of the housing 16.

  In addition, it was found that the upper ridge line shape (black rhombus) of the housing 16 is larger on the upper side than the deformation (white rhombus) in the range where the axial position is c portion. That is, it was found that the inner diameter (upper side) of the spool sliding portion 16b of the housing 16 was enlarged.

  Further, it was found that the upper ridge line shape (black rhombus) of the housing 16 is larger (enlarged) than before deformation (white rhombus) in the range where the axial position is the d portion. Further, it was found that the expansion amount (deformation amount) of the inner diameter (upper side) of the spool sliding portion 16b of the housing 16 is larger than the expansion amount (deformation amount) in the range of the portion c in the axial direction.

  Further, it was found that the upper ridge line shape (black rhombus) of the housing 16 is larger on the upper side than the deformation (white rhombus) in the range where the axial position is the portion e. Further, it was found that the expansion amount (deformation amount) of the inner diameter (upper side) of the spool sliding portion 16b of the housing 16 is larger than the expansion amount (deformation amount) in the range of the d portion in the axial position. Further, after deformation, it was found that the expansion amount (deformation amount) of the inner diameter (upper side) of the spool sliding portion 16b is the largest in the range of the e portion of the entire range of the axial position of the housing 16.

  In addition, it was found that the upper ridge line shape (black rhombus) of the housing 16 is larger on the upper side than the deformation (white rhombus) in the range where the axial position is the f portion. In this range, the enlargement amount (deformation amount) of the inner diameter (upper side) of the spool sliding portion 16b of the housing 16 is smaller than the enlargement amount (deformation amount) of the housing 16 in the axial range. I understood. Further, the enlargement amount (deformation amount) of the inner diameter (upper side) of the spool sliding portion 16b in this range is the enlargement amount (deformation amount) of the inner diameter (upper side) of the spool slide portion 16b in the range where the axial position is the c portion. It turned out to be almost the same.

  Further, it was found that the upper ridge line shape (black rhombus) of the housing 16 is substantially the same size as that before deformation (white rhombus) in the range where the axial position is g. That is, in this range, it was found that the size of the inner diameter (upper side) in the vicinity of the bolt portion 16a of the housing 16 hardly changed before and after the deformation of the housing 16.

  Next, the shape of the lower ridge line of the housing 16 after deformation will be described. After deformation, it was found that the lower ridge line shape (black square) of the housing 16 is larger on the lower side (outside) than before deformation (white square) in the range where the axial position is a part. That is, it was found that the inner diameter (lower side) of the housing 16 in the vicinity of the inlet portion 16e (see FIG. 2) is enlarged.

  Further, it was found that the lower ridge line shape (black square) of the housing 16 is smaller on the upper side (inner side) than before deformation (white square) in the range where the position in the axial direction is b. Here, when the axial position is in the range a, the lower ridge line shape of the housing 16 is enlarged before and after the deformation. On the other hand, when the axial position is in the range b, the lower ridge line shape of the housing 16 is before and after the deformation. Because of the contraction, the vicinity of the inlet portion 16e of the housing 16 shown in FIG. 2 is enlarged in a direction inclined to the arrow X1 direction side from the direction (Y direction) substantially orthogonal to the axial direction (X direction). I understood.

  Further, it was found that the lower ridge line shape (black square) of the housing 16 is further smaller on the upper side than that before the deformation (white square) in the range where the axial position is the c portion. That is, it was found that the shrinkage amount (deformation amount) of the inner diameter (lower side) of the spool sliding portion 16b of the housing 16 is larger than the shrinkage amount (deformation amount) in the range of the portion b in the axial direction.

  Further, it was found that the lower ridge line shape (black square) of the housing 16 is smaller on the upper side than that before deformation (white square) in the range where the axial position is the d portion. It was found that the shrinkage amount (deformation amount) of the inner diameter (lower side) of the spool sliding portion 16b of the housing 16 is larger than the shrinkage amount (deformation amount) in the range of the portion c in the axial direction.

  Further, it was found that the lower ridge line shape (black square) of the housing 16 is smaller on the upper side than that before deformation (white square) in the range where the axial position is the e portion. It was found that the shrinkage amount (deformation amount) of the inner diameter (lower side) of the spool sliding portion 16b of the housing 16 is smaller than the shrinkage amount (deformation amount) in the range of the portion d in the axial direction.

  Further, it was found that the lower ridge line shape (black square) of the housing 16 is smaller on the upper side than that before the deformation (white square) in the range where the axial position is the portion f. In this range, it was found that the axial position is larger than the contraction amount (deformation amount) of the housing 16 in the range of the e portion. Further, it was found that after the deformation, the contraction amount (deformation amount) of the inner diameter (lower side) of the spool sliding portion 16b is the largest in the range of the f portion in the entire range of the axial position of the housing 16.

  Further, it has been found that the lower ridge line shape (black square) of the housing 16 is smaller on the upper side than before deformation (white square) in the range where the axial position is g. It was found that the shrinkage amount (deformation amount) of the inner diameter (lower side) of the spool sliding portion 16b of the housing 16 is smaller than the shrinkage amount (deformation amount) in the range of the f portion in the axial position.

  From the above calculation results, after deformation of the housing 16, between the black rhombus connection line indicating the upper ridge line shape of the housing 16 and the black square connection line indicating the lower ridge line shape of the housing 16, as before the deformation. Since the spool 17 is located (a square portion surrounded by a broken line), it has been found that the spool 17 can slide in the housing 16 in the axial direction. In particular, after the deformation, the vicinity of the inlet portion 16e of the housing 16 is enlarged, so that it is possible to suppress the spool 17 from contacting (spooling) the spool sliding portion 16b in the vicinity of the inlet portion 16e. I understood that.

  Further, assuming that the vicinity of the inlet portion 16e does not expand when the housing 16 is deformed, the lower ridge line shape of the housing 16 has a convex shape on the upper side over the entire axial position as shown by the broken line in FIG. It can be seen that this contracts (deforms). And it turned out that the lower ridgeline shape (broken line) of the housing 16 does not contact with the range (square part enclosed with the broken line) where the spool 17 slides. That is, it has been found that the spool lock does not occur on the lower side of the housing 16 near the inlet portion 16e.

  On the other hand, it can be seen that the shape of the upper ridge line (broken line) of the housing 16 expands (deforms) so as to have a convex shape on the entire upper side in the axial direction. Then, it was found that in the range where the axial position is h, the spool 17 is in contact with the sliding range (square portion surrounded by a broken line). That is, assuming that the vicinity of the inlet portion 16e does not expand, it has been found that a spool lock occurs on the inner surface (upper side) of the housing 16 near the inlet portion 16e.

  As described above, according to the spool built-in bolt 10 according to the present embodiment, the effects listed below can be obtained.

  In the present embodiment, as described above, the flange portion 16c is arranged at the other end side (arrow X2 direction side) of the housing 16 with respect to the spool sliding portion 16b with a distance L1 therebetween, and the inner circumference in the vicinity of the flange portion 16c. A space L2 is provided between the surface 16d and the outer peripheral surface 17a of the spool 17. As a result, when an axial force is applied to the housing 16 and the flange portion 16c is fastened to the surface 30b of the front bush 30, a reaction force acts on the flange portion 16c from the surface 30b of the front bush 30. Is deformed (flexed) into a portion having a distance L2 (direction approaching the axis of the housing 16) provided between the inner peripheral surface 16d of the flange portion 16c and the outer peripheral surface 17a of the spool 17, and the spool sliding portion 16b. The vicinity of the inlet portion 16e is deformed so as to expand outward (in a direction away from the axis of the housing 16). Thus, unlike the case where the flange portion 16c is disposed at a position overlapping the spool sliding portion 16b with respect to the axial direction (X direction) of the housing 16, the vicinity of the inlet portion 16e of the spool sliding portion 16b is expanded outward. As the deformation occurs, it is possible to absorb (cancel) the vicinity of the inlet portion 16e of the spool sliding portion 16b contracting inward. As a result, bending (distortion) in the vicinity of the inlet portion 16e of the spool sliding portion 16b can be suppressed. Moreover, since it is not necessary to separately provide a member for suppressing distortion of the spool sliding portion 16b, an increase in the number of parts can be suppressed.

  Further, in the present embodiment, as described above, the flange portion 16c is spaced from the portion where the spool sliding portion 16b and the spool 17 are opposed to the other end side (arrow X2 direction side) of the housing 16 by the interval L1. Place them apart. As a result, when an axial force is applied to the housing 16 and the flange portion 16c is fastened to the surface 30b of the front bush 30, a spool sliding occurs when a reaction force acts on the flange portion 16c from the surface 30b of the front bush 30. The flange portion 16c can be easily bent to the area on the arrow X2 direction side of the spool sliding portion 16b rather than the portion where the portion 16b and the spool 17 are opposed to each other. As a result, the vicinity of the inlet portion 16e of the spool sliding portion 16b can be easily deformed to expand outward.

  Further, in the present embodiment, as described above, the surface 30b of the front bush 30 to which the flange portion 16c is attached is arranged with the interval L1 on the arrow X2 direction side with respect to the spool sliding portion 16b. As a result, the flange portion 16c can be bent to the inside of the housing 16 (in the direction approaching the axis) with the surface 30b of the front bush 30 to which the flange portion 16c is attached as a fulcrum, and the inlet portion 16e of the spool sliding portion 16b. The vicinity can be deformed so as to expand outward (in a direction away from the axis).

  Further, in the present embodiment, as described above, when the surface 30b of the front bush 30 is inclined at an angle α with respect to a direction (Y direction) substantially orthogonal to the axial direction (X direction) of the housing 16, the flange 30 When the portion 16c is attached to the surface 30b of the front bush 30, the flange portion 16c bends in the direction of the arrow Y2 with the contact portion between the flange portion 16c and the surface 30b of the front bush 30 as a fulcrum, and the spool sliding portion 16b The inlet portion 16e is deformed so as to expand outward (in a direction away from the axis). Thereby, when the surface 30b of the front bush 30 is inclined with respect to the direction substantially orthogonal to the axial direction of the housing 16, the surface 30b of the front bush 30 to which the flange portion 16c is attached is used as a fulcrum. A reaction force (moment) that deflects inward is applied, and a force (moment) that expands outward is applied in the vicinity of the inlet portion 16e of the spool sliding portion 16b. As a result, the flange portion 16c can be bent inwardly (in the direction approaching the axis) of the housing 16, and the vicinity of the inlet portion 16e of the spool sliding portion 16b is deformed to expand outward (in the direction away from the axis). be able to. As a result, when the surface 30b of the front bush 30 is inclined with respect to the direction substantially orthogonal to the axial direction of the housing 16, it is possible to avoid the malfunction of the spool 17 (spool lock). Further, conventionally, in order to avoid the occurrence of the spool lock, the deformation of the housing 16 (the deflection of the flange portion 16 c and the contraction of the bolt portion 16 a) is slid between the housing 16 and the spool 17. However, since it is possible to reduce “the amount of bending of the flange portion 16c” of the housing 16, it is not necessary to consider the amount of bending of the flange portion 16c. As a result, tolerances such as the inner and outer diameters of the housing 16 and the inner diameter of the sprocket 33 provided on the outer periphery of the housing can be relaxed.

  Further, in the present embodiment, as described above, the variable valve timing mechanism 1 is provided that makes the relative rotation phase of the camshaft 2 variable with respect to the crankshaft by operating the movable member 3 by supplying and discharging oil with the spool built-in bolt 10. Applicable to internal combustion engines. Thereby, the variable valve timing mechanism 1 including the spool built-in bolt 10 that can suppress the bending (distortion) in the spool sliding portion 16b can be configured, and thus the reliability of the variable valve timing mechanism 1 is further improved. Can be made.

-Other embodiments-
The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above description of the embodiments but by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

  For example, in the above-described embodiment, an example in which the spool built-in bolt of the present invention is applied to the valve timing variable mechanism is shown, but the present invention is not limited to this. For example, as long as a spool built-in bolt is applicable, a mechanism other than the variable valve timing mechanism can be applied.

  Moreover, in the said embodiment, although the example which attaches the flange part of the housing of the spool built-in bolt of this invention to the surface of a front bush was shown, this invention is not limited to this. For example, if the flange portion of the housing of the spool built-in bolt can be attached (fastened), it may be attached to the surface of an attachment member such as a washer other than the front bush.

  The present invention can be used for a spool built-in bolt, and more specifically, can be used for a spool built-in bolt including a cylindrical housing and a spool movable in the axial direction in the housing.

1, 1a Valve timing variable mechanism 2 Camshaft 3 Movable member 10, 110 Spool built-in bolt 16, 116 Housing 16a, 116a Bolt portion 16b, 116b Spool sliding portion 16c, 116c Flange portion 16d Inner peripheral surface 16e, 116e Inlet portion 17 117 Spool 17a Outer peripheral surface 30, 130 Front bushing (mounting member)
30b, 130b Surface (mounting surface)
116d end

Claims (5)

In a spool built-in bolt comprising a cylindrical housing and a spool movable in the axial direction in the housing,
The housing includes a spool sliding portion that accommodates the spool so as to be capable of reciprocating in the axial direction, a bolt portion formed on one end side of the housing with respect to the spool sliding portion, and a spool sliding portion. A flange portion formed on the other end side of the housing,
The flange portion is spaced from the spool sliding portion on the other end side of the housing,
A spool built-in bolt, wherein a gap is provided between an inner peripheral surface of the flange portion and an outer peripheral surface of the spool. The spool built-in bolt according to claim 1,
The bolt with a built-in spool, wherein the flange portion is disposed on the other end side of the housing with respect to a portion where the spool sliding portion and the spool are opposed to each other. The spool built-in bolt according to claim 1 or 2,
The spool built-in bolt, wherein an attachment surface of an attachment member to which the flange portion is attached is arranged to be spaced apart from the spool sliding portion on the other end side of the housing. The spool built-in bolt according to claim 3,
When the mounting surface of the mounting member is inclined with respect to a direction substantially orthogonal to the axial direction of the housing, the flange portion and the mounting member are attached when the flange portion is mounted on the mounting member. A spool built-in bolt, wherein the flange portion is bent with a contact portion with a surface as a fulcrum, and the spool sliding portion is deformed so that the vicinity of the end portion on the other end side of the housing expands outward. In the spool built-in bolt according to any one of claims 1 to 4,
The spool built-in bolt is applied to an internal combustion engine including a valve timing variable mechanism that operates a movable member by supplying and discharging oil to vary a relative rotational phase of the camshaft with respect to the crankshaft.
The spool is movable in the axial direction in the housing to supply and discharge the oil to and from the valve timing variable mechanism.
The bolt part is attached to the camshaft,
The spool built-in bolt, wherein the flange portion is fixed by sandwiching the movable member between the flange portion and the cam shaft when the bolt portion is attached to the cam shaft.

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