JPH10110604A - Valve timing adjusting device for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve timing adjusting device which can be machined with high accuracy by a simple structure. SOLUTION: In a shoe housing 3, a circumferential wall 4 and a front plate 5 are integrally formed by aluminum die-cast, and at the same time, distortion absorbing holes 42 are formed in respective shoes 3a, 3b, 3c. Also, a sectorial space part 40 which is partitioned by the shoes 3a, 3b, 3c and in which a vane is rotatively stored, is formed in the shoe housing 3. Arched cross sectional recessed parts 50 are axially formed in the peripheral walls of the shoes 3a, 3b, 3c, and clamp seats 51 are formed on a front plate 5 side. When the clamp seats 51 are pushed and pressed by pulling claws 52, the sides of the clamp seats 51 further peripheries from the distortion absorbing holes 42 are elastically deformed, however, the sides thereof further inner circumferentials from the distortion absorbing holes 42 are hardly deformed. Therefore, the machining accuracy of the surface to be machined of the shoe housing 3 which exerts influence on sealed properties and sliding abrasion between members, can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an internal combustion engine (hereinafter referred to as "internal combustion engine").
The opening / closing timing of at least one of an intake valve and an exhaust valve of an “internal combustion engine” (hereinafter referred to as an engine)
The present invention relates to a valve timing adjusting device for changing "opening / closing timing" according to operating conditions.

[0002]

2. Description of the Related Art Conventionally, in a valve timing adjusting device for adjusting at least one of an intake valve and an exhaust valve of an engine, a driving force is transmitted from a crankshaft as a driving shaft of an engine to a camshaft as a driven shaft. Is known in which a vane is used as a driving force transmitting means for transmitting the force. The vane is accommodated in the housing so as to be relatively rotatable, and the phase difference of the vane with respect to the housing is controlled by hydraulic pressure of hydraulic oil or the like.

In order to reduce the leakage of hydraulic oil from the hydraulic chamber and facilitate assembly, it is conceivable to form the housing integrally with the peripheral wall and one of the side walls. In such a housing in which the peripheral wall and one side wall are integrally formed, the inner surface, the inner peripheral surface, and the processing accuracy of the opening end surface on the opposite side of the integrally formed side wall are as follows.
Of particular importance in terms of,

Inner surface, inner peripheral surface: Sealing property between hydraulic chambers Open end face: Leakage of hydraulic oil to outside of housing Depth from open end face to inner face: Sealing property by clearance with vane And galling and uneven wear due to sliding with the vane. Therefore, the housing has, for example, a surface roughness of 3.2 to 6.
3z, depth accuracy 20 μm, squareness 1 between inner peripheral surface and inner surface
It is necessary to perform high-precision cutting such as 0 μm and flatness of the opening end face and inner side face of 20 μm. In order to realize such high-precision processing, the inner surface of the housing which is the workpiece, the inner peripheral surface, and the processing of the opening end surface on the opposite side of the integrally formed side wall are performed by a single clamp, It is necessary to minimize the deformation due to the clamp.

[0005]

However, in a general clamping method in which the outer peripheral wall of the housing is pressed inwardly in the radial direction, it is possible to cut all the surfaces to be processed by one clamping, When a hollow member having a thin portion like a housing of the type is pressed inward in the radial direction, there is a problem that the deformation amount of the housing becomes too large.

Therefore, as shown in FIGS. 14 and 15, the clamp seat 12 is attached to the housing members 120 and 130.
2, 132 may be provided, and the housing members 120, 130 may be pressed in the axial direction by the pulling claws 125 contacting the clamp seats 122, 132. In this clamping method, the opening end faces 121a, 131a, the inner peripheral face 121a,
b, 131b and the inner surfaces 123, 133 can be cut with a single clamp. However, the clamp seats 122, 1 are provided on the outer peripheral side of the thin peripheral walls 121, 131.
When the clamp seats 122 and 132 are pressed, the amount of elastic deformation of the housings 120 and 130 due to the pressing increases as shown by the two-dot chain line in FIGS. 14 and 15. The deformation returns to the original state, and the flatness of the open end faces 121a, 131a, the inner peripheral faces 121a, 131a and the inner side faces 123, 133 are increased.
And the squareness is worse.

[0007] Further, as in the method of machining a revolving scroll disclosed in JP-A-6-712, it is conceivable to reduce the amount of deformation at the time of clamping by forming a circumferential groove and a radial groove on the outer peripheral wall of the head plate. However, in the case of the vane type housing, since a part of the outer peripheral wall does not protrude outward in the radial direction unlike the end plate, the rigidity of the housing is reduced when the circumferential groove is formed. Although it is conceivable to provide an annular flange for increasing the wall thickness or forming a circumferential groove, there is a problem that the apparatus becomes large. Further, there is a problem that the processing of the circumferential groove and the radiation groove is complicated.

The present invention has been made in order to solve such a problem, and an object of the present invention is to provide a valve timing adjusting apparatus which has a simple structure and can be machined with high accuracy.

[0009]

According to the valve timing adjusting device for an engine according to the first aspect of the present invention, the housing member is mounted on the outer peripheral side of the partition formed by partitioning the housing chamber when the housing member is cut. By providing the seat portion against which the pressing member that presses in the direction abuts, deformation of the outer peripheral side of the seat portion and the partition portion due to the pressing of the pressing member is reduced on the inner peripheral side of the radially thick partition portion. Therefore, the processing accuracy of the processed surface of the housing member which affects the sealing performance and the sliding wear between the members is improved.

[0010] Further, since the number of joints between members is reduced,
The sealing performance is improved and the assembly is facilitated. According to the valve timing adjusting device for an engine according to the second aspect of the present invention, since the thickness of the seat is thin, the amount of deformation in the seat is small. Therefore, the amount of deformation of the entire housing member is reduced.

According to the valve timing adjusting device for an engine according to the third aspect of the present invention, the deformation absorbing hole is provided between the inner peripheral surface of the housing member to be cut and the seat, so that the outer periphery of the deformation absorbing hole is provided. The amount of deformation of the partition on the inner peripheral side of the deformation absorbing hole becomes smaller than the amount of deformation of the partition on the side. Therefore, the processing accuracy of the processed surface of the housing member which affects the sealing performance and the sliding wear between the members is improved.

According to the valve timing adjusting device for an engine according to the fourth aspect of the present invention, the peripheral wall and one side wall of the housing member are integrally formed by aluminum die casting, so that the housing member can be easily cut and processed. The weight of the housing member can be reduced. In the engine valve timing adjusting device according to claim 5 of the present invention,
Since a seat portion facing the axial direction of the housing member is formed on the outer side of the housing member and located radially outward of the partition portion, the seat portion can be clamped from the axial direction of the housing. It is possible to reduce the strain applied to the housing during the processing inside.

A mounting hole for mounting a bolt is formed in the partition, and it is desirable that the seat be located radially outside the mounting hole. According to such a configuration, the distortion given to the housing by the mounting hole can be reduced. In addition, by forming the seat portion at one axial end of the housing member and facing the other axial end in the opposite direction, it occurs when the housing member is clamped in the axial direction. The fall of the peripheral wall of the housing member can be reduced.

When the housing member is provided integrally with the side wall together with the peripheral wall, the seat portion is formed on the end side where the integrated side wall is formed for processing the inner surface inside the housing. Further, the seat portion may be formed at one end in the axial direction of the housing member, and may be formed so as to face one end in the axial direction.

[0015]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing a first embodiment of the present invention; (First Embodiment) FIGS. 1 to 6 show an engine valve timing adjusting apparatus according to a first embodiment of the present invention.

The timing gear 1 shown in FIG. 1 receives a driving force transmitted from a crankshaft (not shown) as a drive shaft of an engine by a gear train (not shown), and rotates in synchronization with the crankshaft. Camshaft 2 as driven shaft
Is driven by a timing gear 1 to open and close at least one of an intake valve and an exhaust valve (not shown). The camshaft 2 is rotatable with a predetermined phase difference with respect to the timing gear 1. The timing gear 1 and the camshaft 2 rotate clockwise as viewed from the arrow X direction shown in FIG. Hereinafter, this rotation direction is referred to as an advance direction.

The timing gear 1 and the shoe housing 3 constitute a housing member as a driving-side rotating body, and are coaxially fixed by bolts 20. In a shoe housing 3 as a housing member, a peripheral wall 4 and a front plate 5 as one side wall are integrally formed. FIG.
As shown in the figure, the shoe housing 3 has shoes 3a, 3a as partition portions formed in trapezoidal shapes at substantially equal intervals in the circumferential direction.
b, 3c. Fan-shaped space portions 40 as accommodation chambers for accommodating vanes 9a, 9b, 9c as vane members are formed in three circumferential gaps of the shoes 3a, 3b, 3c, respectively. Has an arc-shaped cross section.

Each shoe 3a, 3b, 3c as a partition
A concave portion 50 having an arcuate cross section is formed in the outer peripheral wall in the axial direction, and a clamp seat 51 as a seat portion shown in FIG. 1 is formed on the front plate side. As shown in FIG. 2, the vane rotor 9 as a vane member has vanes 9a, 9b, 9c at substantially equal intervals in the circumferential direction.
b, 9c are rotatably accommodated in a fan-shaped space formed in a circumferential gap between the shoes 3a, 3b, 3c. As shown in FIG. 1, the vane rotor 9 and the bush 6 are integrally fixed to the camshaft 2 by bolts 21 and form a driven-side rotating body. The bush 6 fixed integrally with the vane rotor 9 is fitted to the inner peripheral wall of the front plate 5 so as to be relatively rotatable. As shown in FIG. 2, the outer peripheral wall of the vane rotor 9 and the shoe housing 3
A minute clearance is provided between the inner peripheral wall and the inner peripheral wall, and the vane rotor 9 can rotate relative to the shoe housing 3. A spring 1 is provided on each of the outer peripheral walls of the vanes 9a, 9b, 9c and the outer peripheral wall of the boss 9d of the vane rotor 9.
The seal member 16 urged in 7 is fitted to prevent leakage of hydraulic oil between the hydraulic chambers.

A retard hydraulic chamber 10 is formed between the shoe 3a and the vane 9a, a retard hydraulic chamber 11 is formed between the shoe 3b and the vane 9b, and a retard hydraulic chamber 11 is formed between the shoe 3c and the vane 9c. A hydraulic chamber 12 is formed. Also, shoe 3
a and a vane 9b, an advanced hydraulic chamber 13 is formed between the shoe 3b and the vane 9c, and an advanced hydraulic chamber 14 is formed between the shoe 3c and the vane 9a. Is formed.

With the above configuration, the camshaft 2 and the vane rotor 9 can rotate relative to the timing gear 1 and the shoe housing 3 coaxially. As shown in FIG. 1, the guide ring 19 is press-fitted and held on the inner wall of the vane 9 a forming the accommodation hole 23, and the guide ring 19 is
, A stopper piston 7 is inserted. Therefore, the stopper piston 7 is accommodated in the vane 9 a so as to be slidable in the axial direction of the camshaft 2, and is urged toward the front plate 5 by the spring 8. Stopper piston 7
Can be fitted into a stopper hole 22 formed in the front plate 5 by the urging force of the spring 8. The communication passage 24 formed in the timing gear 1 communicates with the housing hole 23 on the right side of the flange 7a and is open to the atmosphere, so that the movement of the stopper piston 7 is not hindered.

The hydraulic chamber 37 on the left side of the flange 7a communicates with the retard hydraulic chamber 10 via an oil passage (not shown).
When hydraulic oil is supplied to the retard hydraulic chamber 10, the spring 8
The stopper piston 7 has a stopper hole 22 against the urging force of
Get out of The hydraulic chamber 38 formed at the tip of the stopper piston 7 communicates with the advance hydraulic chamber 15 via an oil passage 39 shown in FIG. When hydraulic oil is supplied to the advance hydraulic chamber 15, the stopper piston 7 comes out of the stopper hole 22 against the urging force of the spring 8.

Position of stopper piston 7 and stopper hole 2
The position 2 indicates that the camshaft 2 is at the most retarded position with respect to the crankshaft,
When the vane rotor 9 is at the most retarded position, the stopper piston 7 is set in the stopper hole 22. The stopper piston 7 and the stopper hole 22 constitute a lock mechanism.

As shown in FIGS. 1 and 2, the boss 9d of the vane rotor 9 is provided with an oil passage 29 at a contact portion with the bush 6, and an oil passage 33 at a contact portion with the camshaft 2. Is provided. Oil passages 29 and 33
Are each formed in an arc shape. The oil passage 29 communicates with a hydraulic pressure source or a drain (not shown) as driving means via oil passages 25 and 27. Further, the oil passage 29 is connected to the retard hydraulic chambers 10, 11, 12 by the oil passages 30, 31, 32.
And is in communication with the hydraulic chamber 37 via an oil passage (not shown).

The oil passage 33 communicates with a hydraulic source or a drain (not shown) as driving means via an oil passage 26 and an oil passage 28. Further, the oil passage 33 includes oil passages 34, 35, 36.
, And is in communication with the hydraulic advance chambers 13, 14 and 15, and communicates with the hydraulic chamber 38 via the hydraulic advance chamber 15 and the oil passage 39. Next, cutting of the valve timing adjusting device will be described.

The shoe housing 3 is formed by aluminum die casting into a shape shown in FIG. The strain absorbing hole 42 as a deformation absorbing hole is formed by aluminum die casting together with the shoe housing 3. Is formed between the inner peripheral surface and the clamping seat 51 of the shoe 4 and the diameter L ₃ of the distortion absorbing holes 42 shown in FIG. 3 (B), respectively the depth L ₆ distortion absorbing holes 42 L ₃ : 5 mm, L ₆ : 22 mm.

Next, the shoe housing 3 is placed on the pedestal 60, and the fixed seat 61 is fitted into the bush hole 5a. A claw portion 52a provided at one end of a pulling claw 52 as a pressing member is engaged with the clamp seat 51 of the shoe housing 3. A protrusion 52b is provided at the other end of the pulling claw 52, and the clamp seat 51 is pressed against the base 60 by the claw 52a by tightening the bolt 53 with the protrusion 52b as a fulcrum.

After the shoe housing 3 is fixed to the pedestal 60, a dotted line portion of the shoe housing 3 shown in FIG. 3B, that is, the opening end surface 4a of the peripheral wall 4, the inner peripheral surface 4 of the peripheral wall 4
b, the inner surface 5b of the front plate 5 is
By cutting. The dimensions of each part after cutting by the end mill 65 shown in FIG. 3B, FIG. 4 and FIG.
The depth L ₁ of the shoe housing 3 is 22 mm, the radial thickness L ₂ of each shoe is 20 mm, the length L ₄ of the clamp seat 51 is 3 mm,
The thickness L5 of the clamp seat 51 is ₅ mm.

When the clamp seat 51 is pressed by the pulling claw 52, as shown in FIG. 6, the outer peripheral side 43 of the shoe from the strain absorbing hole 42 is elastically deformed as shown by a two-dot chain line.
The inner peripheral side 44 of each shoe is hardly deformed relative to the strain absorbing hole 42. Pulling claw 52 after cutting by end mill 65
When removed, the flatness of the open end face 4a of the outer peripheral side 43 and the accuracy of the perpendicularity to the inner side face 5b of the outer peripheral side 43 are reduced, but the open end face 4a of the shoe housing 3 excluding the outer side 43 of each shoe and each shoe are removed. Since the machining accuracy of the inner peripheral surface 4b of the shoe housing 3 including the inner peripheral surface of the shoe housing 3 and the inner side surface 5b of the shoe housing 3 is high without being substantially affected by the deformation of the outer surface 43 of each shoe, the shoe housing 3 and the timing gear 1, The sealing property between the shoe housing 3 and the vane rotor 9 is improved, and caulking and uneven wear in a sliding portion between the shoe housing 3 and another member are reduced.

After cutting by the end mill 65, the strain absorbing hole 42 is tapped to form a female screw portion which is screwed to the male screw portion of the bolt 20. Next, the operation of the valve timing device will be described. During normal engine operation, the retard hydraulic chambers 10, 11, 12 and the advance hydraulic chambers 13, 1
Since the stopper piston 7 has come out of the stopper hole 22 by the hydraulic pressure of the hydraulic oil supplied to 4 and 15, the vane rotor 9 can rotate relative to the shoe housing 3. The phase difference of the camshaft 2 with respect to the crankshaft is adjusted by controlling the hydraulic pressure applied to each hydraulic chamber.

When the engine stops, the retard hydraulic chamber 10,
Since the operating oil is no longer supplied to the hydraulic chambers 11, 12, and the advance hydraulic chambers 13, 14, 15, the vane rotor 9 stops at the most retarded position shown in FIG. Hydraulic chamber 3
Since the operating oil is not supplied to 7 and 38, the stopper piston 7 is fitted into the stopper hole 22 by the urging force of the spring 8.

Even if the engine is restarted, the retard hydraulic chamber 1
0, 11, 12 and the advance piston hydraulic chambers 13, 14, 15 until the hydraulic oil is supplied to the stopper piston 7 in the stopper hole 2
2, the camshaft 2 is held at the most retarded position with respect to the crankshaft. As a result, the vane rotor 9 is locked to the front plate 5 until the hydraulic oil is supplied to each hydraulic chamber, so that the shoe housing 3 and the vane rotor 9 are prevented from colliding with each other due to the fluctuation torque of the cam.

When hydraulic oil is supplied to each of the retard hydraulic chambers or the advance hydraulic chambers and hydraulic oil is supplied to the hydraulic chambers 37 or 38, the stopper piston 7 receives a force to the right in FIG. The stopper piston 7 comes out of the stopper hole 22 against the urging force of the stopper 8. As a result, the coupling between the front plate 5 and the vane rotor 9 by the lock mechanism is released, so that the operating pressure applied to the retard hydraulic chambers 10, 11, 12 and the advance hydraulic chambers 13, 14, 15 causes the shoe housing 3 to be actuated. As a result, the vane rotor 9 relatively rotates, and the relative phase difference of the camshaft 2 with respect to the crankshaft is adjusted.

In the first embodiment described above, the recess 50 is provided on the outer peripheral side of each shoe without increasing the thickness of the shoe housing 3 or increasing the diameter of the shoe housing 3 in order to provide the clamp seat. Thus, the shoe housing 3 can be prevented from being enlarged. Further, in the first embodiment, the configuration in which the rotational driving force of the crankshaft is transmitted to the camshaft 2 by the timing gear 1 is employed. However, a configuration using a timing pulley, a chain sprocket, or the like may be employed.

Further, in the first embodiment, the deformation amount of the shoe housing 3 when the clamp seat 51 is pressed by the pulling claw 52 is reduced by providing the strain absorbing hole 42, but as in the first modification shown in FIG. By providing the clamp seat 51 on the outer peripheral side of each shoe as a partition without providing a strain absorbing hole, the amount of deformation of the shoe housing 3 can be reduced.

Further, as shown in a modified example 2 shown in FIG.
The clamp seat 51 may be pressed against the pedestal 60 by urging the pulling claw 93 as a pressing member with zero. By moving the handle 92 in the direction of the arrow around the support shaft 91, the clamp seat 5 is moved.
1 is pressed against the pedestal 60 by the cam 90. FIG.
The clamp seat 51 may be pressed by using the electromagnetic drive device 100 as in a third modification shown in FIG. The movable rod 101 of the electromagnetic driving device 100 is attached to the pulling claw 110 as a pressing member.
The movable rod 101 is attracted downward in FIG. 9 by energizing the coil 102 of the electromagnetic drive device 100, and the movable rod 10
The first head 101a pulls the pulling claw 110. Thereby, the clamp seat 51 is pressed against the pedestal 60.

In addition to the modified examples 2 and 3, the shoe housing 3 may be pressed by the pulling claw 52 by air pressure or hydraulic pressure. Second Embodiment FIGS. 10 and 1 show a second embodiment of the present invention.
It is shown in FIG. The shoe housing 70 is formed by aluminum die casting.

The recess 71 provided on the outer peripheral side of each shoe is formed so as not to open on the opening side of the shoe housing 70. Then, even when the clamp seat 72 as a seat portion formed on the outer peripheral side of each shoe by the concave portion 71 is pressed by the pulling claw 52, the shoe on the inner peripheral side than the strain absorbing hole 42 is hardly deformed. Shoe housing 7 as in the example
0 can be processed with high precision.

(Third Embodiment) FIG. 1 shows a third embodiment of the present invention.
2 and FIG. The shoe housing 75 is formed by aluminum die casting. A clamp seat 76 as a seat provided on the outer periphery of each shoe protrudes from the outer peripheral wall of the shoe housing 75. Even when the clamp seat 76 is pressed by the pulling claw 52, the shoe on the inner peripheral side with respect to the strain absorbing hole 42 is hardly deformed, so that the shoe housing 75 can be processed with high precision as in the first embodiment.

In the embodiments of the present invention described above,
A clamp seat is provided on the outer periphery of each thick shoe, and each thick shoe is provided with a strain absorption hole.Each shoe outside the strain absorption hole is mainly deformed by the clamp, and the strain absorption hole is formed. The deformation of each shoe inside was smaller. This makes it possible to form the shoe housing without reducing the rigidity even with aluminum which is easily elastically deformed, so that the cutting of the shoe housing is facilitated and the weight can be reduced.

The formation of the deformation absorbing hole in each thick shoe reduces the thickness of each shoe and eliminates an extremely thick portion in the shoe housing. As a result, shrinkage holes (shrinkage holes) are less likely to occur during molding by aluminum die casting, and the quality of the shoe housing is improved. Further, according to a plurality of embodiments of the present invention, by utilizing a clamp seat of a drawing claw after cutting, a through-hole or a screw hole is formed in the clamp seat to allow other components or other devices to be mounted on the shoe housing, for example, a crank angle. A sensor rotor and a plate for preventing leakage from the journal can be attached. Further, in the first and second embodiments, the nut for fastening the gear can be accommodated in the concave portion provided on the outer periphery of each shoe, so that the space of the engine can be saved.

In the embodiments of the present invention, the strain absorbing hole 42 is a stop hole. However, it may be formed as a through hole. (Fourth Embodiment) FIGS. 16 and 17 show a fourth embodiment of the present invention. In the fourth embodiment, the housing 300 includes a peripheral wall 310, a shoe 312, and a side wall 314. The peripheral wall 310 is formed so as to be concave inward in the radial direction at a portion of the shoe 312, and the concave wall surface 31 is formed.
6. The housing 300 has a concave wall surface 31.
A flange portion 510 as a seat portion is formed in the concave portion formed in 6 to protrude like an eave. This flange portion 51
0 is located corresponding to the opening end on one end side of the housing 300. The flange portion 510 has a mounting hole 420 into which a bolt for fixing another side wall (not shown) is mounted. The mounting hole 420 has a function as an absorption hole. In addition, in the housing 300,
A seating surface 512 that is slightly recessed from one end surface 318 of the housing 300 is formed facing one end of the housing 300. When cutting the housing 300, the seating surface 51
The pulling claw 52 is brought into contact with the housing 2 and the housing 300 is pressed down and fixed in the axial direction. According to this embodiment,
Since the seat 510 is formed radially outside the shoe 312, it is possible to prevent the distortion at the time of fixing from reaching the inner surface of the housing 300. Moreover, since the flange portion 510 as a seat portion is formed in a plate shape, distortion is hardly transmitted. Furthermore, since the seating surface 512 is located radially outside of the mounting hole 420, transmission of distortion is also suppressed by the mounting hole 420.

The shape of the seat 510 is not limited to the shape along the circular outer edge of the housing 300 as shown in FIG. 16, but may be the shape extending outward in the radial direction only at the shoe portion. .

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a valve timing adjusting device according to a first embodiment of the present invention.

FIG. 2 is a transverse sectional view showing the valve timing adjusting device of the first embodiment.

FIG. 3A is a schematic plan view showing a state in which the shoe housing of the valve timing adjusting device according to the first embodiment of the present invention is clamped, and FIG. 3B is a cross-sectional view taken along the line BB of FIG. It is.

FIG. 4 is a schematic view showing a shape of a shoe of the first embodiment.

FIG. 5 is a schematic sectional view showing a state where the clamp seat of the first embodiment is clamped.

FIG. 6 is a schematic explanatory view showing a deformation when the clamp seat of the first embodiment is clamped.

FIG. 7 is a schematic sectional view showing Modification Example 1 of the first embodiment.

FIG. 8 is a schematic sectional view showing Modification Example 2 of the first embodiment.

FIG. 9 is a schematic sectional view showing a third modification of the first embodiment.

FIG. 10 is a schematic diagram showing a shape of a shoe according to a second embodiment.

FIG. 11 is a schematic cross-sectional view showing a state where the clamp seat of the second embodiment is clamped.

FIG. 12 is a schematic view illustrating a shape of a shoe according to a third embodiment.

FIG. 13 is a schematic sectional view showing a state where a clamp seat of the third embodiment is clamped.

FIG. 14 is a schematic sectional view showing the structure of a conventional clamp seat.

FIG. 15 is a schematic sectional view showing the structure of a conventional clamp seat.

FIG. 16 is a plan view showing the shape of the shoe of the fourth embodiment.

FIG. 17 is a schematic cross-sectional view showing a state where the clamp seat of the fourth embodiment is clamped.

[Explanation of symbols]

 Reference Signs List 1 timing gear (housing member) 2 camshaft (driven shaft) 3 shoe housing (housing member) 3a, 3b, 3c shoe (partition portion) 4 peripheral wall 5 front plate (one side wall) 7 stopper piston 9 vane rotor (vane member) 9a, 9b, 9c Vane (vane member) 42 Strain absorbing hole (deformation absorbing hole) 50 Recess 51 Clamp seat (seat) 52 Pulling claw (pressing member) 70 Shoe housing (housing member) 72 Clamp seat (seat) 75 Shoe housing (housing member) 76 Clamp seat (seat) 93, 110 (pressing member)

Claims (9)

[Claims] A driving force transmission system for transmitting a driving force from a driving shaft of an internal combustion engine to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve of the internal combustion engine.
A housing member that rotates together with either the drive shaft or the driven shaft and integrally forms a peripheral wall 000000 wall, and is partitioned within the housing member by a partition part that is a part of the housing member. A housing member having a formed accommodation chamber, a vane member that rotates with the other of the drive shaft or the driven shaft and is relatively rotatably accommodated in the accommodation chamber only within a predetermined angle range with respect to the housing member, A hydraulic pressure-driven driving unit that relatively rotates the housing member and the vane member by liquid pressure, and a pressing member that presses and fixes the housing member in the axial direction during cutting of the housing member is in contact with the driving member. A valve timing adjusting device for an internal combustion engine, wherein a seat portion is provided on an outer peripheral side of the partition portion. 2. The valve timing adjusting device for an internal combustion engine according to claim 1, wherein an axial thickness of the seat is substantially equal to or smaller than an axial thickness of the one side wall. 3. The valve timing adjusting device for an internal combustion engine according to claim 1, wherein a deformation absorbing hole is provided between the inner peripheral surface of the partition portion to be machined and the seat portion. 4. The valve timing adjusting device for an internal combustion engine according to claim 1, wherein the peripheral wall and the one side wall are integrally formed by aluminum die casting. 5. A valve timing adjusting device for an internal combustion engine provided in a driving force transmission system for transmitting a driving force from a driving shaft of the internal combustion engine to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve of the internal combustion engine. A housing member that integrally forms a peripheral wall and a partition portion that protrudes inward from the peripheral wall to form a housing chamber that extends in the circumferential direction with the partition portion as an end; and a housing member that is housed in the housing chamber. A vane member that is rotatable relative to the housing member. The vane member is located outside of the housing member in a radially outer side of the partition portion, and is disposed in an axial direction of the housing member. A valve timing adjusting device for an internal combustion engine, wherein a seat portion is formed. 6. The internal combustion engine according to claim 5, wherein a mounting hole for mounting a bolt is formed in the partition, and the seat is located radially outside the mounting hole. Engine valve timing adjustment device. 7. The valve for an internal combustion engine according to claim 5, wherein the seat is formed at one end in the axial direction of the housing member, and faces the other end in the axial direction. Timing adjustment device. 8. The housing member integrally has a side wall at one axial end of the housing chamber together with the peripheral wall,
The valve timing adjusting device for an internal combustion engine according to claim 7, wherein the seat portion is formed on an end portion side where the integral side wall is formed. 9. The valve timing for an internal combustion engine according to claim 5, wherein the seat is formed at one end in the axial direction of the housing member and faces one end in the axial direction. Adjustment device.