JP4120064B2 - Valve timing control device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a valve opening / closing timing control device used for controlling the opening / closing timing of an intake valve or an exhaust valve in a valve operating apparatus for an internal combustion engine.
[0002]
[Prior art]
As one of the valve opening / closing timing control devices of this type, a rotor that rotates together with a camshaft of an internal combustion engine, a rotation transmission member that is mounted on the rotor so as to be relatively rotatable within a predetermined range, and that rotates together with a crankshaft, and the rotation transmission member And a vane provided in the rotor so as to partition the recess formed in the inner peripheral surface into an advance chamber and a retard chamber, and the rotation transmission member has the recess in the inner surface, A cylindrical housing member open at both ends in the direction; first and second plate members joined to both ends of the housing member so as to close the opening; and the housing member and the first and second plate members And a timing sprocket that is connected to the crankshaft via a timing chain, for example, disclosed in Japanese Patent Laid-Open No. 10-141022. It is.
[0003]
According to this valve opening / closing timing control device, the hydraulic oil is supplied to the advance chamber and the hydraulic oil is discharged from the retard chamber, so that the rotor and the housing member relatively rotate in one direction, and the crankshaft rotates. The rotational phase of the camshaft is advanced with respect to the phase, and the opening / closing timing of the valve driven by the camshaft is advanced. Conversely, by supplying the hydraulic oil to the retarding chamber and discharging the hydraulic oil from the advance chamber, the rotor and the housing member rotate relative to each other in the other direction, and the camshaft is rotated relative to the rotational phase of the crankshaft. The opening / closing timing of the valve driven by the camshaft is delayed by delaying the rotation phase.
[0004]
The change of the relative rotational phase of the rotor, vane, and housing member described above is performed based on the difference in hydraulic pressure acting on the advance angle chamber and the retard angle chamber. Therefore, the leakage of hydraulic oil between the advance angle chamber and the retard angle chamber greatly affects the performance of the valve opening / closing timing control device. Therefore, in order to suppress this leakage, the material constituting the rotor and vane, the housing member, The materials constituting the plate member members have the same linear expansion coefficient.
[0005]
[Problems to be solved by the invention]
In the valve opening / closing timing control device disclosed in the above publication, the material constituting the rotor and the vane and the material constituting the housing member and each plate member have the same linear expansion coefficient. As the temperature changes, the rotor, vane, housing member, and each plate member expand or contract at substantially the same ratio as their own shapes. Thereby, the increase in the friction and the increase in the clearance at the fitting portion and the joint portion between the members are reduced to maintain the optimum clearance, and the leakage of hydraulic oil or the increase in the sliding resistance is suppressed.
[0006]
By the way, when the temperature of the hydraulic oil rises and the viscosity decreases as the temperature of the internal combustion engine rises, the hydraulic oil leaks between the advance angle chamber and the retard angle chamber even if the clearance remains constant with respect to the temperature change. The amount increases, and in particular, the amount of leakage through the clearance (side clearance) between each plate member and the vane and rotor increases. On the other hand, when the viscosity of the hydraulic oil decreases, the amount of hydraulic oil leaked at each connection portion of the hydraulic oil supply system from the oil pump to the valve opening / closing timing control device also increases in the same way, and the valve opening / closing timing control device is transferred. The amount of hydraulic fluid supplied decreases. For this reason, when the hydraulic oil is at a high temperature, the operation responsiveness of the valve timing control device tends to decrease.
[0007]
In the conventional device described above, the valve opening / closing timing control device when the hydraulic oil is at a high temperature can be optimally maintained regardless of the temperature change of the hydraulic oil, although the clearance at the fitting portion and the joint portion between the members can be optimally maintained. In order to maintain the operation responsiveness, it is necessary to strictly manage the dimensional accuracy of each member. Therefore, there has been a problem that the manufacturing cost of the valve timing control device is remarkably increased.
[0008]
Therefore, according to the present invention, in the valve timing control apparatus, the dimensional accuracy of each member is not strictly controlled, and the space between the advance angle chamber and the retard angle chamber through the side clearance when the hydraulic oil is high temperature with a simple configuration without strict control. It is an object of the present invention to suppress the leakage of hydraulic oil and maintain the operation responsiveness.
[0009]
[Means for Solving the Problems]
The technical means of the present invention taken in order to solve the above problems includes a rotating member that rotates together with either a crankshaft or a camshaft of an internal combustion engine, and the crankshaft that is mounted on the rotating member so as to be relatively rotatable within a predetermined range. Or a rotation transmission member that rotates together with the other of the camshafts, and a recess formed in the inner peripheral surface of the rotation transmission member so as to partition into an advance angle chamber and a retard angle chamber. A cylindrical housing member having at least one axial end opening, and the rotation transmitting member is joined to one end of the housing member so as to close the opening. that the valve timing control apparatus comprising is composed of a plate member, the non-opposing face of the housing of the plate member, the linear expansion of the material constituting the plate member Than the number is that is embedded an insert plate made of a material having a small linear expansion coefficient.
[0010]
According to the above means, when the plate member expands as the temperature of the hydraulic oil rises, the one side surface portion joined to one end of the housing member expands greatly toward the housing member. In addition, the side clearance with the vane (and the housing member) is appropriately reduced, and leakage of hydraulic oil between the advance chamber and the retard chamber through the side clearance is suppressed.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of a valve timing control apparatus according to the present invention will be described with reference to the drawings.
[0013]
The valve timing control apparatus according to the first embodiment shown in FIGS. 1 and 2 includes a rotor 20 that is integrally assembled with the tip of a camshaft 10 that is rotatably supported by a cylinder head 110 of the internal combustion engine. A rotation member comprising: a housing 30, a plate member 40, 50, and a timing sprocket 31 integrally provided on the outer periphery of the housing 30; A torsion spring 60 assembled between the front plates 40, four vanes 70 assembled to the rotor 20, a lock pin 80 assembled to the housing 30, and the like. As is well known, the timing sprocket 31 is configured such that rotational power is transmitted in the clockwise direction in FIG. 2 from a crankshaft (not shown) via a crank sprocket and a timing chain.
[0014]
The camshaft 10 has a known cam that opens and closes an intake valve (not shown), and an advance angle passage 11 and a retard angle passage 12 that extend in the axial direction of the camshaft 10 are provided therein. The advance passage 11 is connected to the first connection port 101 of the control valve 100 through a radial passage provided in the camshaft 10 and a connection passage 16 provided in the annular groove 14 and the cylinder head 110. The retard passage 12 is connected to the second connection port 102 of the control valve 100 through a radial passage provided in the camshaft 10 and a connection passage 15 provided in the annular groove 13 and the cylinder head 110.
[0015]
The control valve 100 can move the spool 104 to the left in the figure against the spring 105 by energizing the solenoid 103, and when not energized, the supply port connected to the oil pump P driven by the internal combustion engine 106 communicates with the second connection port 102, the first connection port 101 communicates with the discharge port 107, and when energized, the supply port 106 communicates with the first connection port 101, and the second connection port 102 It is configured to communicate with the discharge port 107. For this reason, when the solenoid 103 of the control valve 100 is not energized, the hydraulic oil is supplied to the retard passage 12, and when energized, the hydraulic oil is supplied to the advance passage 11, and the energization to the solenoid is duty-controlled by a control device (not shown). The
[0016]
The rotor 20 is made of an iron-based material, and is integrally fixed to the camshaft 10 through a cylindrical spacer 90 with a single mounting bolt 91. The rotor 20 has vane grooves 21 for attaching the four vanes 70 so as to be movable in the radial direction, and the state shown in FIG. 2, that is, the relative phase of the camshaft 10, the rotor 20, and the housing 30 is predetermined. The receiving hole 22 into which a predetermined amount of the head of the cylindrical lock pin 80 is inserted when synchronized with the phase (most retarded angle position), and a passage through which hydraulic oil can be supplied and discharged from the advance passage 11 to the receiving hole 22 23, a passage 24 for supplying and discharging hydraulic oil from the advance passage 11 to the advance oil chamber R1 (except for the upper one in FIG. 2) defined by each vane 70, and a delay defined by each vane 70. The corner oil chamber R2 has a passage 25 for supplying and discharging hydraulic oil from the retard passage 12. 2 is supplied and discharged through a circumferential groove 27 formed on the outer periphery of the rotor 20 with which the outer end of the passage 23 communicates. . In addition, an axial groove 28 is formed on the outer peripheral surface of the rotor 20 where the receiving hole 22 is opened, rearward from the opening of the receiving hole 22 (shown by a chain line in FIG. 2 for reference). An axial groove 26 is formed on the outer peripheral surface of the rotor 20 whose outer end is open, rearward from the opening of the passage. These grooves 28 and 26 are communicated with each other through a circumferential groove 32 (shown by a chain line in FIG. 2 for reference) formed in the rear end surface of the housing 30 at the most retarded position shown in FIG. Therefore, the hydraulic oil from the advance passage 11 is supplied and discharged to the receiving hole 22 only in the most retarded state. Each vane 70 is urged radially outward by a vane spring 71 (see FIG. 1) housed in the bottom of the vane groove 21. Further, the diameter of the receiving hole 22 is set to be a little larger than the outer diameter of the lock pin 80 (and the inner diameter of a later-described retracting hole 34 that is substantially the same as the outer diameter of the lock pin 80).
[0017]
The housing 30 is made of an iron-based material, and is assembled to the outer periphery of the rotor 20 so as to be relatively rotatable within a predetermined range. The housing 30 has a cylindrical shape. The plate member 40 and the plate member 50 are joined to both ends in the axial direction. The housing 30 is integrally connected by four connecting bolts 92, and the rear end to which the plate member 50 is joined. A timing sprocket 31 is integrally formed on the outer periphery. In addition, four protrusions 33 are formed on the inner periphery of the housing 30 at intervals in the circumferential direction so as to protrude radially inward, and the inner peripheral surface of these protrusions 33 slides on the outer peripheral surface of the rotor 20. The housing 30 is rotatably supported by the rotor 20 in a contact configuration, and a retraction hole 34 for receiving the lock pin 80 and the spring 81 is formed in one protrusion 33 and both sides of the retraction hole 34 in the circumferential direction. The cavity portions 36 and 37 are provided in the inner space.
[0018]
The plate member 40 includes an annular front plate 40b made of an iron-based material having a cylindrical portion 41, and an annular intermediate plate 40a made of an aluminum alloy material interposed between the front plate 40 and one end face of the housing 30. It is composed of The front plate 40b and the intermediate plate 40a are provided with communication holes (not shown) corresponding to the cavities 36 and 37, as well as insertion holes (intermediate plate 40a) and female screw holes (front plate b) of the connection bolt 92 (not shown). ) Is provided. Further, the front plate 40 b is provided with a notch for locking one end of the torsion spring 60 to the inner flange at the end of the cylindrical portion 41.
[0019]
The plate member 50 includes an annular rear plate 50b made of an iron-based material, and an annular intermediate plate 50a made of an aluminum alloy material interposed between the rear plate 50b and the other end surface of the housing 30. . Similar to the plate member 40, the rear plate 50 b and the intermediate plate 50 a are provided with communication holes (not shown) corresponding to the hollow portions 36 and 37 and insertion holes for the connection bolts 92.
[0020]
The torsion spring 60 has one end locked in the notch of the front plate 40 b and the other end locked in the rotor 20, and its winding portion extends in the annular space between the cylindrical portion 41 and the spacer 90 in the axial direction. The rotor 20 is urged in the clockwise direction of FIG. 2 with respect to the housing 30, the plate member 40, and the plate member 50. This torsion spring 60 takes into account the force in the retard direction that always acts between the rotor 20 and the housing 30 due to the variable torque acting on the camshaft 10 during operation of the internal combustion engine (force that inhibits the rotation to the advance side). The rotor 20 is constantly urged toward the advance side with a force equivalent to the average fluctuation torque with respect to the housing 30 and the plate members 40, 50, and thereby the rotor 20 is actuated toward the advance side. The responsiveness is improved.
[0021]
Each vane 70 extends radially outward so that the tip is in sliding contact with the inner peripheral surface of the recess 33a formed between the adjacent protrusions 33, and each of the housings 30 between the intermediate plates 40a, 50a. The fluid pressure chamber R0 formed between the protrusion 33 and the rotor 20 is divided into an advance chamber R1 and a retard chamber R2, and the end face in the circumferential direction of the protrusion 33 in which the retraction hole 34 is formed. When the vane 70 comes into contact with the valve, the phase (relative rotation amount) adjusted by the valve opening / closing timing control device is limited.
[0022]
The lock pin 80 is assembled in the retraction hole 34 so as to be slidable in the axial direction, and is urged toward the rotor 20 by a spring 81. The spring 81 is interposed between the lock pin 80 and the retainer 82. In the present embodiment, a groove 35 is formed at the radially outer end of the retraction hole 34 so as to pass through the retraction hole 34 in the axial direction of the camshaft 10, and one end side of which is open on the front end surface of the housing 30. A plate-like retainer 82 is fitted into the groove 35 from the front end surface of the housing 30 toward the rear end, and one end of the spring 81 is locked. The retainer 82 has a pair of tongues, which are held in the radial direction of the housing 30 by being elastically fitted in the grooves 35, and at the same time the plate member 40 and the rear of the housing 30. It is held in the axial direction of the housing 30 between the bottom surface of the groove 35 on the end side. Thereby, when the relative phase of the cam shaft 10 and the rotor 20 and the housing 30 is synchronized at a predetermined phase (most retarded angle position), the lock pin 80 is inserted into the receiving hole 22 of the rotor 20 by a predetermined amount. Thus, relative rotation between the rotor 20 and the housing 30 is restricted.
[0023]
In the valve opening / closing timing control apparatus of the present embodiment configured as described above, the state shown in FIG. 2, that is, the internal combustion engine is stopped and the oil pump P is stopped, and the solenoid 103 of the control valve 100 is not energized. The rotor 20 and the housing 30 are synchronized at the most retarded position, and the head of the lock pin 80 is inserted into the receiving hole 22 by a predetermined amount, and the rotor 20 and the housing 30 are relative to each other at the most retarded position. Even when the internal combustion engine is started and the oil pump P is driven and the control valve 100 is energized in the locked state where the rotation is restricted, the advance passage 11 of the camshaft 10 from the control valve 100, The pressure of the hydraulic oil supplied to the receiving hole 22 through the passage 23, the axial groove 26, the circumferential groove 32 and the axial groove 28 moves from the receiving hole 22 against the lock pin 80 against the spring 81. It takes a predetermined time until the rise in pressure sufficient to cell, the valve timing control apparatus is maintained in the locked state shown in FIGS. 1 and 2, the occurrence of striking sound due to the vane 70 can be prevented.
[0024]
After a predetermined time has elapsed since the internal combustion engine was started and the oil pump P was driven, the pressure of hydraulic oil supplied to the receiving hole 22 from the energized control valve 100 via the advance passage 11 of the camshaft 10 or the like. Rises, the lock pin 80 moves against the spring 81 and comes out of the receiving hole 33 to be unlocked. As a result, the hydraulic pressure and passage 23 and circumferential groove 27 in each advance chamber R1 (excluding those in the upper part of FIG. 2) to which hydraulic oil has been simultaneously supplied via the advance passage 11 and each passage 24 are reduced. 2 is supplied with hydraulic oil from the advance passage 11, and the rotor 20 and the vanes 70 that rotate together with the camshaft 10 are rotated by the hydraulic pressure in the upper advance chamber R1 in FIG. It rotates relative to the members 40, 50, etc., on the advance side (clockwise in FIG. 2). When the rotor 20 and the housing 30 are rotated relative to each other by a predetermined amount after the lock pin 80 is removed from the receiving hole 22, the communication between the passage 23 and the receiving hole 22 is cut off, and the vibration of the lock pin 80 due to the pulsation of hydraulic oil is prevented. Is prevented.
[0025]
When the lock pin 80 is removed from the receiving hole 22, the hydraulic oil is supplied to the advance passage 11 and the retard passage 12 is supplied by increasing the duty ratio of the current supplied to the solenoid 103 of the control valve 100. When the hydraulic oil is discharged, the rotor 20 rotates relative to the rotation transmission member such as the housing 30 from the most retarded position toward the advanced angle side by the hydraulic oil supplied to the advance angle chamber R1. As a result, the duty ratio of the current supplied to the solenoid 103 of the control valve 100 is increased in accordance with the operating state of the internal combustion engine, the hydraulic oil is discharged from the retard chamber R2, and the hydraulic oil is discharged to the advance chamber R1. The rotation transmission member such as the rotor 20 and the housing 30 is rotated relative to each other, and the vane 70 comes into contact with the circumferential end surface of one protrusion 33 as shown by a two-dot chain line in FIG. The volume of the chamber R2 can be minimized (the most advanced position), and the duty ratio of the current supplied to the solenoid 103 of the control valve 100 can be reduced to discharge the hydraulic oil from the advance chamber R1. At the same time, by supplying the hydraulic oil to the retarding chamber R2, the rotation transmission member such as the rotor 20 and the housing 30 is rotated relative to each other to change from the most advanced state to the most retarded position shown in FIG. Done It can accurately control the opening and closing timing of the intake valve in a valve gear of an internal combustion engine. Further, the duty ratio of the current supplied to the solenoid 103 of the control valve 100 is appropriately controlled to supply hydraulic oil to each advance angle chamber R1 and each retard angle chamber R2, so that the rotor 20 and the housing 30, etc. It is also possible to keep the relative phase at an arbitrary phase between the most retarded angle position and the most advanced angle position.
[0026]
By the way, when the temperature of the hydraulic oil rises and the viscosity decreases as the temperature of the internal combustion engine rises, the fitting portion between the housing 30 and the rotor 20 and the joint portion between the rotor 20 and the vane 70 and the plate member with respect to the temperature change. The hydraulic oil easily leaks through, and particularly when the vane 70 is formed thin as in the present embodiment, it operates between the advance chamber and the retard chamber through the side clearance between the vane 70 and the plate member. Oil easily leaks out. On the other hand, when the viscosity of the hydraulic oil decreases, the amount of hydraulic oil leaked at each connection portion of the hydraulic oil supply system from the oil pump to the valve opening / closing timing control device similarly increases, and the valve opening / closing timing control device The amount of hydraulic oil supplied to For this reason, when the hydraulic oil is at a high temperature, the operation responsiveness of the valve timing control device tends to decrease.
[0027]
In this respect, in the present embodiment, as described above, the front plate 40b and the rear plate 50b made of an iron-based material and the both ends of the housing 30 are made of an aluminum alloy material having a larger linear expansion coefficient than the iron-based material. Intermediate plates 40a and 50a are interposed. Therefore, when the plate members 40 and 50 expand as the temperature of the hydraulic oil rises, the intermediate plates 40a and 50a joined to both ends of the housing 30 expand greatly toward the housing 30, the rotor 20 and the vane 70. The side clearances between the intermediate plates 40a and 50a and the rotor 20 and the vane 70 (and the housing 30) are appropriately reduced, and hydraulic fluid leaks between the advance chamber R1 and the retard chamber R2 through the side clearance. It is suppressed. As a result, it is possible to prevent the operation responsiveness of the valve opening / closing timing control device from being lowered when the hydraulic oil is at a high temperature.
[0028]
Further, in the present embodiment, as described above, the side clearance between the plate members 40, 50, the rotor 20, and the vane 70 can be appropriately reduced when the temperature of the internal combustion engine in which hydraulic oil is likely to leak out. Therefore, the dimensional accuracy at room temperature of the plate members 40 and 50, the rotor 20, the vane 70, and the like can be lowered, and the manufacturing cost of the valve opening / closing timing control device can be reduced.
[0029]
FIG. 3 shows a plate member 140 according to the second embodiment of the present invention. In the second embodiment, an insert plate 140b made of an iron-based material is inserted into a front plate 140a formed by die casting of an aluminum alloy material. The insert plate 140b is inserted by being offset to the opposite surface side of the housing, whereby the plate member 140 has a linear expansion coefficient on the opposite surface side of the housing larger than the linear expansion coefficient on the opposite surface side. Yes. According to the second embodiment, when the plate member 140 expands as the temperature of the hydraulic oil rises, the opposing surface side of the housing expands greatly toward the housing, the rotor, and the vane. The side clearance with the vane (and the housing) is appropriately reduced, and the leakage of hydraulic oil between the advance chamber and the retard chamber through the side clearance is suppressed.
[0030]
FIG. 4 shows a plate member 240 according to the third embodiment of the present invention. In the third embodiment, the plate member 240 sandwiches an annular front plate 240c made of an aluminum alloy material, an annular intermediate plate 240b made of synthetic resin such as nylon, and the intermediate plate 240b between the front plate 240c. It has a three-layer structure composed of an annular thin plate 240a made of an iron-based material, and the thin plate 240a side is joined to one end of the housing. FIG. 5 shows a plate member 340 in a modification of the third embodiment. In the plate member 340, an annular groove 340d is formed on one side of the housing of the front plate 340c made of an aluminum alloy material, and an annular intermediate plate 340b made of a synthetic resin such as nylon is fitted in the groove 340d. ing. An annular thin plate 340a made of a ferrous material is interposed between one side of the front plate 340c on the housing side (the intermediate plate 340b is on the same plane) and one end of the housing. Also in the third embodiment and the modification, as in the above-described embodiments, the opposing surface side of the housing of the plate members 240 and 340 greatly expands toward the housing, the rotor, and the vanes as the temperature of the hydraulic oil rises. Therefore, the side clearance between the plate members 240 and 340 and the rotor and vane (and the housing) is appropriately reduced, and leakage of hydraulic oil between the advance chamber and the retard chamber through the side clearance is suppressed. At this time, an increase in friction is avoided by the thin plates 240a and 340a.
[0031]
In the first embodiment described above, the present invention is implemented in the valve opening / closing timing control device assembled to the intake camshaft 10, but the present invention is applied to the valve opening / closing timing control device assembled in the exhaust camshaft. Can be similarly implemented.
[0032]
In the first embodiment described above, the head of the lock pin 80 assembled to the housing 30 in the state where the advance chamber R1 is at the minimum volume (the most retarded angle state) is in the receiving hole 22 of the rotor 20. Although it is configured to be fitted, the head of the lock pin assembled to the housing is fitted into the receiving hole of the rotor in a state where the retarding chamber R2 has a minimum volume (maximum advance angle state). It is also possible to carry out.
[0033]
In the second embodiment, the third embodiment, and the modifications described above, the present invention is applied to the front plate member. However, when the housing member has a cylindrical shape opened at both ends, the rear plate is used. Application to members is also possible.
[0034]
【The invention's effect】
As described above, according to the first aspect of the present invention, when the plate member expands as the temperature of the hydraulic oil rises, the one side surface portion joined to one end of the housing member increases toward the housing member. Because of the expansion, the side clearance between the plate member, the rotor and the vane (and the housing member) can be appropriately reduced, and the hydraulic fluid leaks between the advance chamber and the retard chamber through the side clearance. Can be suppressed. Thereby, it can prevent that the operation responsiveness of the said valve opening / closing timing control apparatus falls at the time of high temperature of hydraulic fluid.
[0035]
In addition, since the side clearance between the plate member, the rotor, and the vane can be appropriately reduced when the temperature of the internal combustion engine where hydraulic fluid is likely to leak, the dimensional accuracy of the plate member, rotor, vane, etc. at room temperature can be increased. The manufacturing cost of the valve opening / closing timing control device can be reduced.
[Brief description of the drawings]
FIG. 1 is a longitudinal side view showing a first embodiment of a valve timing control apparatus according to the present invention.
FIG. 2 is a cross-sectional view taken along line AA in FIG.
FIG. 3 is a cross-sectional view of a plate member in a second embodiment of the valve timing control device according to the present invention.
FIG. 4 is a cross-sectional view of a plate member in a third embodiment of the valve timing control apparatus according to the present invention.
FIG. 5 is a cross-sectional view of a plate member in a modification of the third embodiment of the valve timing control device according to the present invention.
[Explanation of symbols]
10 camshaft 11 advance passage 12 retard passage 20 rotor (rotating member)
30 Housing (Rotation transmission member)
33 Projection 33a Concave 40 Plate member (rotation transmission member)
40a, 50a Intermediate plate 40b Front plate 50b Rear plate 70 Vane R0 Fluid pressure chamber R1 Advance angle chamber R2 Delay angle chamber

Claims (1)

A rotating member that rotates with one of the crankshaft or camshaft of the internal combustion engine;
A rotation transmitting member that is externally mounted on the rotating member so as to be relatively rotatable within a predetermined range and rotates together with the other of the crankshaft or the camshaft;
A vane provided in the rotating member so as to partition a recess formed in the inner peripheral surface of the rotation transmitting member into an advance angle chamber and a retard angle chamber;
The rotation transmission member has the concave portion on the inner peripheral surface, and a cylindrical housing member having at least one axial end opened, and a plate member joined to one end of the housing member so as to close the opening. In the configured valve opening / closing timing control device,
A valve opening / closing timing control device characterized in that an insert plate made of a material having a linear expansion coefficient smaller than that of the material constituting the plate member is embedded on the opposite surface side of the housing of the plate member. .

Images