JP2914196B2 - Valve timing control device for internal combustion engine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve timing control device for variably controlling the opening and closing timing of intake and exhaust valves of an internal combustion engine.

[0002]

2. Description of the Related Art For example, in an engine of an automobile or the like,
It is effective to provide a valve timing control device as a means for increasing output and improving fuel efficiency. The valve timing control device is for controlling the opening / closing timing of intake / exhaust valves according to the load state during engine operation.

As one example, there is a type in which a moving member is interposed between a timing pulley rotated in synchronization with the rotation of an engine and a cam shaft for driving a valve. The outer spline provided on the outer periphery of the moving member is meshed with the spline provided on the inner periphery of the timing pulley. An inner spline provided on the inner periphery of the moving member is meshed with a spline provided on the outer periphery of the camshaft. Due to this engagement, the driving force of the timing pulley is transmitted to the camshaft via the moving member.

At least one set of the timing pulley and the moving member, and at least one of the moving member and the camshaft is in helical spline engagement. Accordingly, when a biasing force such as a hydraulic pressure of a hydraulic mechanism or a spring is applied to the moving member, the moving member is simultaneously moved in the torsional direction while being moved in the axial direction of the camshaft. . Thereby, the relative rotation phase of the camshaft with respect to the timing pulley is shifted, and the opening / closing timing of the valve is adjusted.

[0005] However, in the valve timing control device having the above-described structure, there is rattling in the timing pulley and the moving member, and the spline meshing portion of the moving member and the timing pulley. For this reason, when the rotation of the camshaft fluctuates due to the fluctuation of the cam drive torque, there is a problem that abnormal noise and vibration due to toothing are generated at the respective spline meshing portions.

In order to prevent the above-mentioned toothing, a design may be adopted in which the clearance between the splines is eliminated. However, it is practically difficult in consideration of dimensional tolerances during processing, ease of assembly, and the like.

Conventionally, in order to solve such a problem, for example, there is one disclosed in Japanese Patent Application Laid-Open No. 4-187804. That is, the moving member is divided into a first moving member meshed with the camshaft, and a second moving member meshed with the first moving member with a straight spline and meshed with the timing pulley. . A coil spring is interposed between the first and second moving members, and each of the coil springs is urged toward the timing pulley and the camshaft, which are engaged with the helical spline, in a direction of reducing rattling. ing.

[0008]

However, in the technique disclosed in the above publication, the moving member is divided into two parts and a coil spring is interposed between the two gears. For this reason, the number of parts has been increased, the number of steps for forming a spline having accuracy on the inner and outer peripheral surfaces of both gears has been increased, and the number of processing and assembling steps has been increased, resulting in an increase in manufacturing costs. In addition, the two-part structure of the moving member and the interposition of the coil spring inevitably increase the weight of the device, which hinders the lightening of the engine.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a valve timing control apparatus for an internal combustion engine which can reduce rattling between splines with a simple structure and can prevent generation of abnormal noise and vibration.

[0010]

In order to achieve the above object, according to the first aspect of the present invention, a rotating body is connected to a camshaft.
Up by the clearance (δE) of
Between the outer spline of the moving member and the spline of the mounting member
Moves downward by its own weight by the clearance (δD) between
In this state, the clearance (δA) between the camshaft and the mounting member was set to be larger than the clearance (δB) between the spline of the mounting member and the inner spline of the moving member .

[0011] In the present invention of claim 2, the clearance (.delta.W) between the inner peripheral surface and the mosquito <br/> Mushafuto of the rotating body, Haujin
Between the spline of the moving member and the outer spline of the moving member.
The spline of the mounting member and the moving part
Add clearance (δZ) to the inner spline of the material.
Approximate the amount obtained.

[0012]

According to the first aspect of the present invention, the rotating body is rotated in synchronization with the rotation of the internal combustion engine, and the rotation of the rotating body drives and rotates the camshaft via the moving member. Then, for example, the moving member is moved in the axial direction of the camshaft by a hydraulic mechanism. At the same time,
Since one of the spline of the housing, the outer spline of the movable member, the inner spline of the movable member, and the spline of the mounting member is a helical spline, the movable member is rotated in the torsion direction. Thereby, the rotation phase of the camshaft with respect to the rotating body is changed, and the opening / closing timing of the valve is adjusted.

When the mounting member is assembled, the mounting member is displaced downward by its own weight. Then, rotate the rotating body
Lift by the clearance (δE) between the shaft
Moving member, the outer spline of the moving member and the mounting member
Own weight by the clearance (δD) between the spline
The clearance (δA) between the camshaft and the mounting member is reduced by the clearance between the spline of the mounting member and the inner spline of the moving member.
(ΔB) . Therefore, it is possible to surely reduce the play between the spline of the mounting member located on the displacement side of the mounting member and the inner spline of the moving member.

According to the second aspect of the invention, the rotation of the internal combustion engine is transmitted to the rotating body via the belt body. At this time, due to the belt load, the rotating body, the inner peripheral surface of the rotating body,
The camshaft is displaced by the distance between the camshaft and the outer peripheral surface.
Then, a clearance (.delta.W) between the inner peripheral surface and mosquito Mushafuto of the rotary member, the spline and the moving part of the housing
The clearance (δY) between the outer spline of the material and
Between the spline of the mounting member and the inner spline of the moving member
To the amount obtained by adding the clearance ([delta] Z) between them . Therefore, for example, when assembling the mounting member to the camshaft, the mounting member is mounted such that the axis of the mounting member is shifted from the axis of the camshaft by the clearance between the maximum camshaft and the inner peripheral surface of the mounting member. Suppose. Even in such a case, the displacement between the splines can be reliably reduced by the displacement of the rotating body, and the rattling can be reduced.

[0015]

First Embodiment A first embodiment of the present invention will be described below with reference to the drawings. As shown in FIG. 1, a camshaft 1 for driving an intake valve has a journal 1
It is supported by a cylinder head 2 of an engine as an internal combustion engine with α, and extends in the front-back direction (refers to the left-right direction on the paper surface; hereinafter, the left side is the front side and the right side is the rear side in each drawing). The flange 1β is provided on the outer peripheral surface of the camshaft 1 near the journal 1α.

The mounting member 4 comprises a cylindrical main body 4α, and a donut-shaped flange 4β protruding from the inner peripheral surface of the main body 4α. In the main body 4α, the mounting portion 4γ is located on the rear side from the flange portion 4β. The mounting member 4 is externally fitted to the front end of the camshaft 1 with its mounting portion 4γ, and is fixed to the camshaft 1 by bolts 5 at the flange portion 4β. Detent pin 6 fixed to camshaft 1
Is a through hole 4 formed at an eccentric position of the flange portion 4β.
at δ with play in the radial direction.
The detent is done. The helical spline 12 is formed on the outer peripheral surface of the mounting member 4, and in FIG.
α indicates a plurality of teeth forming the spline 12, and 12β indicates a groove formed between the teeth.

A boss 7β is integrally formed at the center of the timing pulley 7 as a rotating body, and the timing pulley 7 is fitted around the front outer periphery of the camshaft 1 with the boss 7β. The front end face of the boss portion 7β is in contact with the rear end face of the mounting member 4, and the rear end face is in contact with the flange portion 1β of the camshaft 1. It is held between the unit 1β.

The timing belt 8 is wound around the timing pulley 7 and a timing pulley attached to a crankshaft (not shown) of the engine. The rotation of the crankshaft is transmitted through the timing belt 8. It is transmitted to the timing pulley 7.

The housing 9 is fastened to the front side of the timing pulley 7 by bolts at the outer peripheral end thereof, and a space surrounded by the inner peripheral surface of the housing 9 and the front side of the timing pulley 7 forms a boss of the timing pulley 7. An annular space K surrounding the portion 7β and the mounting member 4 is formed. The helical spline 13 is formed on the inner peripheral surface of the front end of the housing 9. In FIG. 5, 13α denotes a plurality of teeth forming the spline 13, and 13β denotes each tooth 1.
The grooves formed between 3α are shown. Opening 9
α is formed at the center of the housing 9 and its opening 9
α is closed by a lid 9β.

The moving member 10 includes a cylindrical moving member main body 10α and a flange portion 10β formed at the rear end of the moving member main body 10α. The circumferential groove 10γ is recessed in the outer peripheral surface of the flange portion 10β,
The seal member 11 is accommodated in γ. The seal member 11 seals between the outer periphery of the flange portion 10β and the inner periphery of the housing 9. The inner helical spline 16 is formed on the inner peripheral surface of the front end portion of the moving member 10, and the outer helical spline 17 is formed on the outer peripheral surface of the moving member main body 10α. In FIG. 5, 16α and 17α indicate teeth, and 16β and 17β indicate grooves.

The moving member 10 is disposed in the annular space K. The inner helical spline 16 of the moving member 10, the helical spline 12 of the mounting member 4, the outer helical spline 17 and the helical spline 13 of the housing 9 are connected. Each is engaged. Therefore, the camshaft 1 is rotationally driven via the moving member 10 and the mounting member 4 by the rotational force of the crankshaft transmitted to the timing pulley 7.

In FIGS. 2 to 5, the splines 12, 16 and 1 are shown for easy understanding of the embodiment.
The gap between 3 and 17 is exaggerated. The annular space K is defined by the flange portion 10β of the moving member 10, and a space on the front side is a first pressure chamber 14 and a space on the rear side is a second pressure chamber 15. Then, the hydraulic oil is supplied to one of the first pressure chamber 14 and the second pressure chamber 15 by a hydraulic oil supply device (not shown), and the hydraulic oil in the other pressure chamber 15 or 14 is discharged,
A moving force in the axial direction of the camshaft 1 is applied to the moving member 10 by the hydraulic pressure.

In this embodiment, FIG. 2 (FIG. 1)
And a clearance δA between the outer peripheral surface of the distal end portion of the camshaft 1 and the inner peripheral surface of the mounting portion 4γ of the mounting member 4, as shown in FIG. Is larger than the clearance δB between the spline 12 of the moving member 10 and the inner spline 16 of the moving member 10.

That is, the inner diameter of the mounting portion 4γ of the mounting member 4 is φA1, the outer diameter of the tip of the camshaft 1 is φA2, and each tooth portion 16α in the inner spline 16 of the moving member 10.
When the diameter is set as φB1 connecting the tips of the circles, and the diameter of the circle passing through the bottom surface of each groove 12β in the spline 12 of the mounting member 4 is set as φB2, the following equation (1) is satisfied.

ΔA = φA1−φA2> δB = φB1−φB2 (1) Accordingly, the mounting member 4 can be displaced up to δA in the radial direction of the camshaft 1, but the through hole of the flange portion 4β. 4
ε and the through hole 4δ into which the detent pin 6 is inserted have a size that allows the displacement.

Further, in this embodiment, FIGS.
As shown in FIG. 1 (representing a portion surrounded by a circle B in FIG. 1) and the inner peripheral surface of the flange portion 10β of the moving member 10 and the boss portion 7 of the timing pulley 7 corresponding thereto.
The clearance δC between the outer circumferential surface of β and the moving member 10
Outer spline 17 and spline 13 of housing 9
Is configured to be larger than the clearance δD between them.

That is, the inner diameter of the flange portion 10β of the moving member 10 is φC1, the outer diameter of the boss portion 7β of the timing pulley 7 is φC2, and the diameter of the circle connecting the tips of the teeth 13α of the spline 13 of the housing 9 is φ.
When D1 is set as the diameter of a circle passing through the bottom surface of each groove 17β in the outer spline 17 of the moving member 10, φD2, the following equation (2) is satisfied.

ΔC = φC1−φC2> δD = φD1−φD2 (2) Further, FIG. 4 (representing a portion surrounded by a circle C in FIG. 1)
As shown in the figure, there is a clearance δE: φE between the outer peripheral surface of the camshaft 1 and the boss 7β of the timing pulley 7.
1−φE2 is provided.

The operating oil supply device is controlled according to the operating state of the engine, and the first or second pressure chambers 14, 1
The hydraulic oil is supplied to one of the pressure chambers 5 and the hydraulic oil in the other pressure chambers 15 and 14 is discharged. The moving member 10 is moved rightward or leftward in FIG. 1 along the axis of the camshaft 1 by the hydraulic pressure of the hydraulic oil supplied to one of the pressure chambers 14 and 15. For this reason, the helical splines 12, 16 meshing with each other as described above.
The camshaft 1 is relatively rotated with respect to the timing pulley 7 in accordance with the helical angles of 13 and 17, and the rotational phase of the camshaft 1 with respect to the timing pulley 7 is displaced.
The intake valve opening / closing timing is varied in the advance or retard direction.

The valve timing control device having the above configuration is
It is assembled as follows. As shown in FIG.
The housing 9 is assembled to the timing pulley 7 in advance, and the moving member 10 and the mounting member 4 are arranged inside the housing 9, and the splines 12, 16, 13 and 17 are meshed with each other. The lid 9β of the opening 9α of the housing 9 is removed. Then, the unit in this state is attached to the camshaft 1 as shown in FIG. That is, the boss 7β of the timing pulley 7
In addition, the mounting portion 4γ of the mounting member 4 is externally fitted to the outer peripheral surface of the camshaft 1, and the flange portion 4β of the mounting member 4 is engaged with the distal end surface of the camshaft 1.

At this time, the unit is lifted by the clearance δE between the inner peripheral surface of the boss 7β of the timing pulley 7 and the outer peripheral surface of the camshaft 1 located on the boss 7β. Then, the unit is fixed to the camshaft 1 with the bolts 5 and the detent pins 6. At this time, since the relationship between the housing 9 and the moving member 10 satisfies the expression (2), the moving member 10 is moved downward with respect to the housing 9 by the clearance δD due to its own weight. Therefore, there is no play between the spline 13 of the housing 9 and the outer spline 17 of the moving member 10. On the other hand, the mounting member 4 moves downward by its own weight until the spline 12 meshes with the inner spline 16 of the moving member 10 without any gap.

That is, the spline 12 of the mounting member 4 is reliably engaged with the inner spline 16 of the moving member 10 without any gap by the configuration satisfying the above expression (1). The amount of downward movement of the mounting member 4 is equal to the clearance δB and smaller than the clearance δA, so that the amount of downward movement is small. In other words, the amount of displacement of the mounting member 4 with respect to the axis of the camshaft 1 is small. In addition, if the clearance δE between the timing pulley 7 and the camshaft 1 is larger than the clearance δB, the moving member 10 moves toward the axis of the camshaft 1 by δE−δD, and the eccentric amount of the mounting member 4 becomes δB. − (ΔE−δD)
Therefore, the mounting member 4 with respect to the axis of the camshaft 1
In addition, the amount of eccentricity of the moving member 10 is further reduced.

After the assembly is completed, the opening 9α of the housing 9 is closed with the lid 9β. As described above, in the present embodiment, the helical splines 12, 16, and 13, with only a simple operation of slightly adjusting the assembly position of the unit.
The rattling at the meshing portions 17 can be eliminated. Therefore, it is possible to suppress the generation of noise and vibration due to cam torque fluctuation with a simple configuration without increasing the number of parts.

Further, since the mounting member 4 moves only the clearance δB smaller than the clearance δA at the maximum, the eccentricity of the mounting member 4 with respect to the axis of the camshaft 1 is suppressed to be small, and the above-described effect of reducing the rattle noise is achieved. hand,
In addition, the resistance between the splines in the movement of the mounting member 4 can be suppressed low, and the power loss can be suppressed.
In addition, if the clearance δE is set larger than the clearance δB, the amount of eccentricity of the mounting member 4 and the moving member 10 can be further reduced, the resistance between splines can be further reduced, and the power loss can be further suppressed.

Further, the rattling between the splines is reduced by utilizing the own weight movement of the mounting member 4 and the moving member 10. Therefore, each spline 12, 16, and 13, 1
7, the engagement of the moving member 10 is not tight, the movement responsiveness of the moving member 10 is not reduced, and the power loss is prevented as described above.

[0036]

Second Embodiment Hereinafter, a second embodiment of the present invention will be described with reference to the drawings. Note that, compared to the first embodiment, the member configuration of the present embodiment has a similar configuration, and only the method of setting the clearance between the members is different. Accordingly, the description will be given with reference to FIG. 8 which schematically shows each member by changing the reference numerals indicating the clearances between the members with the same member numbers.

As shown in FIG. 8, the clearance δW between the inner peripheral surface of the boss portion 7β of the timing pulley 7 and the corresponding outer peripheral surface of the camshaft 1 is adjusted by the mounting member 4
The clearance δX between the inner peripheral surface of the mounting portion 4γ and the outer peripheral surface of the tip end of the camshaft 1 is configured to be larger.

That is, the boss 7 of the timing pulley 7
The inner diameter of β: φW1, the outer diameter of the camshaft 1 corresponding to the boss 7β: φW2, the inner diameter of the mounting portion 4γ in the mounting member 4: φX1, the outer diameter of the tip of the camshaft 1: φX.
By setting 2, respectively, the following equation (3) is satisfied.

ΔW = φW1−φW2> δX = φX1−φX2 (3) The clearance δW is a clearance δY between the spline 13 of the housing 9 and the outer spline 17 of the moving member 10, and a moving member. 10 inner splines 1
6 and a clearance δZ between the spline 12 of the mounting member 4 and the spline 12.

That is, the spline 13 of the housing 9
Diameter of the circle connecting the tips of the teeth 13α at φY1
(Appears the same as φD1 in FIG. 5), the moving member 10
Diameter of a circle passing through the bottom surface of each groove 17β in the outer spline 17 of φ: φY2 (also φD2), diameter of a circle connecting the tip of each tooth 16α in the inner spline 16 of the moving member 10: φZ1 (φB1), When the diameter of a circle passing through the bottom surface of the groove 12β in the spline 12 of the attachment member 4 is set to φZ2 (φB2), the following equation (4) is satisfied.

ΔW ≒ δY + δZ = (φY1−φY2) + (φZ1−φZ2) (4) In the valve timing control device of the present embodiment having the above-described configuration, when the drive is transmitted from the crankshaft, the belt is used as a belt. A belt load is applied to the timing pulley 7 in the direction of arrow G in FIG. 8 by the timing belt 8, and the timing pulley 7 is displaced by a maximum δW. Due to the displacement of the timing pulley 7, the clearance between the spline 12 of the mounting member 4 and the inner spline 16 of the moving member 10 is biased, and the play between the splines 12, 16 is reliably reduced.

The structure that satisfies the expression (3) is as follows. For example, the camshaft 1 of the mounting member 4
At the time of assembling, it is assumed that the mounting member 4 is mounted with the axis of the camshaft 1 shifted from the axis of the camshaft 1 by a maximum δX. In such a case, if δX> δW, the displacement δW of the timing pulley 7 is equal to the clearance (maximum δX) between both splines 12 and 16 between the mounting member 4 and the moving member 10.
Is not absorbed, and the clearance between the splines 12 and 16 is not absorbed.

Further, according to the displacement of the timing pulley 7 at the maximum δW, first, the housing 9 is displaced by the same amount in the direction of the camshaft 1. This displacement causes the housing 9
And the outer spline 17 of the moving member 10
Is naturally narrower and δW> δY, so that the play between the splines 13 and 17 is reliably reduced. Further, the timing pulley 7 can be moved by the remaining δW−δY, and from Expression (4), δW−δY ≒ δZ. That is, it is possible to surely reduce the play between the splines 12 and 16 having the maximum interval of δZ.

As described above, in the present embodiment, a simple structure that only sets a predetermined clearance is used. In the meshing portion of each of the splines 12, 16, 13, and 17, generation of rattling noise and vibration noise when cam torque fluctuates. Can be suppressed.

In the second embodiment, the rattling reduction effect can be stably exhibited at the load position by assembling the mounting member 4 with less shaft friction. The present invention can be implemented as follows without departing from the spirit of the present invention. (1) In both of the above embodiments, a valve timing control device having a configuration in which the timing pulley 7 is changed to a timing sprocket and the timing belt 8 is changed to a timing chain may be embodied. (2) The spline 13 of the housing 9 and the outer spline 17 of the moving member 10 or the spline 12 of the inner member 16 of the moving member 10 and the spline 12 of the mounting member 4 are embodied in a helical spline mesh. . (3) The present invention is embodied in a valve timing control device for an exhaust valve.

The technical ideas other than the claims that can be grasped from the above embodiment will be described. (1) The rotator 7 is provided with a boss 7β, and the moving member 10 is configured to slide on the outer peripheral surface of the boss 7β, and further moves with the outer peripheral surface of the boss 7β. The clearance δC between the inner peripheral surface of the member 10 and the moving member 1
0 outer spline 17 and housing 9 spline 1
3. The valve timing control device for an internal combustion engine according to claim 1, wherein the clearance is set to be larger than a clearance δD between the valve timing control device and the engine.

In this way, the play between the outer spline 17 of the moving member 10 and the spline 13 of the housing 9 can be reliably reduced .

(2 ) The method of assembling the valve timing control device according to claim 1 or (1), wherein the step of assembling and fixing the mounting member 4 to the camshaft 1 includes the step of: The valve timing control device is mounted after being lifted upward by a clearance δE between the inner peripheral surface of the boss 7β and the outer peripheral surface of the camshaft 1 located on the boss 7β.

In this way, it is possible to reduce the shaft rubbing of the mounting member 4 and the moving member 10 and to reduce the rotational resistance.

[0050]

According to the first and second aspects of the present invention, it is possible to reduce the backlash of each spline meshing portion with a simple configuration in which the clearance between each member is set to a predetermined value. As described above, the manufacturing cost does not increase and the weight increases due to the rattling reduction configuration.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a valve timing control device.

FIG. 2 is an enlarged view of a circle A portion in FIG. 1 and is a schematic diagram in which intervals between members are exaggerated.

FIG. 3 is a schematic diagram of a circle B portion in FIG. 1;

FIG. 4 is a schematic diagram of a circle C portion in FIG. 1;

FIG. 5 is a partial end view of a housing, a moving member, and a mounting member.

FIG. 6 is a schematic diagram showing a procedure for assembling the device.

FIG. 7 is also a schematic diagram.

FIG. 8 is a schematic diagram showing the second embodiment, in which the intervals between the members are exaggerated.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Cam shaft, 4 ... Mounting member, 7 ... Timing pulley as a rotating body, 9 ... Housing, 10 ... Moving member, 12, 13, 16, 17 ... Helical spline, delta
A: Clearance between camshaft and mounting member, δ
B: Clearance between the spline of the mounting member and the inner spline of the moving member.

Claims (2)

(57) [Claims] 1. A camshaft for driving a valve, a mounting member fitted and fixed to the camshaft and having a spline on an outer peripheral surface, and a rotation fitted to the camshaft and connected to a crankshaft of an internal combustion engine. A housing having a spline on the inner peripheral surface, the housing being provided to surround the camshaft on the side surface of the rotating body, and a housing provided between the housing and the mounting member so as to be movable in the axial direction of the camshaft. A spline on the surface, at least one of which has a cylindrical moving member that is a helical spline, and meshes the spline of the housing, the outer spline of the moving member, the inner spline of the moving member, and the spline of the mounting member, respectively. By moving the moving member in the axial direction of the camshaft, the rotation of the camshaft with respect to the rotating body In a valve timing control device which changes a phase and controls opening / closing timing of a valve, a clearance between the rotating body and the camshaft is provided.
(ΔE), and moving the moving member
The gap between the outer spline and the spline of the mounting member
Moved downward by its own weight by the clearance (δD)
In this state, the valve timing control of the internal combustion engine is set such that the clearance (δA) between the camshaft and the mounting member is larger than the clearance (δB) between the spline of the mounting member and the inner spline of the moving member. apparatus. 2. A camshaft for driving a valve, a mounting member fitted and fixed to the camshaft and having a spline on an outer peripheral surface, and an outer fitting on the camshaft, and a belt body connected to a crankshaft of an internal combustion engine. And a housing provided to surround the camshaft on the side surface of the rotating body, and having a spline on an inner peripheral surface thereof, and being movable in the axial direction of the camshaft between the housing and the mounting member. A spline on the inner and outer peripheral surfaces, at least one of which is provided with a cylindrical moving member which is a helical spline, the spline of the housing, the outer spline of the moving member, the inner spline of the moving member, and the spline of the mounting member. By moving the moving member in the axial direction of the camshaft, Changing a rotational phase of Mushafuto, in the valve timing control apparatus adapted to control the opening and closing timings of the valve, the clearance (.delta.W) between the inner peripheral surface and mosquito Mushafuto of the rotating body, the moving member and the splines of the housing Outside
At the clearance (δY) between the side spline and the mounting part
Between the material spline and the inner spline of the moving member.
A valve timing control device for an internal combustion engine that approximates an amount obtained by adding a clearance (δZ) .