JP3473368B2 - Variable rotation phase difference mechanism - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotation in which the relative rotational phase of a partition member in a hydraulic chamber is adjusted by hydraulic pressure so that the rotational phase difference between two rotary shafts can be variably set within an allowable range. The present invention relates to a phase difference variable mechanism, for example, a rotary phase difference variable mechanism that is applied to an internal combustion engine and can variably control the opening / closing timing of an intake valve and an exhaust valve.

[0002]

2. Description of the Related Art Conventionally, a variable valve timing mechanism has been put into practical use, which changes the valve timing of an intake valve and an exhaust valve according to the operating state of an internal combustion engine. As a variable valve timing mechanism of this type, for example, as disclosed in Japanese Patent Application Laid-Open No. 9-60508, by changing the rotational phase (displacement angle) of the camshaft with respect to the crankshaft, the camshaft is rotated along with the rotation. A mechanism is known in which the valve timing of a valve that is opened and closed is changed.

In this Japanese Patent Laid-Open Publication No. 9-60508, as schematically shown in FIG. 14, a timing pulley 502 rotating in synchronization with a crankshaft and an internal rotor 504 connected to a camshaft are relatively rotated. As a result, the variable valve timing mechanism 500 for changing the valve timing is shown.

The timing pulley 502 of the variable valve timing mechanism 500 has a plurality of hydraulic chambers therein, two hydraulic chambers 506 in JP-A-9-60508. An internal rotor 504 is arranged at the center of the timing pulley 502, and partition members (so-called vanes) 508 are radially provided on the internal rotor 504 and inserted into the hydraulic chambers 506. Is divided into a first pressure chamber 510 and a second pressure chamber 512.

The timing pulley 502 is connected to a crankshaft (not shown) via a timing belt (not shown), and the internal rotor 504 is connected to a camshaft (not shown).

The hydraulic pressure generated by driving the internal combustion engine is supplied to the pressure chambers 510 and 512 through a passage (not shown) in the camshaft and a passage (not shown) in the internal rotor 504. The relative rotational position of the partition member 508 within the hydraulic chamber 506 is desired based on the relative relationship between the pressure of the first pressure chamber 510 and the pressure of the second pressure chamber 512 on both sides of each partition member 508. The timing pulley 502 and the internal rotor 504 integrally rotate in this setting state.

Such a variable valve timing mechanism 500
At the time of starting the internal combustion engine, since the internal rotor 504 is at the most displaced position and the hydraulic pressure is not yet generated, each partition member 5 is locked by the lock mechanism (not shown).
08 is the most displaced position, that is, the internal rotor 504 is fixed at the most retarded position with respect to the timing pulley 502. In this way, when the internal combustion engine is started, the relative rotation of the timing pulley 502 and the internal rotor 504 is restricted, and the intake valve timing interlocking with the internal rotor 504 is
The timing is set at the most retarded side (hereinafter, referred to as "most retarded valve timing"). Further, when the internal combustion engine is started, the internal rotor 504 causes the timing pulley 5 to move.
If it is in the most advanced angle position with respect to 02, it is held at the timing changed to the most advanced angle side (hereinafter referred to as the “most advanced valve timing”).

When a sufficient hydraulic pressure is generated as the internal combustion engine is operated after the internal combustion engine is started, the lock mechanism is disengaged by the action of this hydraulic pressure. Then, when the hydraulic pressures of the first pressure chamber 510 and the second pressure chamber 512 on both sides of each partition member 508 differ due to the hydraulic pressure adjustment of the control circuit or the like according to the operating conditions, each partition member 508 is Lower pressure chamber 5
Moving toward 10, 512, the timing pulley 50
2 and the inner rotor 504 rotate relative to each other. By the relative rotation of the timing pulley 502 and the internal rotor 504 in this way, the rotational phase of the camshaft coupled to the internal rotor 504 and the reference rotational phase of the internal combustion engine, that is, the rotational phase of the valve and the crankshaft. A rotation phase difference occurs between the rotation phase and the rotation phase. Therefore, the valve timing with respect to the crank angle is changed to the advance side or the retard side.

[0009]

By the way, regarding each valve timing of the intake valve or the exhaust valve,
In each case, there is a suitable timing range for each model of the internal combustion engine. Therefore, the range from the most retarded valve timing to the most advanced valve timing, that is, the allowable range of the rotational phase difference must be set naturally for each model of the internal combustion engine.

Conventionally, this setting is based on the width W1 of the hydraulic chamber 506.
And the width W2 of the partition member 508 are set. That is, the design of the timing pulley 502 and the internal rotor 504 had to be changed for each model of the internal combustion engine. As described above, there is a problem that it is difficult to reduce the manufacturing cost because the common parts cannot be used between the models.

According to the present invention, even if the allowable range of the rotational phase difference is different between the models of the internal combustion engine,
An object of the present invention is to provide a rotary phase difference variable mechanism having a configuration in which some of the components can be used in common and contribute to the reduction of manufacturing cost.

[0012]

According to a first aspect of the present invention, there is provided a rotation phase difference varying mechanism according to claim 1, wherein a first rotating body interlocked with one of the two rotating shafts and the other of the two rotating shafts. A second rotary body that is interlocked with the rotation axis of the first rotary body,
At least one hydraulic chamber formed between the ridges is formed therein.
The second rotating body has at least one partition member that is inserted into the hydraulic chamber to partition the interior of the hydraulic chamber into a first pressure chamber and a second pressure chamber, The partition member is moved between the ridges by supplying the hydraulic pressure to one or both of the first pressure chamber and the second pressure chamber, and the partition member is relatively moved between the first rotating body and the second rotating body. A rotation phase difference variable mechanism capable of variably setting a rotation phase difference between the two rotation shafts within an allowable region by rotating the rotation shaft, wherein the first rotating body has a plurality of the hydraulic chambers. ,Previous
Note that the second rotating body has the same number as the hydraulic chambers that partition the hydraulic chambers.
With the partition member of, the width of the partition member is
One rotation phase difference limiting contact member that is set to two or more types and that contacts the second rotating body is attached so as to project into one or both of the first pressure chamber and the second pressure chamber. The second member is attached to the contact member for limiting the rotation phase difference.
By abutting the partition member of the rotating body whose width is not the maximum, the internal area of the rotation phase difference allowable region is set according to the mounting position of the rotation phase difference limiting contact member.
The feature is that it is restricted so that it differs depending on the model of the institution .

As described above, by providing one rotating phase difference limiting contact member, when the second rotating body rotates in the hydraulic chamber, the partition member of the second rotating body contacts the rotating phase difference limiting contact member. By abutting against the member, the allowable range of the rotational phase difference can be limited by the rotational phase difference limiting abutting member so as to be different between the models of the internal combustion engine . Therefore, as for the desired range of the rotational phase difference, only one rotational phase difference limiting contact member is attached so as to project to the limit position of the allowable range in one or both of the first pressure chamber and the second pressure chamber. Can be achieved with. For this reason, it is not necessary to change the design of either or both of the first rotating body and the second rotating body, and the rotational phase difference variable mechanism can be used even between internal combustion engine models having different allowable ranges of the rotational phase difference. At least some of the parts can be shared, which contributes to a reduction in manufacturing costs. In the hydraulic chamber, the rotation phase difference limiting contact member is located at the position where it is most likely to contact the partition member even in the configuration of the second rotating body. It is the easiest to provide the surface, and the rotary phase difference variable mechanism can be easily designed.

[0014]

[0015]

[0016]

[0017]

The larger the width of the partition member, that is, the length of the partition member in the circumferential direction of the second rotating body, the larger the width of the partition member is. The allowable range becomes smaller. Conversely, the smaller the length of the partition member, the larger the allowable range of the rotational phase difference. Therefore, by selecting the width of the partition member arranged in the hydraulic chamber in which the rotational phase difference limiting contact member is present from two or more types, it is possible to allow various rotational phase differences even if the same component is used. A range can be realized. Therefore, the degree of freedom of the allowable range of the rotational phase difference is further increased, the parts of the rotational phase difference variable mechanism can be commonly used, and the manufacturing cost can be further reduced.

According to a second aspect of the present invention, the first rotary body has a plurality of hydraulic chambers, and the second rotary body has the same number of partition members as the hydraulic chambers that partition the hydraulic chambers. The width of the hydraulic chamber may be set to two or more types.

[0020] Thus, according to claim 2, unlike the first aspect, a plurality of hydraulic chambers of the first rotating body, and the width of the liquid chamber into two or more. Therefore, even if the rotation phase difference limiting contact member is mounted at the same relative position with respect to the inner surface of the hydraulic chamber, the mounting position of the rotation phase difference limiting contact member is set to any width of the hydraulic chamber. A desired permissible range of the rotational phase difference can be set by selecting the hydraulic chamber such as mounting. Therefore, the degree of freedom of the allowable range of the rotational phase difference is further increased, the parts of the rotational phase difference variable mechanism can be commonly used, and the manufacturing cost can be further reduced.

Further, as described in claim 3 , the contact surface of the second rotating body with which the contact member for limiting the rotational phase difference abuts is abutted according to the radial position of the second rotating body. It may be formed so that the rotational phase of the contact surface changes. For example, the contact surface of the second rotating body may be formed obliquely at an angle with respect to the radial direction of the second rotating body.

In such a structure in which the rotational phase of the contact surface changes depending on the radial position of the second rotating body, even if the rotational phase difference limiting contact members are arranged in the same hydraulic chamber Depending on the radial position of the phase difference limiting contact member,
That is, the rotation phase of the second rotating body in the contact state differs depending on the distance from the rotation center of the second rotating body to the rotation phase difference limiting contact member. This indicates that the allowable range of the rotational phase difference can be adjusted by moving the rotational phase difference limiting contact member away from or near the rotational center of the second rotating body. From this, the allowable range of the rotational phase difference can be arbitrarily set only by sliding and positioning the rotational phase difference limiting contact member in the same hydraulic chamber. Therefore, the components of the rotary phase difference varying mechanism can be commonly used, which contributes to further reduction in manufacturing cost.

Here, as described in claim 3 , the abutment surface of the second rotating body with which the abutment member for limiting the rotational phase difference abuts is provided with a step portion, so that the aforesaid second surface is provided. The contact surface may be formed so that the rotational phase of the contact surface changes depending on the radial position of the rotating body.

That is, as the structure in which the rotational phase changes in the radial direction of the second rotary body, the contact surface of the second rotary body may change continuously, but the contact surface of the second rotary body may change. The contact surface may be changed stepwise by providing the portion.

Also by this, the allowable range of the rotational phase difference can be adjusted by moving the rotational phase difference limiting contact member away from or near the rotational center of the second rotating body, and the same hydraulic chamber can be adjusted. Even in the configuration in which the contact member for limiting the rotational phase difference is arranged in, the allowable range of the rotational phase difference can be arbitrarily set,
This makes it easier to share the components of the variable rotation phase difference mechanism, which can contribute to the reduction of manufacturing cost. As described in claim 4 , the contact surface of the second rotating body with which the rotational phase difference restricting contact member abuts is inside the recess provided on the side surface of the partition member on the hydraulic pressure chamber side. May be provided in the. If a relatively thick contact member for limiting the rotational phase difference is used, the allowable range of the rotational phase difference may be narrowed. That is, compared with the case where there is no contact member for limiting the rotation phase difference,
When the contact member for limiting the rotational phase difference is provided, the diameter of the contact member for limiting the rotational phase difference is usually excluded from the possible range of the allowable range of the rotational phase difference. However, as described in claim 4 , the contact surface of the second rotating body with which the rotation phase difference limiting contact member abuts is inside the recess provided on the side surface of the partition member on the hydraulic chamber side. And the contact member for limiting the rotation phase difference is the second member.
When contacting the contact surface of the rotating body, the entire rotation phase difference limiting contact member, or at least a part of the rotation phase difference limiting contact member enters the recess and It cancels all or part of the diameter of the abutment member. Therefore, the setting range of the allowable range of the rotational phase difference can be made sufficiently wide. Therefore, in the setting of the allowable range of the rotational phase difference, the degree of freedom becomes high, so that even between the models of the internal combustion engines having different allowable ranges of the rotational phase difference, at least some of the components of the variable rotational phase difference mechanism, This makes it easier to standardize and can contribute to further reduction in manufacturing cost. Moreover, since the width of the material of the portion other than the recess can be maintained, the durability and strength of the other portions can be maintained high.

[0026]

As described in claim 5 , the contact member for limiting the rotational phase difference may be attached so as to be positionally adjustable in the radial direction of the second rotating body. That is, in the case where the contact surface of the second rotating body is formed so that the rotation phase changes in the radial direction of the second rotating body, the internal surface of each second internal combustion engine is simply moved in the radial direction of the second rotating body. By adjusting the position of the contact member for limiting the rotational phase difference, it is possible to cope with various allowable ranges of the rotational phase difference. Therefore, it becomes easier to share the components of the variable rotational phase difference mechanism, and the manufacturing cost is further improved. Can contribute to the reduction of

Further, as described in claim 6 , the contact member for limiting the rotational phase difference may be attached so as to be positionally adjustable in the circumferential direction of the second rotating body. With such a configuration, it is possible to cope with various allowable ranges of the rotational phase difference by simply adjusting the position of the rotational phase difference limiting contact member in the circumferential direction of the second rotating body for each model of the internal combustion engine. As a result, it is possible to standardize the parts of the rotary phase difference variable mechanism.
It is easier to do, and it can contribute to further reduction of manufacturing cost.

[0029]

[0030]

[0031]

[0032]

BEST MODE FOR CARRYING OUT THE INVENTION [First Embodiment] In a gasoline engine as an internal combustion engine, a variable valve timing mechanism (VVT) as a rotational phase difference varying mechanism provided for an intake camshaft will be described.

FIG. 2 is a plan view showing the arrangement of the intake side camshaft 11 and the exhaust side camshaft 70. FIG. 2
In FIG. 3, the left side is the tip end side of the cam shafts 11, 70, and the right side is the base end sides of the cam shafts 11, 70.

The intake-side camshaft 11 and the exhaust-side camshaft 70 are rotatably supported on the upper surface of the cylinder head 14. Both camshafts 11 and 70 are
Each has a plurality of cams 75. An intake valve 77 is arranged below the cam 75 belonging to the intake camshaft 11, and an exhaust valve 78 is arranged below the cam 75 belonging to the exhaust camshaft 70.

The VVT 12 is provided at the tip of the intake side camshaft 11. The driven gear 17 connected to the VVT 12 and the drive gear 74 provided at the tip of the exhaust side camshaft 70 mesh with each other. A pulley 71 is provided at the base end of the exhaust side camshaft 70, and the pulley 71 is connected to a crankshaft (not shown) via a timing belt 72.

When the crankshaft is rotated by the driving force of the engine or the starter, the rotational force is transmitted to the pulley 71 via the timing belt 72 and the exhaust side camshaft 70 is rotated. The rotational force of the exhaust side camshaft 70 is transmitted through the gears 74 and 17 to the intake side camshaft 11
And the intake side camshaft 11 is rotated. In this way, by rotating both cam shafts 11 and 70, the intake valve 77 and the exhaust valve 78 are opened and closed.

FIG. 1 is a sectional view showing a VVT 12 provided at the tip of the intake side camshaft 11. FIG. 3 shows FIG.
3 shows a cross section taken along line 3-3 of FIG. The diagram of the internal rotor 19 and its related parts shown in FIG.
It is depicted as a cross-sectional view along line 1.

As shown in FIG. 1, the upper end of the cylinder head 14 and the bearing cap 15 rotatably support the journal 11a of the intake side camshaft 11.
The inner rotor 19 fixed to the tip end surface of the intake side camshaft 11 by a bolt 22 has a knock pin (not shown).
Prevents the intake side camshaft 11 from rotating,
It rotates integrally with the intake camshaft 11. The inner rotor 19 has a plurality of vanes, four vanes 24a, 24b, 24c, 24d (corresponding to partition members) on its outer peripheral surface in the present embodiment.

On the other hand, the driven gear 17 provided so as to cover the tip of the intake camshaft 11 and rotatable relative to the intake camshaft 11 has a plurality of external teeth 17a on its outer circumference. . The side plate 18, the housing 16 and the cover 2 which are sequentially attached to the tip end surface of the driven gear 17.
0 is bolt 2 as a part of VVT housing
It is fixed to the driven gear 17 by 1 and rotates integrally with the driven gear 17. Further, the cover 20 covers the tip surfaces of the housing 16 and the internal rotor 19. The housing 16 is provided so as to include the inner rotor 19, and has a plurality of protrusions 25 on its inner peripheral surface.

One vane 24a of the inner rotor 19 is
It has a through hole 32 extending along the axial direction of the intake camshaft 11. The lock pin 33 that is movably accommodated in the through hole 32 has an accommodation hole 33a therein. The spring 35 provided in the accommodation hole 33a
Urges the lock pin 33 toward the side plate 18. When the lock pin 33 is opposed to the locking hole 34 provided in the side plate 18, the lock pin 33 is locked in the locking hole 34 by the urging force of the spring 35, so that the inner rotor 19 is relatively opposed to the side plate 18. The rotation position is fixed. As a result, the relative rotation of the inner rotor 19 with respect to the housing 16 is prohibited, and the relative rotation positional relationship is maintained, so that the intake camshaft 11 and the driven gear 17 rotate integrally.

Further, the inner rotor 19 has an oil groove 36 formed on its tip surface. The oil groove 36 connects the arc-shaped elongated hole 37 opening to the cover 20 and the through hole 32. The oil groove 36 and the elongated hole 37 have a function of discharging the air or oil located on the tip side of the lock pin 33 inside the through hole 32 to the outside.

As shown in FIG. 3, the inner rotor 19 has a flat cylindrical boss 23 located at the center thereof and the boss 2 of the same.
Four vanes 24a, 24b, 24c, and 24d formed at equal intervals of, for example, about 90 ° are provided. On the other hand, the housing 16 has four protrusions 25 arranged on the inner peripheral surface thereof at substantially equal intervals, like the vanes 24a to 24d. Hydraulic chambers 26a, 26b formed between the protrusions 25,
The corresponding vanes 24a to 24d are inserted in 26c and 26d (corresponding to the hydraulic chambers). The outer peripheral surface of each vane 24a to 24d is in contact with the inner peripheral surface of each hydraulic chamber 26a to 26d, and the tip end surface of each protrusion 25 is in contact with the outer peripheral surface of the boss 23. In this way, each hydraulic chamber 26a-26d
By being divided into two by the inserted vanes 24a to 24d, each of the vanes 24a to 2 in the rotation direction is formed.
The first hydraulic chambers 30a, 30b, 3 are provided on both sides of 4d, respectively.
0c, 30d (corresponding to a first pressure chamber) and second hydraulic chambers 31a, 31b, 31c, 31d (corresponding to a second pressure chamber) are formed.

In each of the vanes 24a to 24d, the first hydraulic pressure located on the side opposite to the rotation direction of the driven gear 17 (shown by an arrow in FIG. 3) (hereinafter, this direction is defined as "retarding direction"). Oil is supplied to the chambers 30a to 30d when advancing (advancing) the valve timing. Oil is supplied when the valve timing is delayed (retarded) to the second hydraulic chambers 31a to 31d located on the same side as the rotation direction (hereinafter, this direction is defined as the “advance direction”). It

The vanes 24a to 24d and the ridges 25 have grooves 27 and 40 at their tips. In the groove 27 of each vane 24a to 24d, a seal plate 28 and the seal plate 28 are provided in each of the hydraulic chambers 26a to 26.
A leaf spring 29 for urging the inner peripheral surface of d is provided.
Similarly, in the groove 40 of each protrusion 25, the seal plate 4
1 and a leaf spring 42 that urges the seal plate 41 toward the outer peripheral surface of the boss 23.

The lock pin 33 operates as shown in FIGS. 4 and 5. 4 and 5 are sectional views taken along line 4-4 of FIG. In FIG. 4, the internal rotor 19 is at the most retarded position (however, in FIG. 3, it is not at the most retarded position and is advanced slightly), and the vanes 24a to 24d have the ridges 2 formed therein.
It is in a stationary state in contact with 5. At this time, vane 24
Since the lock pin 33 provided in a does not face the locking hole 34, the tip portion 33b of the lock pin 33 has a locking hole 3
Not inserted in 4.

The hydraulic pressure in the first hydraulic chambers 30a to 30d has risen to zero or sufficiently high, for example, when the engine is started, or when hydraulic control by an electronic control unit (ECU) not shown is not started. When not present, a reverse torque is generated in the intake side camshaft 11 due to the cranking operation at the time of starting, and the internal rotor 19 relatively rotates in the advance direction with respect to the housing 16. As a result, the lock pin 33 reaches the relative rotation position where it can be inserted into the locking hole 34, and the lock pin 33 is inserted into the locking hole 34 and locked as shown in FIG. In this way, the lock pin 33 is locked in the locking hole 34.
When locked to the inner rotor 19 and the housing 16
The relative rotation with respect to is prohibited, and the inner rotor 19 and the housing 16 can rotate together.

To release the lock pin 33 locked in the locking hole 34, hydraulic pressure is supplied from the second hydraulic chamber 31a to the annular oil space 13 via the oil passage 59 shown in FIGS. 4 and 5. It is done by That is, as the hydraulic pressure supplied to the annular oil space 13 rises, the lock pin 33 disengages from the locking hole 34 against the biasing force of the spring 35,
The lock of the lock pin 33 is released. Further, the hydraulic pressure is supplied from the first hydraulic chamber 30a to the locking hole 34 via the oil passage 54, and the unlocked state of the lock pin 33 is reliably maintained.
As described above, in the state where the lock pin 33 is unlocked, relative rotation between the housing 16 and the internal rotor 19 is allowed and is supplied to the first hydraulic chambers 30a to 30d and the second hydraulic chambers 31a to 31d. The relative rotation phase of the inner rotor 19 with respect to the housing 16 can be adjusted according to the hydraulic pressure.

In one second hydraulic chamber 31c, as shown in FIG. 6 (a sectional view taken along line 5-5 in FIG. 3), from the side plate 18 to the variable angle limiting pin 80 (rotational phase difference limiting pin). (Corresponding to a contact member and a pin member) is provided so as to project. The variable angle limiting pin 80 includes a protruding portion 80a and a male screw portion 80b, and the female screw portion 18 provided on the side plate 18 is provided.
By attaching the male screw portion 80b to a, the protruding portion 80a is mounted so as to protrude into the second hydraulic chamber 31c. Therefore, even if the vane 24c is rotated by the hydraulic pressure of the first hydraulic chamber 30c in the direction of narrowing the second hydraulic chamber 31c (the direction of the arrow in the drawing), and the contact surface 92c thereof is brought into contact, the pressing force received from the vane 24c (Other first hydraulic chamber 3
The vane 24c is completely stopped against the pressing force of the hydraulic pressure of 0a, 30b, 30d).
It is possible to prevent further relative rotation of the entire body toward the advance side.

Therefore, due to the existence of the variable angle limiting pin 80, the relative rotation of the internal rotor 19 toward the advance side is limited to the position where the vane 24c abuts against the variable angle limiting pin 80. That is, the variable angle limiting pin 80 limits the rotational phase difference of the internal rotor 19 with respect to the housing 16 on the advance side. The relative rotation of the internal rotor 19 toward the retard angle side is limited to the position where the vanes 24a to 24d contact the protrusion 25.

If there is no variable angle limiting pin 80,
The vanes 24a, 24c, and 24d are movable between two adjacent ridges 25 as a rotation phase difference allowable region. However, since only the vane 24b has a narrow vane width on the second hydraulic chamber 31b side as described later, the first hydraulic chamber 30 does not need the variable angle limiting pin 80.
The ridge 25 on the b side is reached, but the ridge 25 on the second hydraulic chamber 31b side is not reached.

The four vanes 24a to 24d are the same as the vane 2
In addition to the special provision of the lock pin 33, 4a has the following morphological differences. That is, as shown in FIG. 7, the vane widths θa, θb, θ represented by angles are shown.
c and θd are different from each other. Further, regarding the vane 24d, the contact surface 92d, which is the side surface on the second hydraulic chamber 31d side, is provided with the notch 94 having a depth of the angular width θp, so that the vane width θq at the notch 94 portion is It is smaller than θd.

These vane widths θa, θb, θc, θd,
The magnitude relation of θq is as shown in the following equation.

[0053]

## EQU00001 ## .theta.b <.theta.q <.theta.c = .theta.d <.theta.a Among these, the hydraulic chamber 26 in which the three vanes 24b, 24c, 24d in which the oil passages 54, 59 are not formed are arranged.
The widths represented by the angles b, 26c, and 26d are all the same. Only the hydraulic chamber 26a in which the vane 24a is arranged has a large width according to the vane width θa. Therefore,
As mentioned above, if there is no variable angle limiting pin 80, then 3
The two vanes 24a, 24c, 24d are movable between two adjacent ridges 25 to a position where they abut the ridge 25.

Next, based on FIG. 1, each of the first hydraulic chambers 30a ...
An oil supply / discharge structure for supplying / discharging oil to / from 30d and each of the second hydraulic chambers 31a to 31d will be described. The cylinder head 14 has a first oil passage 38 formed therein,
It has a second oil passage 39. The first oil passage 38 is formed inside the intake side camshaft 11 through an oil groove 44 formed in the entire circumference of the intake side camshaft 11 and an oil hole 45 formed inside the journal 11a. It leads to the passage 46. The front end side of the oil passage 46 opens into the annular space 47. Radially formed inside the boss 23
The one oil hole 48 includes the annular space 47 and the first hydraulic chambers 30a to 30a.
The oil supplied to the annular space 47 is communicated with the first hydraulic chambers 30a to 30d.

The second oil passage 39 is connected to the intake camshaft 11
Communicates with an oil groove 50 formed on the entire circumference of. The oil hole 56 formed in the intake-side camshaft 11, the oil passage 57, the oil hole 53, and the oil groove 58 formed in the driven gear 17 are the oil groove 50 and the annular oil groove 51 formed in the side plate 18. Communicate with. As shown in FIGS. 1 and 3, the side plate 18 has four oil holes 52 that open in the vicinity of the side surface of each protrusion 25. Each oil hole 52 includes an oil groove 51 and each second hydraulic chamber 31a-3.
1d is connected and the oil in the oil groove 51 is supplied into each of the second hydraulic chambers 31a to 31d.

The first oil passage 38, the oil groove 44, the oil hole 45, the oil passage 46, the annular space 47 and the oil holes 48 form an oil passage P1 for supplying oil to the first hydraulic chambers 30a to 30d. Constitute. Second oil passage 39, oil groove 50, oil hole 56, oil passage 5
7, oil hole 53, oil groove 58, oil groove 51 and each oil hole 52
Defines an oil passage P2 for supplying oil to each of the second hydraulic chambers 31a to 31d. Electronic control unit (EC
U) is the first hydraulic chamber 30 through these oil passages P1 and P2.
The hydraulic pressure supplied to the a to 30d and the second hydraulic chambers 31a to 31d is controlled. It is well known that a flow rate control valve such as an oil control valve is used in controlling the hydraulic pressure.

On the other hand, the vane 24a having the through hole 32 is provided with an oil passage 54 as shown in FIG.
Reference numeral 4 communicates with the first hydraulic chamber 30a and the locking hole 34, and the hydraulic pressure supplied to the first hydraulic chamber 30a allows the locking hole 3
It is also possible to supply to 4.

Further, in the through hole 32, the lock pin 3
An annular oil space 13 is formed between the vane 3 and the vane 24a. This annular oil space 13 communicates with the second hydraulic chamber 31a via an oil passage 59 shown in FIG.
The hydraulic pressure supplied to 1a can also be supplied to the annular oil space 13.

Next, the operation of the VVT 12 according to the present embodiment configured as described above will be described below. V
In the VT12, before the engine is started, the first
Hydraulic chambers 30a-30d and second hydraulic chambers 31a-31d
Oil is not supplied to the inside of both hydraulic chambers 30a to 30d,
Most of the portions 31a to 31d are filled with air. At this time, it is assumed that the internal rotor 19 is already at the most retarded position with respect to the housing 16 as shown in FIG. 8 by the control by the ECU when the engine is stopped.

In this state, the lock pin 33 is not acted on by the oil pressure facing the spring 35. However, since the lock pin 33 is present at the relative rotational position out of the locking hole 34, the lock pin 33 urged by the spring 35 comes into contact with the surface of the side plate 18 as shown in FIG.
It is not locked in the locking hole 34.

When cranking is started from this state to start the engine, a positive torque and a reverse torque are generated in the camshafts 11 and 70 due to the nature of the engine of the present embodiment. At this time, since the engine is starting and the control of the ECU is not started, both hydraulic chambers 30
Since the hydraulic pressures of a to 30d and 31a to 31d have not yet risen, the internal rotor 19 is generated at the timing of the reverse torque generation.
Advances with respect to the housing 16.

When the vanes 24a to 24d are separated from the protrusion 25 by this advance angle, that is, when the vanes 24a to 24d are advanced from the most retarded position, the lock pin 33 and the locking hole 34 are brought into a rotational position where they coincide with each other. Therefore, the lock pin 33 and the locking hole 34 are locked. Therefore, the internal rotor 19 and the housing 16 are integrated during cranking. This integrated state is set so that the valve timing is at a suitable relative rotation position (a relative rotation position near the most retarded angle position) when the engine is started.

When the engine is started in the state of being fixed at such a suitable relative rotation position, first, the second hydraulic chamber 31
The hydraulic pressure is supplied to a to 31d, and the second hydraulic chambers 31a to 3d are supplied.
1d fills with oil after a few seconds. However, at this time,
The ECU that performs hydraulic control controls the first hydraulic chamber 30a until the second hydraulic chambers 31a to 31d are completely filled with oil.
The supply of hydraulic pressure to 30d is not controlled. That is, E
By such control of the CU, the locking of the lock pin 33 is continued for a while. That is, the relative rotation position suitable for starting continues for a while.

Next, when the hydraulic control of the ECU is started to supply the hydraulic pressure to the first hydraulic chambers 30a to 30d and the hydraulic pressure of the second hydraulic chambers 31a to 31d exceeds the urging force of the spring 35, the above-mentioned operation is performed. As described above, the lock pin 33 is housed in the through hole 32, and the lock pin 33 with respect to the locking hole 34 is
Is unlocked. As a result, relative rotation between the housing 16 and the internal rotor 19 is possible.

After the locking of the lock pin 33 is released in this way, hydraulic pressure is supplied from the second hydraulic chambers 31a to 31d to the annular oil space 13 via the oil passage 59, and also to the first via the oil passage 54. 1 From the hydraulic chambers 30a to 30d to the locking hole 34
Is also supplied with hydraulic pressure. As a result, the state in which the lock pin 33 is housed in the through hole 32 continues and the unlocked state is maintained until the hydraulic pressure becomes less than the urging force of the spring 35 due to the engine being stopped thereafter.

As described above, after releasing the lock of the lock pin 33, the ECU controls the two hydraulic chambers 30a to 30d and 31a to 31d.
By controlling the supply of hydraulic pressure to the intake valve 77, the valve timing of the intake valve 77 is continuously (steplessly) changed to a predetermined timing between the most retarded timing and the most advanced timing, or the valve timing is changed. Can be held.

However, as shown in FIG. 9, the contact position 92c, which is the side surface of the vane 24c on the side of the second hydraulic chamber 31c, is located at the protruding portion 8 of the variable angle limiting pin 80, as shown in FIG.
This is the position where it abuts 0a. Therefore, the timing of the most advanced angle is adjusted by the mounting position of the variable angle limiting pin 80. In the present embodiment, this VVT 12
The mounting position of the variable angle limiting pin 80 is determined so that the timing of the most advanced angle becomes suitable in conformity with the model of the gasoline engine in which is used.

When the engine is stopped, the E
The most retard command is issued from the CU, and the second hydraulic chambers 31a-3a
By setting the pressure of 1d higher than the pressure of the first hydraulic chambers 30a to 30d, the vanes 24a to 24d move toward the most retarded position. At this time, since the state in which the lock pin 33 is housed in the through hole 32 continues, the lock pin 33 housed in the through hole 32 is not locked in the locking hole 34, After passing through the upper part, it reaches the most retarded position and returns to the state shown in FIGS.

According to the present embodiment described above, the variable angle limiting pin 80 has the protrusion 80a with the hydraulic chamber 26c.
By arranging so as to project inward, the allowable range of the rotational phase difference of the angular width θ1 as shown in FIG. 9 can be realized.

Further, in the case of an engine in which a wider allowable range of the rotational phase difference is suitable for the advance side, as shown in FIG. 10, the second hydraulic chamber 31b in the hydraulic chamber 26b in which the vane 24b is inserted is shown. In, a female screw portion is formed on the side plate 18 at the same position as that arranged in the hydraulic chamber 26c, and the variable angle limiting pin 80 of the same shape is screwed and attached. By changing the position of the variable angle limiting pin 80 in this way, the allowable range of the rotational phase difference is changed from the angular width θ1 to the angular width θ2.
By changing to, the timing on the most advanced side can be further widened.

Further, the allowable range of the rotational phase difference is widened to the advance side as compared with the case of FIG. 9, but in the case of the engine in which the allowable range of the rotational phase difference which is not as large as that of FIG. 10 is preferable, as shown in FIG. , The hydraulic chamber 26 in which the vane 24d is inserted
In the second hydraulic chamber 31d in d, a female screw portion is formed on the side plate 18 at the same position as that arranged in the hydraulic chamber 26c, and the variable angle limiting pin 80 of the same shape is screwed and attached. As a result, the notch 94 (which also corresponds to the contact surface) in the contact surface 92d contacts the protrusion 80a, so that the allowable range of the rotational phase difference is changed from the angular width θ1 to the angular width θ3. , The timing on the most advanced side can be widened to the moderate side.

When the variable angle limiting pin 80 is arranged in the second hydraulic chamber 31d of the hydraulic chamber 26d as described above, the variable angle limiting pin 80 is arranged so as to be displaced toward the center side. Abutting surface 92d at a portion other than the notch 94
The protruding portion 80a of the variable angle limiting pin 80 can be brought into contact with. That is, even within the same second hydraulic chamber 31d, two types of permissible ranges of rotational phase differences can be realized by adjusting the mounting position of the variable angle limiting pin 80 in the radial direction.

As described above, the second hydraulic chambers 31b-31
By providing the variable angle limiting pin 80 projecting inside d, a part of the inner rotor 19, here, the vane 24b.
By abutting 24d on the variable angle limiting pin 80, the allowable range of the rotational phase difference can be limited to a range suitable for the engine.

Although the example in which the variable angle limiting pin 80 is arranged in the second hydraulic chamber 31a in the hydraulic chamber 26a has not been shown in the above-mentioned example, the position or shape that does not block the opening of the oil passage 59. With the variable angle limiting pin 80 of No. 2,
The variable angle limiting pin 80 may be arranged in the hydraulic chamber 31a so as to abut against the vane 24a. Also, the second
The variable angle limiting pin 80 may be arranged in the first hydraulic chambers 30a to 30d instead of being arranged in the hydraulic chambers 31a to 31d. As a result, the allowable range of the rotational phase difference can be limited so that the timing on the most retarded angle side becomes suitable for the engine. Also, the first hydraulic chamber 30a-
30d and the second hydraulic chambers 31a to 31d are both provided with the variable angle limiting pin 80, and the rotational position is adjusted so that the timings on the most retarded side and the most advanced side are suitable for the engine. It is possible to limit the allowable range of the phase difference.

Thus, the variable angle limiting pin 80 is simply
The first hydraulic chambers 30a to 30d and the second hydraulic chamber 31a.
Even if the design of the inner rotor 19 is not changed by mounting so as to project to one or both of
The allowable range of the rotational phase difference can be changed. Therefore, even between engine models having different allowable ranges of rotational phase difference, at least a part of the VVT 12, that is, the internal rotor 19 in the present embodiment, can be shared, which contributes to a reduction in manufacturing cost.

In this embodiment, the housing 16
Also on the side, only the position of the female screw portion 18a is different,
The allowable range of the rotational phase difference can be changed arbitrarily. Therefore, the housing 16 can be shared before the female screw portion 18a is formed. It should be noted that the housing 16 is often different for each engine model due to the influence of other mechanisms in the engine.
The change in the position of the female screw portion 18a itself has almost no effect on the manufacturing cost.

In the vane 24d, the variable angle limiting pin 8 is used instead of making the entire vane 24b thinner.
The notch 94 is formed only in the portion where the 0 protrusion portion 80a abuts. This indicates that only the portion that abuts the variable angle limiting pin 80 may be formed as a recess and the width of the vane may be narrowed. If the variable angle limiting pin 80 having a relatively large diameter is used, the allowable range of the rotational phase difference may be narrowed. That is, when the variable angle limiting pin 80 is provided, as compared with the case where the variable angle limiting pin 80 does not exist, the diameter of the variable angle limiting pin 80 can be within the allowable range of the rotational phase difference. Usually excluded from scope.

However, as shown in FIG. 12, if the variable angle limiting pin 80 contacts the notch 94 (corresponding to a recess in this case) of the vane 24d, the variable angle limiting pin 80 is attached to the vane 24d. When abutting, a part of the variable angle limiting pin 80 enters into the notch 94 and cancels a part of the diameter of the variable angle limiting pin 80. Therefore, the allowable range of the rotational phase difference can be made sufficiently wide. Moreover, in this case, since the width of the root portion 96 of the vane 24d is not reduced, the vane 24
The durability and strength of d can be kept high. The depth of the notch 94 may be such that all the variable angle limiting pins 80 enter the notch 94 and offset all the diameters of the variable angle limiting pin 80.

Therefore, since the degree of freedom of the allowable range of the rotational phase difference is increased, even between engine models,
At least a part of the rotary phase difference variable mechanism can be more commonly used, which contributes to further reduction in manufacturing cost.

[Second Embodiment] The internal rotor 19 described above.
A method of processing the oil hole 48 will be described. FIG. 13 shows an oil hole 48 bored inside the boss 23 from the base of the vane 24a on the retard side. The other three oil holes 48 are also formed by the same processing as the oil holes 48 at the base of the vane 24a, so the oil hole 48 at the base of the vane 24a will be described as a representative. In addition, FIG.
(B) shows a cross section along the axis of the oil hole 48.

First, the inner rotor 19 is preliminarily machined to a state shown in FIG. 13A as a state of a rough material. In the state of the rough material, a drill contact surface 100 orthogonal to the axial direction of the oil hole 48 is formed at the position where the oil hole 48 shown by the two-dot chain line is formed by the drill.

When the oil hole 48 is formed with a drill,
The oil hole 48 is formed by applying a drill tip at a right angle to the drill contact surface 100 to perform a drilling process. Next, the surface of the boss 23 is cut and finished to the level S1 shown by the alternate long and short dash line. By this step, FIG.
The inner rotor 19 is formed as shown in FIG.

According to the present embodiment described above, the spot facing step can be omitted as compared with the conventional case. That is, conventionally, as shown in FIG. 15 (a), since the drill contact surface was not formed in the state of the rough material, before the oil hole 48 was drilled, the oil hole 48 was previously formed by counter boring. Drill counterbored hole 200 with a larger diameter,
2 is formed, and then the tip of the drill is applied at a right angle to the drill contact surface 202 to perform a drilling process to form an oil hole 48.
Was formed. Then, next, the surface of the boss 23 is cut to a level S1 shown by the alternate long and short dash line, and then the surface shown in FIG.
It was finished like

Therefore, it is possible to omit the conventionally required counterboring, simplify the process, and reduce the manufacturing cost. Further, in the past, in FIG.
As shown in (b), even if the surface is ground, the counterbore 20
0 remains. The counterbore hole 200 has a larger diameter than the oil hole 48, and is located at a position separated from the vane 24a by a distance L1.
A corner portion 200a of 00 is formed. Therefore, conventionally, in order to prevent damage caused by cutting the vanes 24a to 24d by the corner portion 200a, it is necessary to increase the diameter of the boss 23 to secure a necessary sliding surface 23a, and as a result, , VVT12 is also enlarged.

However, in the internal rotor 19 processed as in this embodiment, the corner portion 48a of the oil hole 48 has the vane 2
It becomes the distance L2 from 4a and is smaller than the distance L1. As a result, even if the diameter of the boss 23 is reduced, the required sliding surface 2
3a can be secured, and the entire VVT 12 can be downsized.

[Other Embodiments] In the above embodiment, the gasoline engine is
Although an engine in which a reverse torque is generated in the camshafts 11 and 70 during cranking of an L-type 4 cylinder, a V-type 6 cylinder, a V-type 8 cylinder, etc. is used, other gasoline engines or diesel engines may be used.

In the above embodiment, the variable angle limiting pin 80 is screwed and fixed to the side plate 18, but it may be fixed to the side plate 18 by welding or shrink fitting. Further, the fixing position may be the cover 20 instead of the side plate 18. Also, by fixing to the ridge 25, the vane 2 from the ridge 25
You may make it protrude toward 4a, 24b, 24c, 24d.

In the above-described embodiment, the presence or absence of the notch 94 with respect to the vanes 24b, 24c, 24d with which the variable angle limiting pin 80 abuts, or the vane 24.
Due to the difference in the angular widths of b, 24c, and 24d, the difference in the allowable range of the optimum rotational phase difference for each engine model was absorbed to achieve common parts, but even if all the vanes have the same shape, By adjusting the mounting position of the variable angle limiting pin 80, it is possible to absorb the difference in the allowable range of the optimum rotational phase difference for each engine model and achieve common parts.

Further, by providing two or more kinds of angular widths of the hydraulic chambers 26b to 26d, the hydraulic chambers to which the variable angle limiting pin 80 is attached corresponding to the difference in the optimum permissible range of the rotational phase difference for each engine model. You may make it select 26b, 26c, 26d. With this configuration, even if the variable angle limiting pin 80 is attached to the inner surface of any one of the hydraulic chambers 26b, 26c, and 26d at the same relative position, the variable angle limiting pin 80 can be attached at any width. The desired allowable range of the rotational phase difference can be set by selecting the hydraulic chambers 26b, 26c, 26d such as whether they are mounted in the hydraulic chambers 26b, 26c, 26d. Furthermore,
If the mounting position of the variable angle limiting pin 80 in the hydraulic chambers 26b, 26c, 26d is also taken into consideration, the degree of freedom of the allowable range of the rotational phase difference is further increased, and the VVT is increased.
The 12 parts can be commonly used, which contributes to further reduction of the manufacturing cost.

Contact surfaces 92b, 92c, 92 of the vanes 24b, 24c, 24d with which the variable angle limiting pin 80 abuts.
d or notch 94 (this also corresponds to the contact surface)
Is such that, for example, the vanes 24b, 24c, 2 are continuously arranged so that the rotational phase changes in the radial direction of the inner rotor 19.
The contact surfaces 92b, 92c, 92d of 4d or the notch 94 may be changed. That is, these surfaces 92b, 92c, 92d, 94 may be formed obliquely at an angle with respect to the radial direction. As described above, depending on the radial position of the inner rotor 19, the contact surfaces 92b,
In the configuration in which the rotational phase of the cutouts 92c and 92d or the cutout 94 changes, the variable angle limiting pin 80 has the same hydraulic chamber 2
6b, 26c, and 26d, the position of the variable angle limiting pin 80 in the radial direction is adjusted, that is, from the center of rotation of the inner rotor 19 to the variable angle limiting pin 8.
The rotation phase of the contacting inner rotor 19 differs depending on the distance to 0. This indicates that the allowable range of the rotational phase difference can be adjusted by moving the variable angle limiting pin 80 away from or near the rotation center of the internal rotor 19. From this, the same hydraulic chamber 2
The allowable range of the rotational phase difference can be arbitrarily set only by sliding the variable angle limiting pin 80 in the radial direction in 6b, 26c, and 26d and positioning it. Therefore, the parts of the VVT 12 can be commonly used, which can contribute to further reduction of the manufacturing cost.

In the vane 24d of the above embodiment, only one step is provided when the notch 94 is viewed as a step, but two or more steps may be provided. Also by this, the contact angle 92b, 92c, 92d or the notch 94 can be angled with respect to the radial direction by moving the variable angle limiting pin 80 away from or near the rotation center of the internal rotor 19. The same effect as in the case of holding and forming diagonally can be produced.

In the above embodiment, the variable angle limiting pin 80 is screwed and fixed, but the variable angle limiting pin 80 is attached so that the position of the variable angle limiting pin 80 can be adjusted in the circumferential direction of the inner rotor 19. It may be that. With this configuration, the internal rotor 1 is simply changed for each engine model.
Since it is possible to cope with the permissible range of various rotational phase differences only by adjusting the position of the variable angle limiting pin 80 in the circumferential direction of 9,
It becomes easier to standardize the parts of the VVT 12,
It can contribute to the reduction of manufacturing cost.

[0093]

The rotary phase difference variable mechanism according to claim 1 is
By providing one rotation phase difference limiting contact member,
When the second rotating body rotates in the hydraulic chamber, the partitioning member of the second rotating body is brought into contact with the contact member for limiting the rotational phase difference, so that the allowable range of the rotational phase difference is different between the models of the internal combustion engine. Difference
As described above, the rotation phase difference limiting contact member can limit the rotation phase difference. Therefore, as for the desired range of the rotational phase difference, only one rotational phase difference limiting contact member is attached so as to project to the limit position of the allowable range in one or both of the first pressure chamber and the second pressure chamber. Can be achieved with. For this reason, it is not necessary to change the design of either or both of the first rotating body and the second rotating body, and the rotational phase difference variable mechanism can be used even between internal combustion engine models having different allowable ranges of the rotational phase difference. At least some of the parts can be shared, which contributes to a reduction in manufacturing costs. Further, if the rotation phase difference limiting contact member comes into contact with the partitioning member existing at the position where the rotation phase difference limiting contact member is most likely to contact, the rotation phase difference variable contact member The mechanism can be easily designed.

[0094]

Further , the first rotating body has a plurality of hydraulic chambers, the second rotating body has the same number of partition members as the hydraulic chambers, and the width of the partition members is 2 When the number of types is set to be more than one, even if the rotation phase difference limiting contact member is provided at a fixed position, it is simply the second
The desired allowable range of the rotational phase difference can be set only by adjusting the arrangement of the partition members having different widths of the rotating body. Therefore, by further adjusting the mounting position of the contact member for limiting the rotational phase difference, the degree of freedom of the allowable range of the rotational phase difference is further increased, and the components of the rotational phase difference varying mechanism can be easily shared. Therefore, it can contribute to further reduction of manufacturing cost.

According to the second aspect , in the plurality of hydraulic chambers of the first rotary body, the widths of the hydraulic chambers are set to two or more types.
Therefore, even if the rotation phase difference limiting contact member is attached at the same relative position with respect to the inner surface of the hydraulic chamber, by selecting the hydraulic chamber to which the rotation phase difference limiting contact member is attached,
A desired permissible range of the rotational phase difference can be set.
This also facilitates the common use of the components of the rotary phase difference varying mechanism, which contributes to further reduction in manufacturing cost.

As described in claim 3 , in the structure in which the rotation phase of the contact surface changes depending on the radial position of the second rotary body, the rotation phase difference limiting contact member is provided in the same hydraulic chamber. The allowable range of the rotational phase difference can be set arbitrarily by only sliding and positioning in the radial direction. Therefore, it becomes easy to share the components of the rotary phase difference variable mechanism,
This can contribute to further reduction in manufacturing cost.

Further , since the contact surface is changed stepwise by providing a step on the contact surface of the second rotary body with which the contact member for rotation phase difference limiting contacts, the contact member for rotation phase difference limiting contact member. By separating the rotation center of the second rotating body from or near the rotation center, the allowable range of the rotation phase difference can be adjusted, and even if the rotation phase difference limiting contact member is arranged in the same hydraulic chamber, The allowable range of the phase difference can be set arbitrarily, the parts of the rotary phase difference varying mechanism can be commonly used, and the manufacturing cost can be reduced. As described in claim 4 , the contact surface of the second rotating body with which the rotation phase difference limiting contact member abuts is provided inside the concave portion provided on the side surface of the partition member on the hydraulic pressure chamber side. Then, at the time of contact, all of the rotation phase difference limiting contact member, or at least part of the rotation phase difference limiting contact member enters the recess, and the diameter of the rotation phase difference limiting contact member is reduced. Offset all or part of it. Therefore, the setting range of the allowable range of the rotational phase difference can be made sufficiently wide, and the degree of freedom of the setting range of the allowable range of the rotational phase difference becomes high. Therefore, even between internal combustion engine models having different rotational phase difference permissible ranges, at least some of the components of the rotational phase difference variable mechanism can be easily shared, which contributes to further reduction in manufacturing cost. Further, since the width of the material of the portion other than the concave portion can be maintained, the durability of other portions can be maintained.

[0099]

As described in claim 5 , when the rotational phase difference limiting abutting member is attached so as to be positionally adjustable in the radial direction of the second rotating body, the rotational phase difference limiting abutting member is simply provided for each model of the internal combustion engine. Since it is possible to deal with various allowable ranges of the rotational phase difference only by adjusting the position of the rotational phase difference limiting contact member in the radial direction of the two-rotation body, the parts of the rotational phase difference varying mechanism can be shared more effectively. It becomes easier and can contribute to further reduction of manufacturing cost.

As described in claim 6 , when the rotational phase difference limiting contact member is attached such that the position thereof can be adjusted in the circumferential direction of the second rotating body, it is simply provided for each model of the internal combustion engine. Since it is possible to deal with various allowable ranges of the rotational phase difference only by adjusting the position of the contact member for limiting the rotational phase difference in the circumferential direction of the two-rotation body, the parts of the variable rotational phase difference mechanism can be shared more effectively. It becomes easier and can contribute to further reduction of manufacturing cost.

[0102]

[0103]

[Brief description of drawings]

FIG. 1 is a first embodiment of a rotary phase difference varying mechanism of the present invention.
Sectional view showing the configuration of a variable valve timing mechanism as the above.

FIG. 2 is a plan view showing a valve mechanism according to the first embodiment.

FIG. 3 is a sectional view taken along line 3-3 of FIG.

FIG. 4 is an operation explanatory view of the lock pin explained in a section taken along line 4-4 of FIG.

5 is an operation explanatory view of the lock pin described in a section taken along line 4-4 of FIG.

6 is a cross-sectional view showing the peripheral structure of the variable angle limiting pin taken along line 5-5 of FIG.

FIG. 7 is a plan view of the internal rotor according to the first embodiment.

FIG. 8 is a schematic plan view showing relative rotational positions of the internal rotor and the housing in the first embodiment.

FIG. 9 is a schematic plan view showing relative rotation positions of the internal rotor and the housing in the first embodiment.

FIG. 10 is a schematic plan view showing relative rotation positions of the internal rotor and the housing in the first embodiment.

FIG. 11 is a schematic plan view showing relative rotational positions of the internal rotor and the housing in the first embodiment.

FIG. 12 is a schematic plan view showing relative rotation positions of the internal rotor and the housing in the first embodiment.

FIG. 13 is an explanatory diagram of drilling according to the second embodiment.

FIG. 14 is a schematic plan view schematically showing a relative rotation position between an internal rotor and a housing in a conventional example.

FIG. 15 is an explanatory diagram of drilling processing in a conventional example.

[Explanation of symbols]

11 ... Intake side camshaft, 11a ... Journal, 12
... Variable valve timing mechanism (VVT), 13 ... Annular oil space, 14 ... Cylinder head, 15 ... Bearing cap, 16 ... Housing, 17 ... Driven gear, 17a ... Plural external teeth, 18 ... Side plate, 18a ... Female screw part , 19 ... Inner rotor, 20 ... Cover, 21 ... Bolt, 22 ... Bolt,
23 ... Boss, 23a ... Sliding surface, 24a, 24b, 24
c, 24d ... Vane, 25 ... Ridge, 26a, 26b, 2
6c, 26d ... Hydraulic chamber, 27 ... Groove, 28 ... Seal plate, 29 ... Leaf spring, 30a, 30b, 30c, 30d ...
1st hydraulic chamber, 31a, 31b, 31c, 31d ... 2nd hydraulic chamber, 32 ... through hole, 33 ... lock pin, 33a ... accommodation hole, 33b ... tip part, 34 ... locking hole, 35 ... spring, 36 ... Oil groove, 37 ... Oblong hole, 38 ... First oil passage, 39 ...
Second oil passage, 40 ... Groove, 41 ... Seal plate, 42 ... Leaf spring, 44 ... Oil groove, 45 ... Oil hole, 46 ... Oil passage, 47 ...
Annular space, 48 ... Oil hole, 48a ... Corner, 50 ... Oil groove, 5
1 ... Oil groove, 52, 53 ... Oil hole, 54 ... Oil passage, 56 ... Oil hole, 57 ... Oil passage, 58 ... Oil groove, 59 ... Oil passage, 70 ... Exhaust side camshaft, 71 ... Pulley, 72 ... Timing belt, 74 ... Drive gear, 75 ... Cam, 77 ... Intake valve, 78 ... Exhaust valve, 80 ... Variable angle limiting pin, 80
a ... protruding portion, 80b ... male screw portion, 92b, 92c, 92
d ... Abutting surface, 94 ... Notch, 96 ... Vane root, 100 ... Drill contact surface, P1, P2 ... Oil passage.

Claims (6)

(57) [Claims] 1. A first rotating body that interlocks with one of the two rotating shafts, and a second rotating body that interlocks with the other rotating shaft of the two rotating shafts. One rotating body is
At least one hydraulic chamber formed between the ridges is formed therein.
The second rotating body has at least one partition member that is inserted into the hydraulic chamber to partition the interior of the hydraulic chamber into a first pressure chamber and a second pressure chamber, The partition member is moved between the protrusions through the supply of the hydraulic pressure to one or both of the first pressure chamber and the second pressure chamber, and the partition member is relatively moved between the first rotary body and the second rotary body. A rotation phase difference variable mechanism capable of variably setting a rotation phase difference between the two rotation shafts within an allowable region by rotating the rotation shaft, wherein the first rotating body has a plurality of hydraulic chambers. , The second time
The tumbling body divides the hydraulic chambers into the same number of the hydraulic chambers.
In addition to having a drawing member, the width of the partition member is two or more.
One rotation phase difference limiting abutting member that is set above and abuts the second rotating body is attached so as to project into one or both of the first pressure chamber and the second pressure chamber, and In the partition member of the second rotating body, the contact member for limiting the rotation phase difference
By abutting a member having a non-maximum width, the allowable range of the rotational phase difference is restricted so as to be different between the models of the internal combustion engine according to the mounting position of the rotational phase difference limiting abutting member. A rotary phase difference variable mechanism characterized by being formed. Wherein said first rotary member has a plurality of said fluid pressure chamber, together with the second rotating body having a fluid pressure chamber and the same number of the partition member partitioning the liquid chamber, the liquid The rotary phase difference variable mechanism according to claim 1, wherein the width of the pressure chamber is set to two or more types. 3. Interlocking with one of the two rotary shafts
The first rotating body and the other of the two rotating shafts
A second rotating body that is interlocked with the shaft, wherein the first rotating body is
At least one hydraulic chamber formed between the ridges is formed therein.
The second rotating body is inserted into the hydraulic chamber.
Divides the inside of the hydraulic chamber into a first pressure chamber and a second pressure chamber.
Defining at least one partition member, the first pressure
Chamber and one or both of the second pressure chambers
Moving of the partition member between said ribs through the supply of hydraulic pressure
Relative rotation between the first rotating body and the second rotating body
The rotational phase difference between the two rotary shafts by
With a rotary phase difference variable mechanism that can be variably set within the allowable range
There is one rotation phase difference limiting contact with which the second rotating body makes contact.
A member is attached to one of the first pressure chamber and the second pressure chamber.
Or so that it is attached to both sides, this rotational phase difference control
Attach the partition member of the second rotating body to the limited contact member.
By removing the contact member for limiting the rotational phase difference.
The allowable range of the rotational phase difference is set to the internal combustion engine according to the mounting position.
The limits differently among models, the second rotation the abutting member rotational phase difference limit contact
The contact surface of the body is provided with a step portion,
The rotational position of the abutting surface according to the radial position of the second rotating body
A rotating phase difference variable mechanism characterized in that the phase is formed so as to change . 4. The contact surface of the second rotating body with which the rotation phase difference limiting contact member abuts is the hydraulic pressure of the partition member.
The rotation phase difference variable mechanism according to claim 1 or 2 , wherein the rotation phase difference variable mechanism is provided inside a recess provided on the side surface on the chamber side . 5. The contact member for limiting the rotational phase difference comprises:
It is mounted so that the position can be adjusted in the radial direction of the second rotating body.
Rotational phase difference variable mechanism according to claim 3, wherein the that. 6. The contact member for limiting the rotational phase difference comprises:
It is mounted so that the position of the second rotating body can be adjusted in the circumferential direction.
Rotational phase difference variable mechanism according to any one of claims 1 to 5, characterized in that that.