JP2008240735A - Valve timing control device for internal combustion engine - Google Patents

Abstract

An object of the present invention is to perform accurate positioning in the circumferential direction of a lock piston and a lock hole at the time of assembly to prevent the occurrence of misalignment and facilitate the operation of forming a positioning recess.
In order to ensure good startability of the engine, a lock piston 30 in a vane 22 is engaged with a lock hole 31 of a rear plate 13 to restrain free rotation of the vane member 7 with respect to a housing 5. It has become. A positioning pin that integrally forms a positioning recess 33 on the outer peripheral edge of the housing main body 11 during sintering, and that engages the positioning recess in the axial direction when assembled on the outer peripheral portion near the lock hole of the rear plate. 34 is provided, and the locking piston and the locking hole can be accurately positioned by the positioning action.
[Selection] Figure 1

Description

  The present invention relates to a valve timing control device housing for an internal combustion engine that variably controls the opening / closing timing of an engine valve, which is an intake valve or an exhaust valve of the internal combustion engine, according to an operating state.

  Various conventional valve timing control devices are provided, and one of them is, for example, a vane type device described in Patent Document 1 below.

  In brief, the valve timing control device includes a housing in which a cylindrical housing body and a front cover and a rear plate that close both ends of the housing body are integrally coupled by a plurality of bolts. A vane member fixed to the end of the camshaft is rotatably housed inside the housing, and three substantially trapezoidal shoes projecting inward from each other in the diameter direction on the inner peripheral surface of the housing; An advance oil chamber and a retard oil chamber are formed between the three vanes of the vane member. A sprocket is integrally formed on the outer peripheral side of the rear plate to transmit the rotational force from the crankshaft through the timing chain.

  In addition, a lock pin is provided in a sliding hole formed in the inner axial direction of the one vane so as to be able to protrude and retract, and a lock hole for engaging and disengaging the lock pin is formed on an inner end surface of the rear plate. ing.

  Then, the hydraulic pressure discharged from the electric pump that rotates in the forward and reverse directions is selectively supplied to one of the advance oil chamber and the retard oil chamber according to the engine operating state, and the vane member is moved by the drive oil pressure. The relative rotation phase between the timing pulley and the camshaft is changed by forward and reverse rotation to variably control the opening / closing timing of the intake valve.

Further, when the engine is stopped, the lock pin is engaged in the lock hole, and the relative conversion angle position of the vane member with respect to the housing is held at an optimum position when the engine is started so as to ensure good restartability. It has become.
JP 2003-113703 A

  However, in the conventional valve timing control device, when the components are assembled, the housing main body and the rear plate and the front plate provided with the lock holes are joined together by a plurality of bolts. The bolt and the bolt hole formed on the rear plate side are slightly shifted from each other in the housing circumferential direction, and as a result, the position of the lock hole may be out of the normal position.

  For this reason, when the engine is stopped, the lock pin is difficult to engage with the lock hole at the lock position, and the vane member and the housing may not be restrained.

The invention described in claim 1 includes a housing body formed in a cylindrical shape, a first plate and a second plate provided on both axial sides of the housing body, and the housing body, the first plate, and the second plate. A housing composed of a plurality of bolts integrally connecting the
A sprocket that is integrally provided on the outer peripheral side of the housing body, and that transmits the rotational force from the crankshaft to the housing body;
A plurality of shoes protruding in the circumferential direction from the inner peripheral surface of the housing body;
A vane that is rotatably provided in the housing body and has a plurality of radially extending vanes, and the plurality of vanes and the shoe separate the interior of the housing into an advance oil chamber and a retard oil chamber. A member,
A plurality of seal members fitted in seal grooves formed on the respective front end surfaces of the plurality of vanes, and in sliding contact with the inner peripheral surface of the housing body;
A lock piston provided on one vane of the plurality of vanes, disposed at a position biased in a circumferential direction with respect to the seal member, and provided so as to be movable back and forth in an axial direction;
A lock hole provided in the first plate, wherein the lock piston advances and engages, thereby restricting relative rotation between the vane member and the housing;
A vane provided with the lock piston, and a notch formed on the side opposite to the seal member with respect to the lock piston;
A build-up portion provided on a shoe facing the notch and disposed at a position facing the notch;
A positioning recess provided in the build-up portion of the housing body and formed in a groove shape so as to open to the outer peripheral surface of the housing body;
A circumferential position between the housing body and the first plate at a position where the lock piston is engaged with and released from the lock hole, and is provided on the first plate so as to face the positioning recess in the axial direction. A positioning pin provided so that is determined,
The housing main body and the sprocket are made of a material harder than the first plate.

  1 to 5 show a first embodiment of a valve timing control apparatus for an internal combustion engine according to the present invention.

  That is, the valve timing control device includes a sprocket 1 that is rotationally driven via a timing chain by a crankshaft (not shown) of the engine, a camshaft 2 that is provided to be rotatable relative to the sprocket 1, and a sprocket. 1 and a camshaft 2, and a phase conversion mechanism 3 that converts the relative rotational positions of the two and a hydraulic circuit 4 that operates the phase conversion mechanism 3.

  The camshaft 2 is rotatably supported by a cylinder head (not shown) via a cam bearing, and a plurality of drive cams for opening the intake valve via a valve lifter are integrally provided at a predetermined position on the outer peripheral surface. In addition, a female screw hole 2b into which a cam bolt 6 described later is screwed is formed in the inner axial direction of the one end portion 2a.

  The phase conversion mechanism 3 is fixed to the one end portion of the camshaft 2 from the axial direction by the cam bolt 6 at one end portion of the camshaft 2 and is rotatably accommodated in the housing 5. The five vane members 7 are formed in the housing 5 and separated by five shoes 8 on the inner peripheral surface of the housing 5 to be described later and five vanes 22 to 26 of the vane member 7. A corner oil chamber 9 and an advance oil chamber 10 are provided.

  The housing 5 includes a substantially cylindrical housing body 11, and a front plate 12 and a rear plate 13 that close the front and rear opening ends of the housing body 11, and the housing body 11, the front plate 12, and the rear plate 13 are 5. The bolts 14 are integrally coupled together by tightening from the axial direction.

  The housing body 11 is integrally formed with the sprocket 1 on the outer periphery and is entirely formed of a sintered alloy material. After the sintering molding, the entire body is heat-treated to have high strength and hardness. Yes.

  Further, the five shoes 8 are integrally projected on the inner peripheral surface of the housing body 11 at substantially equal intervals on the circumference. Each of the shoes 8 has a substantially U-shaped side surface, and a substantially U-shaped seal member 16 is fitted in a seal groove formed along the axial direction at each tip portion. In addition, bolt insertion holes 17 through which the bolts 14 are inserted are formed in the inner axial direction on the base side of the shoes 8.

  Further, as shown in FIGS. 3 to 5, the one shoe 8 is integrally formed with a built-up portion 18 on one side in the circumferential direction of the base portion. The build-up portion 18 has an outer surface 18 a formed in a substantially circular arc shape, and is formed in a gently curved shape along the inner peripheral surface 11 a of the housing body 11 from the rising portion on one side surface of the shoe 8.

  The front plate 12 is formed into a relatively thin disk shape by press molding, and has a large diameter hole 12a through which the cam bolt 6 is inserted, and a predetermined position of a hole edge of the large diameter hole 12a. An arc-shaped cutout groove 12b is formed in the upper part. Further, five bolt holes 12c through which the respective bolts 14 are inserted are formed through the circumferentially equidistant positions on the outer peripheral side.

  The rear plate 13 is formed into a disk shape thicker than the front plate 11 by sintering molding, and a support hole 19 is formed in the center, through which one end 2a of the camshaft 2 is inserted and rotatably supported. In addition, five advance oil grooves 20 that extend radially from the edge of the support hole 19 and communicate with the advance oil chambers 10 are formed on the inner end surface. Further, female screw holes 13a into which the male screws at the tip ends of the respective bolts 14 are screwed are formed at circumferentially equidistant positions on the outer peripheral side. As described above, the rear plate 13 is sintered and molded, but is not heat-treated, and therefore has a lower hardness than the housing body 11.

  The vane member 7 is integrally formed of a metal material, and as shown in FIGS. 2 and 3, one end portion 2a of the camshaft 2 is formed by the cam bolt 6 inserted through the insertion hole 7a formed in the center from the axial direction. The vane rotor 21 is axially fixed to the vane rotor 21, and five vanes 22 to 26 project radially from the outer circumferential surface of the vane rotor 21 at substantially equal intervals in the circumferential direction.

  The vane rotor 21 is rotatably supported while sliding on a seal member 16 fitted to the upper surface of the tip of each shoe 8 and is connected to the five retard oil chambers 9 in the inner radial direction. Each of the corner side oil holes 27 is formed through. A fitting groove 21a is formed at the center of the end surface on the camshaft 2 side to fit the tip of one end 2a of the camshaft 2.

  Each of the vanes 22 to 26 is disposed between the shoes 8 and is substantially U-shaped in sliding contact with the inner peripheral surface 11a of the housing body 11 in a seal groove formed in an axial direction on each tip surface. A sealing member 28 having a shape is fitted. Further, as shown in FIGS. 3 to 5, the vanes 22 to 26 have different circumferential widths, and one vane 22 is formed to have a maximum width, and the vanes 22 and the vanes 22 are radially formed. The widths of the two vanes 23 and 24 located at substantially opposite positions are set to be slightly smaller than the maximum width vane 22 and set to an intermediate width, and the vanes 25 and 26 positioned on both sides of the maximum width vane 22 are set to the intermediate width. The width is set to be smaller than the vanes 23 and 24. In this way, the overall weight balance of the vane member 7 is made uniform by changing the width of each of the vanes 22 to 26.

  The vane 22 having the maximum width is formed with a notch 22 a at a portion facing the build-up portion 18 of the one shoe 8. The notch 22a is formed in an arc shape having substantially the same curvature as the arcuate outer surface 18a of the build-up portion 18, and the vane member 7 is rotated in the maximum counterclockwise direction as shown in FIG. Further, it is formed so as to face the outer surface 18a of the build-up portion 18 with a slight arc-shaped gap.

  Further, a substantially triangular projection 22b is integrally formed on the side surface of the vane 22 having the maximum width opposite to the notch 22a. As shown in FIG. 5, when the vane member 7 rotates in the maximum clockwise direction, the protrusion 22b abuts against the side surface of the shoe 8 facing the tip 8 to restrict further rotation, thereby The relative rotation conversion angle with respect to 5 is adjusted.

  Further, a lock mechanism for restricting free rotation of the vane member 7 is provided between the maximum width vane 22 and the rear plate 13.

  The lock mechanism is slidably accommodated in a sliding hole 29 formed through the vane 22 in the direction of the internal axis, and is provided with a lock piston 30 that is movable forward and backward with respect to the rear plate 13 side. A lock hole 31 formed at a predetermined position in the circumferential direction of the inner end surface of the plate 13 so that the distal end portion 30a of the lock piston 30 advances and engages or retreats and is disengaged, and starting of the engine The lock piston 30 includes an engagement / disengagement mechanism that engages or disengages the lock piston 30 with the lock hole 31 according to the state.

  The lock piston 30 is formed in a cylindrical pin shape, and the tip end portion 30a is formed in a stepped substantially frustoconical shape so that it can be easily engaged in the lock hole 31.

  A rectangular notch groove 29 a is formed in the hole edge of the sliding hole 29 on the front plate 12 side, and the notch groove 29 a and the notch groove 12 b of the front plate 12 are always in the rotation range of the vane member 7. It functions as an air vent hole for communicating and ensuring good sliding of the lock piston 30.

  The lock hole 31 is formed in a bottomed shape that does not penetrate the rear plate 13 and is formed at a position biased toward the advance oil chamber 10 in the circumferential direction, as shown in FIGS. 4 and 5. When the lock piston 30 is engaged, the relative conversion angle between the housing 5 and the vane member 7 is set to be on the retard side where the optimum conversion angle is obtained when the engine is started.

  The engagement / disengagement mechanism is elastically mounted between the rear end portion of the lock piston 30 and the inner end surface of the front plate 12, and a coil spring 32 that urges the lock piston 30 in the advance direction, and the lock hole 31. A release hydraulic circuit (not shown) that supplies hydraulic pressure to retract the lock piston 30 is selectively supplied to the retard oil chamber 9 and the advance oil chamber 10 respectively. The hydraulic pressure is introduced through a predetermined oil hole.

  Further, when the components are assembled by the bolts 14 between the housing main body 11 and the rear plate 13, the rotational positions of the housing main body 11 and the rear plate 13, that is, the distal end portion of the lock piston 30 are used. Positioning means for positioning the rotation direction of 30a and the lock hole 31 in the rotational direction is provided.

  That is, as shown in FIGS. 1 and 2, the positioning means includes a positioning recess 33 formed at a predetermined position on the outer peripheral edge of the housing body 11 on the rear plate 13 side, and an outer peripheral side of the rear plate 13. It is comprised from the positioning pin 34 provided in the position corresponding to the said positioning recessed part 33 of an inner end surface.

  That is, the positioning recess 33 is formed at the same time when the housing body 11 is molded by sintering, and as shown in FIGS. A groove is formed in a substantially rectangular shape along the outer end surface on the rear plate 13 side from the outer peripheral surface. That is, the positioning recess 33 is formed with an opening at the side and upper portion so that it does not become an undercut portion at the time of forming the sintered mold.

  On the other hand, as shown in FIG. 3, the positioning pin 34 is press-fitted and fixed in a pin hole 35 formed in the vicinity of the lock hole 31 on the outer peripheral portion side of the rear plate 13 along the axial direction, and the tip end portion 34a is fixed. It protrudes in the direction of the housing body 11 and engages in the positioning recess 33 from the axial direction. The positioning recess 33 is set to have a width that is slightly larger than the outer diameter of the positioning pin 34, and the backlash in the circumferential direction of the housing body 11 and the rear plate 13 is related to the inserted positioning pin 34. Is set so that there is no occurrence.

  The hydraulic circuit 4 selectively supplies the oil pressure to the oil chambers 9 and 10 or discharges the oil in the oil chambers 9 and 10, as shown in FIG. The hydraulic pressure is selectively supplied to each of the passages 36 and 37 through an electromagnetic switching valve 38, the retard passage 36 communicating with the oil hole 27, the advance passage 37 communicating with each of the advance side oil grooves 20. An oil pump 39 and a drain passage 40 that selectively communicates with the passages 36 and 37 via an electromagnetic switching valve 38 are provided.

  The both passages 36 and 37 are connected to the oil holes 27 and the oil grooves through oil passage holes 36a and 37a and groove grooves 36b and 37b formed in the camshaft 2 along the radial direction and the axial direction. 20 communicates.

  The electromagnetic switching valve 38 is a two-way valve and selectively switches between the passages 36 and 37 and the discharge passage 39a and the drain passage 40 of the oil pump 39 by an output signal from a controller (not shown). It has become.

  In the controller, an internal computer inputs information signals from various sensors such as a crank angle sensor, an air flow meter, a water temperature sensor, and a throttle valve opening sensor (not shown) to detect the current engine operating state, A control current is output to the electromagnetic coil of the electromagnetic switching valve 38 in accordance with the engine operating state.

  Hereinafter, the operation of the present embodiment will be described. First, when starting the engine, as shown in FIG. 4, the tip 30a of the lock piston 30 is previously engaged in the lock hole 31, and the vane member 7 is started. It is constrained to the optimum retarded position. For this reason, when start-up is started by turning on the ignition switch, good startability is obtained by smooth cranking.

  Then, in a predetermined low rotation and low load region after the engine is started, the controller cuts off the energization to the electromagnetic coil of the electromagnetic switching valve 38. As a result, the advance side passage 37 communicates with the discharge passage 39a of the oil pump 39, and at the same time, the retard side passage 36 and the drain passage 40 communicate with each other.

  For this reason, the hydraulic oil discharged from the oil pump 39 flows into the advance oil chamber 10 through the advance side passage 37 and the advance oil chamber 10 becomes high pressure, while the retard oil chamber 9 The hydraulic fluid inside is discharged from the drain passage 40 into the oil pan 41 through the retard side passage 36, and the inside of the retard oil chamber 9 becomes low pressure.

  At this time, the hydraulic oil that has flowed into the advance oil chamber 10 flows into the lock hole 31, and the lock piston 30 is moved backward to be removed from the lock hole 31. Thereby, the vane member 7 is ensured to rotate freely.

  Therefore, as the volume of the advance oil chamber 10 increases, the vane member 7 rotates clockwise as shown in FIG. Therefore, the camshaft 2 has a relative rotation angle converted to the advance side with respect to the sprocket 1.

  On the other hand, when the engine shifts to, for example, a high rotation / high load range, a control current is output from the controller to the electromagnetic switching valve 38 to connect the discharge passage 39a and the retard side passage 36, and at the same time, the advance side passage 37. And the drain passage 40 are communicated with each other. As a result, the hydraulic oil in the advance oil chamber 10 is discharged and becomes low pressure, and the hydraulic oil is supplied into the retard oil chamber 9 and the inside becomes high pressure. At this time, since the hydraulic pressure is supplied from the retarded oil chamber 9 into the lock hole 31, the lock piston 30 is kept out of the lock hole 31.

  For this reason, as shown in FIG. 4, the vane member 7 rotates counterclockwise with respect to the housing 5 to convert the relative rotation phase with respect to the sprocket 1 to the retard side.

  As a result, the opening / closing timing of the intake valve is controlled to the retard side, and the output of the engine in such a high rotation / high load region can be improved.

  Further, immediately before the engine is stopped, the supply of hydraulic pressure to the oil chambers 9 and 10 is stopped, and the vane member 7 is relatively rotated to the retard side by the alternating torque acting on the camshaft 2, and the lock piston 30. Is advanced by the spring force of the coil spring pudding 32, and the tip 30 a is engaged in the lock hole 31. In this case, as will be described later, since the positioning of the lock piston 30 and the lock hole 31 in the circumferential direction of the housing 5 is accurately performed when each component member is assembled, the smooth engagement action of the lock piston 30 is achieved. can get.

  That is, in this embodiment, when assembling each constituent member, when the front plate 12 and the rear plate 13 are assembled to the housing body 11 with the bolts 14, the front plate 12 is attached to the front end side of the housing body 11. While temporarily fixing each bolt 14, the positioning pin 34 is engaged with the positioning recess 33 of the housing body 11 from the axial direction while the rear plate 13 is disposed on the rear end side of the housing body 11.

  At this time, the lock piston 30 and the coil spring pudding 32 are accommodated in the sliding hole 29, and the distal end portion 30 a of the lock piston 30 is engaged with the lock hole 31 of the rear plate 13.

  Then, if the bolts 14 are tightened as they are while screwing the front male threads of the bolts 14 into the female screw holes 13 a of the rear plate 13, the plates 12 and 13 can be firmly coupled to the housing body 11. At the same time, the rear plate 13 can be reliably positioned with respect to the housing body 11 in the circumferential direction.

  Therefore, even if the displacement between each bolt 14 and each bolt insertion hole 17 of the housing main body 11 occurs, it is possible to reliably position the lock piston 30 and the lock hole 31 in the circumferential direction of the housing 5.

  As a result, a smooth engagement action with respect to the lock hole 31 of the lock piston 30 when the engine is stopped is obtained. Further, for example, the circumferential displacement between the lock piston 30 and the lock hole 31 due to rotational torque applied to the housing body 11 from the rotation transmission member during driving of the engine can be prevented.

  Further, since the positioning recess 33 and the positioning pin 34 are formed in the housing main body 11 in which the lock piston 30 is formed and the rear plate 13 in which the lock hole 31 is formed, the positioning accuracy of the lock piston 30 and the lock hole 31 at the time of assembly. Will improve.

  In this embodiment, the housing body 11 has a sufficient volume for the relative rotational conversion torque between the housing 5 and the vane member 7 by the five oil chambers 9 and 10 separated by the five vanes 22 to 26. Therefore, the axial length can be shortened as much as possible.

  As a result, the axial length of the entire apparatus can be shortened, so that, for example, the mountability of an engine of the type placed in the engine room is improved, and the degree of freedom in layout is improved.

  Further, since the front plate 12 and the rear plate 13 are coupled to the housing body 11 by five bolts 14 arranged at equal intervals in the circumferential direction, Uniform and good sealing performance by metal touch between the end face and both side faces of the housing body 11 can be ensured.

  Further, since the notch 22a of the vane 22 having the maximum width is formed only on the side of the front end surface of the vane 22 facing the one side surface of the shoe 8, the front end surface of the vane 22 on the opposite side has the Even if the sealing groove is formed, the width of the vane 22 can be made as small as possible. As a result, the relative rotation conversion angle between the housing 5 and the vane member 7 can be increased.

  Moreover, since the positioning recess 33 is provided in the build-up portion 18 of the shoe 8 of the housing body 11, the space of the build-up portion 18 can be used effectively.

  Further, in order to form the positioning recess 33, the thickness of the housing body 11 corresponding to the depth of the positioning recess 33 must be increased, but the shoe 8 is originally formed in a thickness. It is not necessary to increase the thickness of the housing body 11 because of the positioning recess 33. Therefore, it is not necessary to increase the outer diameter of the housing body 11. As a result, the increase in the radial direction of the apparatus can also be suppressed.

  In addition, since the cutout portion 22a and the outer side surface 18a of the built-up portion 18 are formed in an arc shape, corner hitting is prevented and the strength of the vane 22 can be ensured.

  Furthermore, since the housing main body 11 is formed of a relatively high hardness material from the viewpoint of durability, it is difficult to perform drilling by drilling in this part. Since it can be formed by molding together with the housing main body 11, the molding operation becomes easy.

  In addition, since the positioning recess 33 is formed in a groove shape having an open side and upper portion, no undercut portion is generated in the molding, and the molding operation is facilitated.

  Furthermore, since the positioning pin 34 and the positioning recess 33 are disposed at positions sufficiently close to the lock hole 31, the positioning accuracy between the lock piston 30 and the lock hole 31 can be further increased.

  FIG. 6 shows a second embodiment of the present invention in which the structure of the positioning means is changed, and the first positioning recess 33 on the housing body 11 side is the same, but the positioning pin on the rear plate 13 side is the same. Instead, a second positioning recess 35 is formed, and both positioning recesses 33 and 36 are configured to be aligned by the alignment jig 36.

  More specifically, the second positioning recess 36 is formed in an axially penetrating state on the outer peripheral edge of the rear plate 13 in the vicinity of the lock hole 31 and is formed in a substantially U-shaped notch and is radially formed. The outside is formed with an opening. For this reason, when the rear plate 13 is molded, the portion of the first positioning recess 36 does not become an undercut portion like the second positioning recess 33, so that the molding operation is facilitated.

  As shown in FIG. 7, the alignment jig 37 is formed in a bottomed annular shape, and is integrally projected at a substantially central position of the bottom portion 37 a, so that the shaft is inserted into the fitting groove 21 a of the vane rotor 21 during assembly. A substantially cylindrical protrusion 37b that is fitted from the direction and an outer peripheral edge of the bottom portion 37a are integrally provided, and fitted to the outer peripheral surface of the rear plate 13 and the outer peripheral surface of the end portion of the housing body 11 from the outer axial direction during assembly. And an alignment pin 37e press-fitted into a fixing hole 37d formed in the vicinity of the peripheral wall 37c of the bottom portion 37a.

  The outer diameter of the positioning pin 37e is set to be slightly smaller than the inner diameters of the positioning recesses 33 and 36 so that play in the circumferential direction does not occur.

  Therefore, when assembling the front plate 12 and the rear plate 13 to the housing main body 11, the procedure is basically the same as in the first embodiment, but when the rear plate 13 is arranged on the rear end side of the housing main body 11. First, the positioning recesses 33 and 36 are aligned with each other in advance, and then fitted into the rear plate 13 and the housing main body 11 via the projection 37b and the peripheral wall 37c of the alignment jig 37 as shown in FIG. When mating, the alignment pin 37e is inserted into the second positioning recess 36 from the outer axial direction, and is inserted into the first positioning recess 33 as it is.

  If each bolt 14 is tightened in this state, the circumferential positioning of the rear plate 13 with respect to the housing body 11 can be reliably performed. As a result, it is possible to reliably position the lock piston 30 and the lock hole 31 in the rotation direction.

  In addition, after the assembly work is completed, the alignment jig 37 is removed from the axial direction.

  Therefore, according to this embodiment, the same effects as those of the first embodiment can be obtained, and the positioning pins 34 and the like as described above can be obtained simply by forming the second positioning recess 36 in the rear plate 13. Therefore, the manufacturing cost can be reduced.

  The positioning jig 37 may have a further simplified structure. For example, a minus driver may be used, or both positioning recesses may be used without using these jigs. It is also possible to match 33 and 36 by visual recognition.

  The technical ideas other than the invention described in the claims, as grasped from the embodiment, will be described below.

  The valve timing control device for an internal combustion engine according to claim 3, wherein the positioning recess is formed on an outer periphery of the housing main body where the shoe closest to the lock hole is located.

  (2) The internal combustion engine according to (1), wherein the lock piston formed on the vane is disposed at a position biased in a circumferential direction near the positioning recess with respect to the vane. Valve timing control device.

  According to the invention described in claims (1) and (2), since the positioning recess and the positioning pin are arranged as close as possible to the lock hole and the lock piston, the positioning of the lock piston and the lock hole is achieved. Accuracy is improved.

1 is an exploded perspective view showing a first embodiment of a valve timing control device according to the present invention. It is the schematic which shows the hydraulic circuit of the valve timing control apparatus of this embodiment. It is a front view which shows the vane member provided for this embodiment. It is an operation explanatory view showing the state where valve timing by this embodiment was controlled to the retard side. It is effect | action explanatory drawing which shows the state which controlled the valve timing by this embodiment to the advance side. It is a disassembled perspective view which shows the 2nd Embodiment of this invention. It is a longitudinal cross-sectional view which shows the assembly | attachment operation | work of the structural member in this embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Sprocket 2 ... Camshaft 3 ... Phase conversion mechanism 4 ... Hydraulic circuit 5 ... Housing 7 ... Vane member 8 ... Shoe 9 ... Retarded oil chamber 10 ... Advance oil chamber 11 ... Housing body 12 ... Front plate 13 ... Rear plate DESCRIPTION OF SYMBOLS 14 ... Bolt 18 ... Overlay part 22 ... Maximum width vane 23-26 ... Vane 28 ... Seal member 30 ... Lock piston 31 ... Lock hole 33 ... Positioning recessed part 34 ... Positioning pin 36 ... 2nd positioning recessed part

Claims (4)

A housing body formed in a cylindrical shape, a first plate and a second plate provided on both axial sides of the housing body, and a plurality of bolts integrally connecting the housing body, the first plate and the second plate A housing composed of; and
A sprocket that is integrally provided on the outer peripheral side of the housing body, and that transmits the rotational force from the crankshaft to the housing body;
A plurality of shoes protruding in the circumferential direction from the inner peripheral surface of the housing body;
A vane that is rotatably provided in the housing body and has a plurality of radially extending vanes, and the plurality of vanes and the shoe separate the interior of the housing into an advance oil chamber and a retard oil chamber. A member,
A plurality of seal members fitted in seal grooves formed on the respective front end surfaces of the plurality of vanes, and in sliding contact with the inner peripheral surface of the housing body;
A lock piston provided on one vane of the plurality of vanes, disposed at a position biased in a circumferential direction with respect to the seal member, and provided so as to be movable back and forth in an axial direction;
A lock hole provided in the first plate, wherein the lock piston advances and engages, thereby restricting relative rotation between the vane member and the housing;
A vane provided with the lock piston, and a notch formed on the side opposite to the seal member with respect to the lock piston;
A build-up portion provided on a shoe facing the notch and disposed at a position facing the notch;
A positioning recess provided in the build-up portion of the housing body and formed in a groove shape so as to open to the outer peripheral surface of the housing body;
A circumferential position between the housing body and the first plate at a position where the lock piston is engaged with and released from the lock hole, and is provided on the first plate so as to face the positioning recess in the axial direction. A positioning pin provided so that is determined,
The valve timing control device for an internal combustion engine, wherein the housing body and the sprocket are made of a material harder than the first plate. A housing body formed in a cylindrical shape, a first plate provided on one side of the housing body in the axial direction and not subjected to heat treatment, a second plate provided on the other side in the axial direction of the housing body, A housing composed of a plurality of bolts integrally connecting the housing body, the first plate and the second plate;
A sprocket that is integrally provided on the outer peripheral side of the housing body, transmits the rotational force from the crankshaft to the housing body, and is heat-treated with the housing body;
A plurality of shoes protruding in the circumferential direction from the inner peripheral surface of the housing body;
A vane that is rotatably provided in the housing body and has a plurality of radially extending vanes, and the plurality of vanes and the shoe separate the interior of the housing into an advance oil chamber and a retard oil chamber. A member,
A plurality of seal members fitted in seal grooves formed on the respective front end surfaces of the plurality of vanes, and in sliding contact with the inner peripheral surface of the housing body;
A lock piston provided on one vane of the plurality of vanes, disposed at a position biased in a circumferential direction with respect to the seal member, and provided so as to be movable back and forth in an axial direction;
A lock hole provided in the first plate, wherein the lock piston advances and engages, thereby restricting relative rotation between the vane member and the housing;
A vane provided with the lock piston, and a notch formed on the side opposite to the seal member with respect to the lock piston;
A build-up portion provided on a shoe facing the notch and disposed at a position facing the notch;
A positioning recess provided in the build-up portion of the housing body and formed in a groove shape so as to open to the outer peripheral surface of the housing body;
A positioning recess formed in a groove shape so as to open on the outer peripheral surface of the housing body;
A circumferential position between the housing body and the first plate at a position where the lock piston is engaged with and released from the lock hole, and is provided on the first plate so as to face the positioning recess in the axial direction. A valve timing control device for an internal combustion engine, comprising: a positioning pin provided so as to be determined. A housing body formed in a cylindrical shape by a sintered alloy, a first plate formed by a sintered alloy provided on one axial side of the housing body, and a first plate provided on the other axial side of the housing body. A housing composed of two plates and a plurality of bolts integrally connecting the housing body, the first plate and the second plate;
A sprocket that is integrally formed on the outer peripheral side of the housing body by a sintered alloy and that transmits the rotational force from the crankshaft to the housing body;
A plurality of shoes protruding in the circumferential direction from the inner peripheral surface of the housing body;
A bolt insertion hole formed in the plurality of shoes and through which the bolt is inserted;
A vane that is rotatably provided in the housing body and has a plurality of radially extending vanes, and the plurality of vanes and the shoe separate the interior of the housing into an advance oil chamber and a retard oil chamber. A member,
A plurality of seal members fitted in seal grooves formed on the respective front end surfaces of the plurality of vanes, and in sliding contact with the inner peripheral surface of the housing body;
A lock piston provided on one vane of the plurality of vanes, disposed at a position biased in a circumferential direction with respect to the seal member, and provided so as to be movable back and forth in an axial direction;
A lock hole provided in the first plate, wherein the lock piston advances and engages, thereby restricting relative rotation between the vane member and the housing;
A vane provided with the lock piston, and a notch formed on the side opposite to the seal member with respect to the lock piston;
A build-up portion provided on a shoe facing the notch and disposed at a position facing the notch;
A positioning recess provided in the shoe having the build-up portion, disposed on the build-up portion side of the bolt insertion hole, and formed in a groove shape so as to open to the outer peripheral surface of the housing body;
A circumferential position between the housing body and the first plate at a position where the lock piston is engaged with and released from the lock hole, and is provided on the first plate so as to face the positioning recess in the axial direction. A positioning pin provided so that is determined,
The valve timing control device for an internal combustion engine, wherein the housing body and the sprocket are made of a material harder than the first plate. A housing main body formed in a cylindrical shape from a sintered alloy, a first plate that is provided on one side of the housing main body in the axial direction and is formed of a sintered alloy and not subjected to heat treatment, and an axial direction of the housing main body A housing constituted by a second plate provided on the other side, and a plurality of bolts integrally connecting the housing body, the first plate and the second plate;
A sprocket that is integrally provided on the outer peripheral side of the housing body by a sintered alloy, transmits the rotational force from the crankshaft to the housing body, and is heat-treated with the housing body;
A plurality of shoes protruding in the circumferential direction from the inner peripheral surface of the housing body;
A bolt insertion hole formed in the plurality of shoes and through which the bolt is inserted;
A vane that is rotatably provided in the housing body and has a plurality of radially extending vanes, and the plurality of vanes and the shoe separate the interior of the housing into an advance oil chamber and a retard oil chamber. A member,
A plurality of seal members fitted in seal grooves formed on the respective front end surfaces of the plurality of vanes, and in sliding contact with the inner peripheral surface of the housing body;
A lock piston provided on one vane of the plurality of vanes, disposed at a position biased in a circumferential direction with respect to the seal member, and provided so as to be movable back and forth in an axial direction;
A lock hole provided in the first plate, wherein the lock piston advances and engages, thereby restricting relative rotation between the vane member and the housing;
A vane provided with the lock piston, and a notch formed on the side opposite to the seal member with respect to the lock piston;
A build-up portion provided on a shoe facing the notch and disposed at a position facing the notch;
A positioning recess provided in the shoe having the build-up portion, disposed on the build-up portion side of the bolt insertion hole, and formed in a groove shape so as to open to the outer peripheral surface of the housing body;
A circumferential position between the housing body and the first plate at a position where the lock piston is engaged with and released from the lock hole, and is provided on the first plate so as to face the positioning recess in the axial direction. A valve timing control device for an internal combustion engine, comprising: a positioning pin provided so as to be determined.

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