JP2003003808A - Valve timing controller for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a valve timing control responsibility from lowering with the rotation of the vane member by worsening the sealing characteristics due to the interval and contamination at a working initial stage in the prior art. SOLUTION: There are provided a timing gear 1, a relatively rotatable cam shaft 4, a housing 3 comprising a housing body 3a consisting of an almost cylindrical circumference wall 7, on which a partition 9 is projected at the internal circumference side and a side wall 8 integrally formed sealing the end opening of the circumference wall, and the timing gear for sealing the rear end opening of the circumference wall, and a vane member 6 forming a hydraulic chamber 17 at timing angle side and a hydraulic chamber 18 being secured with the cam shaft at the retardant angle side between the partition A seal member 20 for sealing the hydraulic chamber is inserted in a seal groove 19 formed along the longitudinal direction at an end part 16 of a vane 16. A corner part 21 of an end part 20a corresponding to a corner part 14 with a round shape of the housing body of the seal member is formed in the round shape at the manufacturing.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vane type valve timing control device for varying the opening / closing timing of an engine valve, which is an intake valve or an exhaust valve of an internal combustion engine, according to the operating condition.

[0002]

2. Description of the Related Art As a conventional valve timing control device, for example, a vane type device described in JP-A-10-141024 is known.

In this valve timing control device, a housing composed of a cylindrical housing body and a thin rear plate is fixed by bolts on the outer side of a timing gear to which a rotational force is transmitted by a crankshaft of an engine, and an outer periphery of the housing is fixed. A vane member fixed to the front end of a cam shaft to which a cam is fixed is provided inside the housing so as to be relatively rotatable.

The housing body is integrally formed in a substantially bowl shape by aluminum die casting, and has a substantially cylindrical peripheral wall with a substantially trapezoidal partition wall protruding from the inner peripheral side and a timing gear of the peripheral wall. And one side wall having a substantially different shape integrally formed while closing the one end opening on the side, and three partition walls are formed at equal intervals in the circumferential direction. In addition, the inner corner where the peripheral wall and the side wall are joined is not necessarily formed into a right angle but is formed into a rounded shape having a predetermined curvature when molding.

The vane member includes a rotor fixed to the tip of the camshaft from the axial direction by a bolt,
The rotor is composed of three vanes radially provided on the outer peripheral surface of the rotor, and an advance-side hydraulic chamber and a retard-side hydraulic chamber are defined between the three vanes and the partition walls of the housing. Has been done.

Sealing grooves are formed along the longitudinal direction at the outer peripheral ends of the vanes, and the respective hydraulic grooves are slidably in contact with the inner peripheral surface of the peripheral wall. A seal member that seals between the chambers is attached. This seal member is made of a relatively soft PPS resin as a base material, is biased in the inner peripheral surface direction of the peripheral wall by a leaf spring provided in the seal groove, and has a front end surface and one end surface on the side wall side. The flat inner peripheral surface of the peripheral wall and the flat inner end surface of the side wall are formed flat, respectively, but the corners between the tip surface and the one end surface are formed substantially at right angles.

Therefore, when assembling the vane member in the housing, the seal members are respectively inserted into the seal grooves of the vanes via the leaf springs, and at this time, the corner portions of the seal members are formed in right angles. Therefore, in the initial stage of assembling, each of the seal members has a shape in which the corners hit the rounded corners of the housing body and are pushed toward the rotor. Since the sealing member is pushed out toward the inner peripheral surface of the peripheral wall by the force, each corner portion is pressed against each corner portion to generate a concentrated load. For this reason, the corners of the seal member are worn, and the wear progresses over time, so that the seal member changes into a rounded shape that conforms to the corner shape. As a result, the seal member comes into close contact with the inner peripheral surface of the peripheral wall and the inner surface of the side wall to ensure the sealing property.

Incidentally, in each of the hydraulic chambers on the advance side and the retard side, hydraulic pressure is selectively supplied and discharged from the hydraulic circuit in accordance with the operating state of the engine to rotate the vane member forward and backward to rotate the timing gear. By changing the relative rotational phase between the camshaft and the camshaft, the opening / closing timing of the intake valve is made variable.

[0009]

However, in the above-mentioned conventional valve timing control device, each corner portion of each sealing member is formed at a right angle at the beginning of manufacture, and this corner is formed at the time of operation after assembly. Since the parts hit the corners of the housing body and adapt to the shape while wearing, during the initial stage of operation, that is, until this wear progresses sufficiently, there is a gap between the corners and the corners. A gap is likely to be formed in the. Therefore, due to the existence of such a gap, the sealing performance is deteriorated and the hydraulic pressure leaks between the hydraulic chambers. As a result, the rotational responsiveness of the vane member is reduced due to the change in the engine operating state, and the control responsiveness of the valve timing is reduced.

Also, so-called contamination is likely to occur in which abrasion powder generated by the wear of the seal member enters between the seal member and the inner peripheral surface of the peripheral wall or the inner surface of the side wall, whereby the smooth rotation of the vane member occurs. Operation may be impaired.

Further, in this conventional example, there is also disclosed a structure in which the housing and the vane member are directly slid to seal without using the sealing member, and the peripheral wall and the side wall of the housing body are integrally molded. Later, since a minute convex wall remains in the rounded corner portion where the both are joined, a tapered chamfered portion is provided at the outer edge of the one end of the vane member corresponding to this, and the convex wall is formed. It is also considered to prevent interference with.

However, when the chamfered portion is formed on the vane member as described above, both end edges of the chamfered portion are in close contact with the peripheral wall and the side wall to ensure the sealing property, but the chamfered portion has a central portion and a corner portion. A relatively large gap is formed between them. As a result, the working oil pressure easily leaks from such a gap, and it is not possible to sufficiently secure the sealing property between the two hydraulic chambers. As a result, as in the case described above, there is a possibility that the rotational responsiveness of the vane member is reduced due to the change in the engine operating state, and the control responsiveness of the valve timing is reduced.

[0013]

The present invention has been devised in view of the technical problems of the conventional valve timing control device, and the invention according to claim 1 is a rotating body rotationally driven by an engine. A cam shaft rotatable relative to the rotating body, and a peripheral wall fixed to either the rotating body or the cam shaft and having a partition wall projecting toward the inner peripheral side and one end opening of the peripheral wall. And a housing formed of a housing body composed of a side wall integrally formed with the peripheral wall and a sealing member for sealing the other end opening of the peripheral wall, and fixed to the other of the rotating body or the cam shaft, A vane member capable of rotating in the housing in the forward and reverse directions between the partition walls, and an advance side hydraulic chamber and a retard angle chamber defined between the vane member and the partition wall to selectively supply and discharge hydraulic pressure to the inside. Outside the side hydraulic chamber and the vane member A valve timing control device for an internal combustion engine, comprising: a seal member, which is held in a seal groove formed at an end portion along a longitudinal direction and seals between the hydraulic chambers, and a peripheral wall and a side wall of the housing body. A chamfered portion or a rounded portion is formed in advance at the time of manufacturing, and a chamfered portion or a rounded portion along the shape of the corner portion is formed at the outer edge of one end portion corresponding to the corner portion of the seal member. Is formed at the time of manufacturing and the outer edge of the other end of the seal member is formed substantially at a right angle.

Therefore, according to the present invention, since the peripheral wall of the housing body, the corners of the side wall, and the outer edge of the one end of the seal member are preliminarily formed into a chamfered shape or a rounded shape at the time of manufacture, each of them is assembled at the time of assembly. When the vane is pushed all the way into the housing, it fits snugly into the corner.

The outer edge of the other end of the seal member is formed substantially at a right angle, and the peripheral wall of the housing and the inner corner of the seal member are also at a substantially right angle, so that the seal member is also on the seal member side. And the housing fit together in a familiar state.

For this reason, a reliable sealing action between the hydraulic chambers can be obtained by the respective seal members from the initial operation of the apparatus, the occurrence of hydraulic pressure leakage at the initial operation as in the prior art is eliminated, and the seal members are worn. The occurrence of contamination can be prevented.

According to a second aspect of the present invention, the rotating body and the sealing member are integrally formed.

The invention according to claim 3 is characterized in that an outer edge of one end portion of the seal member is formed into a rounded shape corresponding to a rounded corner portion of the housing.

The invention according to claim 4 is characterized in that the radius curvature of the outer edge of the one end of the seal member is set to be smaller than the radius curvature of the corner of the housing body.

The invention according to claim 5 is characterized in that a mark portion, which serves as a guide in the assembling direction, is formed on one side in the longitudinal direction of the seal member.

According to a sixth aspect of the present invention, the mark portion is
It is characterized in that a portion on the seal groove side of the seal member is formed to have an asymmetrical shape in the longitudinal direction.

According to a seventh aspect of the present invention, the outer edge of the other end portion of the seal member is formed substantially at a right angle, and the seal member is mounted in the wrong mounting direction with respect to the seal groove. When assembled in the housing body, the outer end edge of the other end of the seal member abuts the corner portion so that the tip portion protrudes from the other end opening of the housing body.

According to an eighth aspect of the present invention, there is provided a rotating body which is rotationally driven by the engine, a cam shaft which is rotatable relative to the rotating body, and which is fixed to either the rotating body or the cam shaft. A housing body composed of a peripheral wall having a partition wall projecting on the inner peripheral side and a side wall that closes one end opening of the peripheral wall and a side wall integrally formed with the peripheral wall; and a sealing member that seals the other end opening of the peripheral wall. And a vane member fixed to the other of the rotating body or the camshaft and capable of rotating in the housing in the forward and reverse directions between the partition walls, and defined between the vane member and the partition wall. , Advance-side hydraulic chambers and retard-side hydraulic chambers in which hydraulic pressure is selectively supplied and exhausted, and hydraulic pressure is selectively supplied to and exhausted from the hydraulic chambers according to the engine operating state to normalize the vane member. Relative rotation between the rotating body and the camshaft In a valve timing control device for an internal combustion engine including a phase conversion mechanism that converts a dynamic phase, a chamfered portion or a rounded portion is formed in advance at the corner where the peripheral wall and the side wall of the housing body are joined together during manufacturing, and A chamfered portion or a rounded portion along the shape of the corner is formed in advance at the outer edge of the one end corresponding to the corner of the vane member at the time of manufacturing and the outer edge of the other end of the vane member is formed. It is characterized in that it is formed in a substantially right angle shape.

According to a ninth aspect of the present invention, the rotating body and the sealing member are integrally formed.

According to a tenth aspect of the present invention, the outer end edge of the one end of the vane member is formed into a rounded shape.

The eleventh aspect of the present invention is characterized in that the radius curvature of the outer edge of the one end of the vane member is set smaller than the radius curvature of the corner of the housing.

[0027]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which a valve timing control device for an internal combustion engine according to the present invention is applied to the intake side will be described in detail below with reference to the drawings.

FIG. 1 and FIG. 2 show a first embodiment of the present invention, in which a housing 3 having an operating space inside, and a timing chain provided integrally with the housing 3 by a crankshaft (not shown) of the engine are used. The timing gear 1, which is a rotating body rotatably driven through the one end portion 4a, is inserted into the housing 3 through the central hole 1a of the timing gear 1, and a plurality of intake valves (not shown) are opened on the outer circumference. The cam shaft 4 has a cam, and a vane member 6 axially fixed to the one end 4a of the cam shaft 4 by a cam bolt 5 and rotatably accommodated in the working space of the housing 3. .

The housing 3 has a substantially cylindrical peripheral wall 7 integrally formed into a bowl shape by aluminum die casting.
And a housing body 3a which closes the front end side opening of the peripheral wall 7 and a side wall 8 integrally formed with the peripheral wall 7 by molding, and a sealing member for sealing the rear end side opening of the peripheral wall 7. And the timing gear 1 as
The housing body 3a and the timing gear 1 are integrally connected by a bolt 2.

The timing gear 1 is integrally formed on the outer periphery of the sealing member in the housing 3 and has a substantially spur gear shape, and the tooth portion 1 around which the timing chain is wound.
b is formed. The timing gear 1 is
An iron-based metal having a hardness higher than that of the housing body 3a is desirable.

The peripheral wall 7 is bulged and deformed inward at a position of approximately 120 ° in the circumferential direction, and a partition 9 having a substantially trapezoidal shape on the inner peripheral side.
And three fan-shaped pedestals 10 are formed on the outer ends of the formation portions of the respective partition walls 9.
An insertion hole 11 through which the bolt 2 is inserted is formed at a central position in the circumferential direction of each pedestal portion 10. Also,
As shown in FIG. 2, a sliding hole 23, in which a lock pin 25 of a lock mechanism 22 to be described later is arranged, is provided in the boss portion 12 formed between the adjacent partition walls 9 along the radial direction. Has been.

The side wall 8 is formed in a shape that conforms to the outer shape of the peripheral wall 7 including the respective partition walls 9, and a bolt hole 13 through which the cam bolt 5 is inserted is formed in the central portion of the side wall 8. .

The inner corner 14 of the joint between the peripheral wall 7 and the side wall 8 is formed into a rounded shape having a predetermined curvature when the housing body 3a is molded as shown in FIGS.

The vane member 6 corresponds to the camshaft 4
A substantially cylindrical rotor 15 directly bolted to the one end 4a of the rotor from the axial direction by the fixing bolt 5, and three vanes 1 radially protruding from the outer peripheral surface of the rotor 15.
6 and 6.

In the rotor 15, the one end portion 4a of the camshaft 4 is fitted in the fitting groove 15a provided at the central position on one side, while the three vanes 16 are connected to the partition walls 9 of the housing 3. In between, three advancing side hydraulic chambers 17 and three retarding side hydraulic chambers 18 are defined.

Sealing grooves 19 are formed in the radial end portions 16a of the vanes 16 along the longitudinal direction, and the inner peripheral surface of the peripheral wall 7 is formed in the sealing grooves 19. Sealing members 20 for sliding contact with the hydraulic pressure chambers 7a to seal the respective hydraulic chambers 17 and 18 are mounted.

As shown in FIGS. 3 and 4, the sealing member 20 is made of a synthetic resin material (PPS, PEEK, etc.) which is softer than the housing body 3a as a base material and has a substantially U-shaped cross section and a substantially longitudinal direction. The hydraulic chambers 1 are formed in an elongated horizontal shape and are simply mounted in the seal groove 19.
The inner peripheral surface 7a of the peripheral wall 7 is driven by the hydraulic pressure supplied into the inner walls 7 and 18.
The outer surface 2
0c and one end surface 20d on the side wall 8 side are formed flat corresponding to the flat arc-shaped inner peripheral surface 7a of the peripheral wall and the flat inner end surface 8a of the side wall 8. Also, the outer surface 20
The corner portion 21 between c and the one end face 20d is formed into a substantially rounded shape corresponding to the rounded shape of the corner portion 14 of the peripheral wall 7 and the side wall 8. That is, this corner portion 21 is formed together when the seal member 20 is molded, and its curvature is set to be smaller than the curvature of the corner portion 14.

The seal member 20 has an asymmetrical shape in the longitudinal direction and the outer edge 20.
e is formed at a right angle of about 90 °, and the shape of the other end 20b including the outer edge 20e serves as a mark when the housing 3 is assembled.

As shown in FIG. 2, the lock mechanism 22 has a sliding hole 23 radially formed in the boss portion 12 of the peripheral wall 7 and the rotor 15 corresponding to the sliding hole 23.
A lock hole 24 formed in the radial direction on the outer peripheral surface of the and a slidably held inside the sliding hole 23,
a is a lock pin 25 which is provided in the lock groove 24 so as to be engageable and disengageable, a plug body 26 having a drain hole which is press-fitted and fixed to the rear end of the sliding hole 23, and an elastic member between the lock pin 25. And a coil spring 27 for biasing the lock pin 25 toward the lock groove 24. Further, the lock pin 25 is provided in a pressure receiving chamber 28 formed on the bottom side of the lock hole 24 in a first hydraulic passage 3 described later.
The hydraulic pressure supplied after the engine is started through one of the first oil holes 31a causes the sliding movement into the sliding hole 23.

Further, hydraulic pressure is selectively supplied to and discharged from each of the advance side hydraulic chamber 17 and the retard side hydraulic chamber 18 from a hydraulic circuit 30 which is a phase conversion mechanism. As shown in FIG. 1, the hydraulic circuit 30 includes a first hydraulic passage 31 for supplying / discharging hydraulic pressure to / from the advance side hydraulic chamber 17, and a retard side hydraulic chamber 18.
There are two systems of hydraulic passages, a second hydraulic passage 32 for supplying and discharging hydraulic pressure, and a supply passage (not shown) and a drain passage, which are not shown, are respectively provided in the hydraulic passages 31, 32 for electromagnetic switching. It is connected via a switching valve. An oil pump for pumping the oil in the oil pan is provided in the supply passage, and the upstream end of the supply passage and the downstream end of the drain passage communicate with the oil pan.

The first hydraulic passage 31 is bent in the axial direction and the radial direction at one side inside the cam shaft 4 from the inside of the cylinder head through the groove groove on the inner circumference of the cam bearing. Three first oil holes 3 are formed radially on the side surface of the rotor 15 and are sealed by the timing gear 1 so that each groove communicates with each advance-side hydraulic chamber 17.
1a to 31c are formed.

On the other hand, the second hydraulic passage 32 similarly passes from the inside of the cylinder head through the groove groove on the inner periphery of the cam bearing,
The cam shaft 4 is bent in the other side of the inside in the axial direction and the radial direction, and is formed radially in the rotor 15, and each of the two second parts communicates with each retard angle side hydraulic chamber 18. It has oil holes 32a to 32c.

The electromagnetic switching valve is a 4-port 2-position type valve, and the internal valve body controls switching between the hydraulic passages 31 and 32 and the supply passage and the drain passage. Switching operation is performed by a control signal from a controller (ECU) incorporating a microcomputer. The controller detects the current operating state by the engine rotation speed signal from the crank angle sensor that detects the engine speed, the load signal from the air flow meter that detects the intake air amount, and the engine water temperature signal from the water temperature sensor. The relative rotational position between the timing gear 1 and the cam shaft 4 is detected by signals from the external crank angle and cam angle sensors.

The operation of this embodiment will be described below. First, the operation of the device will be described. In the engine start-up and in a predetermined low rotation and low load range after the start-up, the electromagnetic switching valve to which the control signal is output from the controller makes the supply passage and the second hydraulic passage 32 communicate with each other. The drain passage and the first hydraulic passage 31 are communicated with each other. For this reason, the hydraulic pressure is not supplied to the advance side hydraulic chamber 17 and is maintained in a low pressure state as in the case where the engine is stopped, while the retarded side hydraulic chamber 18 is supplied with the hydraulic pressure that is secondarily fed from the oil pump. From the hydraulic passage 32 to the second oil hole 3
Although it is supplied through 2a, since the hydraulic pressure has not yet risen sufficiently, the lock pin 25 maintains the state of being locked in the lock hole 24 by the spring force of the coil spring 27, and the vane member 6 is 2, the timing gear 1 and the camshaft 4 are maintained in the positions shown in FIG.

Therefore, the cranking of the engine is quickly started up and the startability is improved by maintaining the predetermined retard control which is suitable for the startability of the valve timing of the intake valve. It is possible to suppress the occurrence of fluttering of the vane member 6 due to the positive and negative torque fluctuations that affect the Further, since such a locked state is maintained even during idling operation, utilization of inertial intake improves combustion efficiency to improve fuel efficiency and stabilize rotation.

After that, when the engine shifts to the medium-rotation / medium-load range, the electromagnetic switching valve is activated by the control signal from the controller to connect the supply passage and the first hydraulic passage 31, while the drain passage and the second hydraulic passage are connected. 32 is connected. Therefore, the oil pressure in the retard angle side hydraulic chamber 18 is equal to the second hydraulic pressure passage 32.
Through the drain passage to the inside of the oil pan and the pressure in the retard angle side hydraulic chamber 18 becomes low. On the other hand, the hydraulic pressure is supplied into the advance side hydraulic chamber 17 via the first oil hole 31a to become a high pressure, and this hydraulic pressure acts on the tip portion 25a of the lock pin 25 from the pressure receiving chamber 28 to cause the coil spring 27 to move. The tip end portion 25a is pulled out from the lock hole 24 because the tip end portion 25a is moved backward against the spring force. Therefore, the vane member 15 is allowed to relatively rotate only in the retard angle side hydraulic chamber 18 direction, that is, in the advance angle side direction, and as the hydraulic pressure in the advance angle side hydraulic chamber 18 increases, the delay of the partition wall 9 is delayed. It is rotated to the maximum and held at the most advanced side position until it comes into contact with the other side surface of the angular hydraulic chamber 17 side.

Therefore, the timing gear 1 and the camshaft 4 are controlled to rotate relative to the most advanced side to control the opening / closing timing of the intake valve to the most advanced side. As a result, the pump loss of the engine is reduced and the output can be improved.

Further, the rotary member 3 can be continuously held at a desired intermediate position by supplying / discharging the hydraulic pressure to / from the hydraulic chambers 17 and 18 in accordance with the operating condition of the engine.

Next, the operation at the time of assembling each component, particularly,
The operation of assembling the vane member 6 into the housing 3 will be described. That is, the seal groove 19 of each vane 16 is previously formed.
The seal member 20 is mounted inside the housing 3 with the seal member 20 mounted therein.
However, since it is formed in a substantially rounded shape corresponding to the rounded shape of the corners 14 of the peripheral wall 7 and the side wall 8, as shown in FIG. 3, when each vane 16 is pushed into the housing 3 to the end, The rounded corners 21 are closely attached to the corners 14 in a familiar state. Therefore, a reliable sealing action between the hydraulic chambers 17 and 18 is obtained by the seal members 20 from the initial operation of the apparatus, and the occurrence of hydraulic pressure leakage at the initial operation as in the conventional example is eliminated, and at the same time, the seal members 20 are prevented from operating. It is possible to prevent contamination due to wear.

Further, since the corner portion 21 of the tip portion 20a of the seal member 20 is not a chamfered shape obtained by post-cutting but has a rounded shape which is formed simultaneously at the time of molding, the rounding operation is facilitated.

Further, since the radius curvature of the corner portion 21 of the seal member 20 is set to be smaller than the radius curvature of the corner portion 14, the corner portion 21 should be more closely adhered to the corner portion 14 during assembly. Therefore, the sealing performance is further improved.

Since the outer edge 20d of the other end 20b of the seal member 20 is formed in a right angle as described above, the inner peripheral surface 7a of the peripheral wall 7 and one side surface of the timing gear 1 are sealed. Since they can be brought into contact with each other without a gap, a reliable sealing property can be secured at such a portion.

Further, since the outer end edge 20d of the other end portion 20b is formed in a right angle shape, when the tip end portion 20a and the other end portion 20b are assembled in reverse, the seal groove 19 is assembled. As shown in FIG. 5, the right-angled outer end edge 20d hits the rounded surface of the corner portion 14, and the tip portion 20a slightly protrudes from the housing 3 by that amount. Therefore, since it is possible to recognize in advance that the operator erroneously assembles due to such a protrusion phenomenon, especially by tactile sensation, it is possible to prevent the erroneous work from being found after the assembly is completed.

FIG. 6 shows a second embodiment, in which the shape of the corner 14 and the shape of the seal member 20 are changed to make it easier to recognize the wrong assembly, and the corner 14 is not rounded. The peripheral wall 7 and the side wall 8 are formed into a flat taper shape that connects the peripheral wall 7 and the side wall 8 in an inclined shape, and the tip portion 20a of the seal member 20 is formed.
The corner portion 21 is formed in the same tapered surface shape as the tapered surface shape of the corner portion 14. In addition, the seal member 20
The other end portion 20b has a shape in which the outer edge 20d is formed in a right angle shape as in the first embodiment, and the tip portion 20a
Side and the other end 20b side are formed asymmetrically.

Therefore, according to this embodiment, when the seal member 20 is normally assembled to the seal groove 19 when the vane member 20 is assembled in the housing 3, as shown in FIG. While the corner portion 21 of the seal member 20 is in proper contact with the corner portion 14 to ensure good sealing performance, when assembled in the opposite direction, the other end portion of the seal member 20 is provided as shown in FIG. 20b abuts the inclined taper surface of the corner portion 14 to prevent further incorporation, and the tip portion 20a on the opposite side largely protrudes from the housing 3 to the outside. Instead, it can be clearly judged by visual inspection. Therefore, misassembly can be recognized more reliably. In particular, the work can be easily and visually determined, and the work can be performed easily and easily. Therefore, the assembling workability thereafter is further improved.

FIG. 8 and FIG. 9 show a third embodiment. In this embodiment, the vane 16 is eliminated by eliminating the sealing member.
The front end portion 16a of the peripheral wall 7 is in sliding contact with the inner peripheral surface 7a of the peripheral wall 7 to seal between the hydraulic chambers 17 and 18. That is, the tip portion 16a of each vane 16 is formed flat along the inner peripheral surface 7a of the peripheral wall 7 and the inner surface 8a of the side wall 8 to which the outer surface 16b and the one side surface 16c correspond, and the outer edge 16d therebetween. Are formed in the same rounded shape as the corner portion 14. The radius of curvature of the outer edge 16d is formed to be slightly smaller than that of the corner portion 14.

Therefore, according to this embodiment, the tip end 16a of each vane 16 abuts on the peripheral wall 7 and the side wall 8 so that the sealing action between the hydraulic chambers 17 and 18 can be secured, and especially the outer edge is Since the curvature of 16d is slightly smaller than the curvature of the corner portion 14, sufficient adhesion between them is ensured and the sealing performance is improved.

Further, since the seal member is eliminated, the seal groove is not necessary, so that the efficiency of manufacturing work and assembling work can be improved by reducing the number of parts and simplifying the structure.

The present invention is not limited to the configuration of each of the above-described embodiments. For example, as a mark portion, the tip portion 20a and the other end portion 20b of the seal member 20 are colored to form a mark in the assembling direction. It is also possible to do so. In addition, the corner 1
It is also possible to form the chamfered portion by polishing or the like after molding, while the chamfering is performed after molding 4 while the corner portion 21 of the seal member 20 is also adjusted to this.

Further, in each of the embodiments, the description has been given of the timing gear in which the rotating body is driven by a chain, but it may be a timing pulley which is rotationally driven by a rubber belt, for example, and a chain is not used. It may be rotationally driven by meshing with a gear provided on another camshaft.

Further, in each of the embodiments, the timing gear, which is a rotating body, is used as the sealing member, but a member separate from the timing gear may be provided. In that case, it is possible to dispose the housing body in each embodiment in the axially opposite direction.

In each of the embodiments, the timing gear is integrally fixed to the housing and the camshaft is integrally fixed to the vane member. However, the timing gear is integrally fixed to the vane member and the camshaft is integrally formed with the housing. You may fix it to.

In each of the embodiments, the seal member is not provided at the inner peripheral end of each partition wall, but a seal groove is provided at the inner peripheral end of each partition wall and the seal member is arranged at the seal groove. It doesn't matter. At that time, it is desirable that both longitudinal edges of the seal member are formed substantially at right angles.

Furthermore, in each of the embodiments, the seal member is made of a synthetic resin material, but it may be made of a sintered material made of iron-based metal.

[0065]

As is apparent from the above description, claim 1
According to the invention described in (1), at the outer edge of one end of the seal member,
Since the chamfered portion or the rounded shape is formed along the shape of the corner portion, it is possible to effectively seal between the advance side hydraulic chamber and the retard side hydraulic chamber from the initial operation of the device. As a result, it is possible to prevent the rotational responsiveness of the vane member from being lowered due to the change in the engine operating state, and to improve the control responsiveness of the valve timing.

Further, since the outer edge of the one end of the seal member is not worn, deterioration of the sealing performance due to so-called contamination can be sufficiently prevented.

Further, since the outer edge of the other end portion of the seal member is formed in a substantially right angle shape, the other end portion, for example, a member such as a rotating body that closes the other end opening of the housing or one side surface. Since the inner peripheral surface of the peripheral wall and the outer edge of the other end can be brought into close contact with each other without a gap, the sealing property at such a portion is also improved.

According to the second aspect of the invention, since the rotating body and the sealing member are integrated, the increase in the number of parts is suppressed as compared with the case where they are separately formed, and the manufacturing work and the assembly work efficiency are improved. Can be improved.

According to the third aspect of the present invention, since the rounded portion is formed at the time of molding the seal member, the work of molding the rounded portion becomes extremely easy.

According to the fourth aspect of the present invention, since the curvature of the rounded portion of the seal member is formed to be smaller than the curvature of the rounded corner, the adhesion between the two members after assembly is increased and the sealing performance is improved. Can be further improved.

According to the fifth aspect of the invention, since the mark portion of the seal member can recognize the erroneous mounting state in the seal groove at the time of assembling to the housing, the assembling workability is improved.

According to the sixth aspect of the invention, the seal groove side of the seal member is asymmetrical, and the mark portion can be formed without changing the seal surface of the seal member. Also, since the correct mounting position can be detected by judging the shape, automatic mounting by a machine is also possible.

According to the seventh aspect of the invention, since the outer edge of the other end of the seal member is formed at a right angle to form a mark portion, the mark portion can be easily molded.

According to the invention of claim 8, claim 1
Similar to the invention described in (1), it is possible to effectively seal between the advance side hydraulic chamber and the retard side hydraulic chamber from the initial operation of the device. As a result, it is possible to prevent the rotational responsiveness of the vane member from being lowered due to the change in the engine operating state, and to improve the control responsiveness of the valve timing.

Further, since the outer edge of the one end of the seal member is not worn, it is possible to sufficiently prevent deterioration of the sealing performance due to so-called contamination.

According to the invention of claim 9, claim 2
The same effects as those of the invention described in (1) can be obtained.

According to the invention described in claim 10, the same operational effect as that of the invention described in claim 3 can be obtained.

According to the eleventh aspect of the invention, the same operational effect as that of the fourth aspect of the invention can be obtained.

[Brief description of drawings]

FIG. 1 is a sectional view taken along line AA of FIG. 2 showing a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line B-BA of FIG.

FIG. 3 is an enlarged view of a main part of this embodiment.

FIG. 4 is an enlarged view of part C in FIG.

FIG. 5 is an explanatory view showing an erroneous assembly state of the present embodiment.

FIG. 6 is an enlarged view of an essential part showing a second embodiment of the present invention.

FIG. 7 is an explanatory diagram showing an erroneous assembly state of the present embodiment.

FIG. 8 is an enlarged view of a main part showing a third embodiment of the present invention.

FIG. 9 is an enlarged view of a main part of the third embodiment.

[Explanation of symbols]

1 ... Timing gear (rotating body, sealing member) 3 ... Housing 3a ... Housing body 4 ... Camshaft 6 ... Vane member 7 ... Surrounding wall 8 ... Side wall 14 ... Corner 15 ... Rotor 16 ... Vane 17 ... Advancement side hydraulic chamber 18 ... Retardation side hydraulic chamber 19 ... Seal groove 20 ... Sealing member 20a ... Tip 20b ... the other end 21 ... Corner

Claims (11)

[Claims] 1. A rotating body that is rotationally driven by an engine, a cam shaft that can rotate relative to the rotating body, and a partition wall that is fixed to either the rotating body or the cam shaft and that projects toward the inner peripheral side. A housing composed of a housing body formed of a peripheral wall and a side wall integrally formed with the peripheral wall and closing one end opening of the peripheral wall, and a sealing member sealing the other end opening of the peripheral wall, Fixed to the other of the rotating body or the camshaft,
A vane member capable of rotating in the housing in the normal and reverse directions between the partition walls, and an advance-side hydraulic chamber and a retard angle which are defined between the vane member and the partition wall and in which hydraulic pressure is selectively supplied and discharged. A valve timing control device for an internal combustion engine, comprising: a side hydraulic chamber; and a seal member that is retained in a seal groove formed along the longitudinal direction at the outer peripheral end of the vane member to seal between the hydraulic chambers. In, while forming a chamfered portion or a rounded portion in advance at the corner where the peripheral wall and the side wall of the housing body are joined at the time of manufacturing, at one end outer edge corresponding to the corner of the seal member,
Chamfered portion or rounded portion along the shape of the corner,
A valve timing control device for an internal combustion engine, which is preformed at the time of manufacturing and the outer edge of the other end of the seal member is formed substantially at a right angle. 2. The valve timing control device for an internal combustion engine according to claim 1, wherein the rotating body and the sealing member are integrally formed. 3. The valve timing of an internal combustion engine according to claim 1, wherein an outer edge of one end of the seal member is formed into a rounded shape corresponding to a rounded corner of the housing. Control device. 4. The valve timing control of an internal combustion engine according to claim 3, wherein the radius curvature of the outer edge of the one end of the seal member is set smaller than the radius curvature of the corner of the housing body. apparatus. 5. The valve timing control device for an internal combustion engine according to claim 1, wherein a mark portion serving as a guide for an assembling direction is formed on one of the longitudinal sides of the seal member. 6. The valve timing control device for an internal combustion engine according to claim 5, wherein the mark portion is formed such that a portion on the seal groove side of the seal member has an asymmetric shape in a longitudinal direction. 7. An outer edge of the other end portion of the seal member is formed substantially at a right angle, and the seal member is assembled in the housing main body in a state where the seal member is installed in the seal groove in the wrong direction. The outer edge of the other end of the seal member abuts on the corner so that the tip of the seal member protrudes from the other end opening of the housing body.
5. A valve timing control device for an internal combustion engine according to any one of 1. 8. A rotating body which is rotationally driven by an engine, a cam shaft which is rotatable relative to the rotating body, and a partition wall which is fixed to one of the rotating body and the cam shaft and projects toward the inner peripheral side. A housing composed of a housing main body formed of a peripheral wall and a side wall integrally formed on the peripheral wall and closing the one end opening of the peripheral wall, and a sealing member for sealing the other end opening of the peripheral wall, Fixed to the other of the rotating body or the camshaft,
A vane member capable of rotating in the housing in the normal and reverse directions between the partition walls, and an advance-side hydraulic chamber and a retard angle which are defined between the vane member and the partition wall and in which hydraulic pressure is selectively supplied and discharged. Phase conversion for converting the relative rotational phase of the rotating body and the camshaft by selectively supplying and discharging hydraulic pressure to and from the side hydraulic chambers and the respective hydraulic chambers according to the engine operating state to rotate the vane member forward and backward. In a valve timing control device for an internal combustion engine including a mechanism, a chamfered portion or a rounded portion is formed in advance at the corner where the peripheral wall and the side wall of the housing body are joined at the time of manufacturing, and at the corner of the vane member. A chamfered portion or a rounded portion that conforms to the shape of the corner is formed in advance on the outer edge of the corresponding one end at the time of manufacturing, and the outer edge of the other end of the vane member is formed in a substantially right angle shape. Valve valve for internal combustion engine characterized by Imming control device. 9. The valve timing control device for an internal combustion engine according to claim 8, wherein the rotating body and the sealing member are integrally formed. 10. The outer edge of the one end of the vane member is rounded.
A valve timing control device for an internal combustion engine as set forth in. 11. The valve timing of an internal combustion engine according to claim 9, wherein the radius curvature of the outer edge of the one end of the vane member is set smaller than the radius curvature of the corner of the housing. Control device.