JP2002227618A - Valve timing control device for internal combustion engine - Google Patents

Abstract

(57) [Summary] [PROBLEMS] To ensure that even in a case where supply hydraulic pressure is low, fluttering inside a device due to a reaction force from an engine valve is prevented, and quietness and operation responsiveness are enhanced. An eccentric rotary gear is provided between a housing and a rotor. First internal teeth 4 are provided in the housing 5, and first external teeth 6 meshing with the first internal teeth 4 and having one fewer tooth than the internal teeth 4 are provided on the gear 8. A second external tooth 7 is provided on the gear 8, and a second internal tooth 9 meshing with the second external tooth 7 and having one more tooth than the external tooth 7 is attached to the rotor 10.
To be provided. The tooth surface of each tooth is formed in a shape forming a trochoid curve. By appropriately supplying and discharging hydraulic pressure to and from a plurality of working chambers 11 formed between the first internal teeth 4 and the first external teeth 6, the housing 5 and the rotor 10 are relatively rotated. Since the two external teeth 6 and 7 of the gear 8 are always eccentric to the same side, when the reaction force is input from the engine valve, the engagement between the first internal teeth 4 and the first external teeth 6 causes the housing 5 and the rotor 10 to rotate. Relative rotation is prevented.

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").
Say "engine". The present invention relates to a valve timing control device for controlling the opening / closing timing of the intake valve and the exhaust valve according to the operating conditions.

[0002]

2. Description of the Related Art By rotating an assembling angle between a driving force transmitting member such as a timing pulley or a chain sprocket that rotates in synchronization with an engine and a camshaft having a driving cam on the outer periphery, an intake valve and an exhaust valve ( Hereinafter, a valve timing control device that variably controls the opening / closing timing of the “engine valve” has been proposed.
For example, it is disclosed in Japanese Patent Application Laid-Open No. 2000-2103.

[0003] In the valve timing control device described in this publication, a vane member having two blades projecting radially outward is integrally attached to an end of a cam shut, and the vane member is integrated with a driving force transmitting member. The housing is provided with an advance hydraulic chamber facing one surface of each blade and a retard hydraulic chamber facing the other surface inside the housing, and selectively disposed in each hydraulic chamber. By absorbing and discharging the hydraulic pressure, the vane member is relatively rotated with respect to the housing, thereby changing the rotational phase of the driving force transmitting member and the camshaft to change the opening / closing timing of the engine valve. .

[0004]

In such a so-called vane type valve timing control apparatus, when a reaction force from an engine valve is input to a camshaft during a valve timing change operation, the reaction force is applied to a vane member. In the rotational direction (alternating torque acts). Therefore, if the hydraulic pressure supplied to the advance hydraulic chamber or the retard hydraulic chamber is low, the vane member flaps due to the reaction force (alternating torque) from the engine valve when the valve timing is changed, and abnormal noise is generated. This causes a problem that the operation responsiveness is reduced.

[0005] As a countermeasure for this, it is conceivable to increase the capacity of the hydraulic pump. However, if the capacity of the hydraulic pump is increased, the entire apparatus becomes large, and even if the capacity of the pump is increased, the engine starts. Under the condition that the pump rotation speed is not sufficiently increased, as in the case of the above, the above-mentioned problem cannot be solved.

Accordingly, the present invention is to provide a valve having high quietness and high operation response by reliably preventing fluttering inside the device due to the reaction force from the engine valve even when the supply hydraulic pressure is low. It is intended to provide a timing control device.

[0007]

Means for Solving the Problems As means for solving the above-mentioned problems, the invention described in claim 1 is a driving force transmitting member driven by a crankshaft of an internal combustion engine, and an engine valve on an outer periphery. A camshaft that has a driving cam for causing the driving force transmission member to rotate relative to the driving force transmission member as needed, and that is driven by the driving force transmission member to rotate in a driven manner; A housing having a first internal tooth composed of a curved line and rotating integrally with one of the driving force transmitting member and the camshaft; and an outer peripheral portion having one tooth smaller than the first internal tooth. Is formed so as to reduce the number of teeth, the first outer teeth having a generating curve meshing with the inner teeth, and the second outer teeth having the generating curve are formed on the outer periphery of a portion axially separated from the first outer tooth. Having the first An eccentric rotating gear housed in the housing so as to be eccentrically rotatable while meshing the teeth with the first internal teeth, and the driving force transmitting member and the other of the camshaft are integrally rotatably attached to the inner peripheral portion; A second internal tooth having a generation curve meshing with the second external tooth and having one more tooth than the second external tooth is provided, and eccentricity is caused by the engagement of the second external tooth and the second internal tooth. The rotor is configured to allow eccentric rotation of the rotary gear, and is formed between the first internal teeth and the first external teeth so that the volume gradually increases and decreases with the eccentric rotation of the eccentric rotary gear with respect to the housing. A plurality of working chambers and a substantially half group of working chambers arranged on one side in the circumferential direction starting from an inner contact point of the first inner tooth at an outermost diameter position on the first outer tooth of the eccentric rotary gear. A first working area consisting of A hydraulic distribution means for supplying and discharging oil pressure to a working area of a structure having a.

In the case of the present invention, when high-pressure hydraulic oil is supplied to one of the first operating region and the second operating region, the direction in which the eccentric rotary gear is inscribed in the housing and the one operating region is further expanded. Turns (orbits). At this time, the eccentric rotary gear moves the inner contact at the outermost diameter position on the first external tooth in the turning direction, and rotates (rotates) with respect to the housing in the direction opposite to the turning direction. Also, at this time, due to the turning of the eccentric rotary gear, the inner contact point of the second inner tooth at the outermost diameter position on the second outer tooth moves in the turning direction, and the rotor moves between the second outer tooth and the second outer tooth. Rotate in the same direction as the turning direction through the meshing of the internal teeth of. As a result, the housing and the rotor relatively rotate, and the rotational phases of the driving force transmitting member and the camshaft are changed.

When the rotor is integrated with the camshaft and a reaction force from the engine valve is input to the rotor through the camshaft, the reaction force is eccentrically rotated through the second internal teeth of the rotor. The input is input to the second external teeth of the gear. At this time, the first external teeth of the eccentric rotary gear are eccentric with respect to the first internal teeth of the housing on the same side as the second external teeth. The reaction force received by the first external teeth from the first internal teeth acts to prevent the eccentric rotary gear from turning. On the other hand, when the housing is integrated with the camshaft side and a reaction force from the engine valve is input to the housing side through the camshaft, the reaction force is passed through the first internal teeth of the housing and the eccentric rotary gear is driven. The input force is input to the first external teeth. At this time, the reaction force received by the second external teeth from the second internal teeth acts to prevent the eccentric rotary gear from turning. Therefore, in any case, when the reaction force is input from the engine valve, the relative rotation between the housing and the rotor is prevented.

According to a second aspect of the present invention, the housing is mounted integrally with the driving force transmitting member, and the rotor is integrally mounted on the camshaft, and the driving force transmitting member is disposed at the end of the housing near the camshaft, and is eccentric. Rotating gear second
2. The valve timing control device for an internal combustion engine according to claim 1, wherein the second external teeth of the eccentric rotary gear are arranged closer to the camshaft than the first external teeth. 3. Was also formed to have a small diameter.

In the present invention, the second internal teeth of the rotor are arranged on the outer periphery of the second external teeth, and the housing is located on the outer periphery of the second internal teeth. Is formed smaller in diameter than the first external teeth, the maximum diameter of the housing becomes smaller.

According to a third aspect of the present invention, a plurality of passage grooves having one end communicating with the bottoms of the first internal teeth are provided substantially radially on a surface of the housing where the end surface of the eccentric rotary gear slides. The first supply / discharge port and the second supply / discharge port are provided on the end face of the eccentric rotary gear at substantially equal intervals in the circumferential direction and alternately, each of which is smaller by one than the passage groove. The hydraulic pressure distribution means is constituted by providing a switching valve for selectively switching the connection between the first supply / discharge port and the second supply / discharge port between the supply passage and the discharge passage.

In the present invention, at a position corresponding to the relative rotation angle between the housing and the eccentric rotary gear, substantially half of the passage groove on one side in the circumferential direction communicates with the first supply / discharge port, and the remaining substantially half of the passage groove is provided. Communicates with the second supply / discharge port. Therefore,
Now, when high-pressure hydraulic oil is supplied to one of the first supply / discharge port and the second supply / discharge port, the hydraulic oil is introduced into substantially half the working chamber group on one side in the circumferential direction, and the pressure of the hydraulic oil is increased. As a result, the eccentric rotary gear rotates eccentrically to one side with respect to the housing. Then, as the eccentric rotation proceeds, the passage groove communicating with the first supply / discharge port moves continuously in the circumferential direction according to the rotation position of the eccentric rotation gear, and the housing and the rotor move to the predetermined relative rotation position. The eccentric rotation of the eccentric rotary gear is further advanced until it becomes.

[0014]

Next, an embodiment of the present invention will be described with reference to the drawings.

In FIG. 1, reference numeral 1 denotes a camshaft on an intake side or an exhaust side of an engine. The camshaft 1 is rotatably supported by a cylinder head (not shown) via a bearing, and has a main part thereof. A drive cam (not shown) for opening and closing an engine valve (an intake valve or an exhaust valve) is provided on the outer periphery. The valve timing control device 2 according to the present invention is provided at one end of the camshaft 1.

As shown in FIG. 1, the valve timing control device 2 includes a chain sprocket 3 as a driving force transmitting member that is rotationally driven by a crankshaft (not shown) via a timing chain (not shown). When,
This chain sprocket 3 is formed on the rear end side outer periphery (the left side in FIG. 1 is referred to as “front” and the right side is referred to as “rear”), and has first internal teeth 4 on the front end side inner periphery. A housing 5 and first outer teeth 6 that are accommodated in the housing 5 so as to be eccentrically rotatable and are meshed with the first inner teeth 4 of the housing 5 on the outer periphery of the front end, and have the second outer teeth 6 on the outer periphery of the rear end. An eccentric rotary gear 8 having external teeth 7 of the type described above, and the housing 5 is assembled to a front end portion so that the housing 5 can rotate as required,
The camshaft 1, which is driven by the power transmitted from the chain sprocket 3, is integrally coupled to the front end of the camshaft 1 in the housing 5 and meshed with the second external teeth 7 on the inner periphery of the front end. The operation of the engine is performed by a rotor 10 having two internal teeth 9 and a plurality of working chambers 11 formed between the tooth surfaces of the first internal teeth 4 of the housing 5 and the first external teeth 6 of the eccentric rotary gear 8. And a hydraulic distribution unit 12 that appropriately absorbs and discharges the hydraulic pressure according to the state.

The housing 5 includes a substantially cylindrical internal tooth ring 13 having the first internal teeth 4 formed on an inner peripheral surface thereof, and a front cover 1 disposed on a front end of the internal tooth ring 13.
4, a spacer ring 15 and a rear cover 16 which are arranged at the rear end of the internal gear ring 13 in an overlapping manner.
A plurality of bolts 1 through which these four members penetrate in the axial direction
7 together.

The first internal teeth 4 of the internal tooth ring 13 have eleven tooth surfaces as shown in FIG. 5, and the tooth surface shape is formed so as to form a trochoid curve. As shown in FIGS. 3 and 4, the front cover 14 has a through hole 19 at the center thereof into which a cam bolt 18 to be described later is inserted. A plurality of (11) passage grooves 20 are formed substantially radially so as to face each tooth bottom. In addition, the spacer ring 15
As shown in FIG. 2, a thin restricting flange 21 extending radially inward is integrally formed at the front end thereof.
Thus, the axial displacement of the eccentric rotary gear 8 is regulated.

As shown in FIGS. 6 to 8, the eccentric rotary gear 8 has a large diameter at the front end and a small diameter at the rear end, and has the first external teeth 6 on the outer periphery of the large diameter portion at the front end. Are formed, and the second external teeth 7 are formed on the outer periphery of the small diameter portion on the rear end side. The first external teeth 6 have ten tooth surfaces one less than the first internal teeth 4, and the second external teeth 7 have six tooth surfaces, and these tooth surface shapes Are formed so as to form a trochoid curve.

In the center of the eccentric rotary gear 8, a circular guide hole 22 is formed.
2, a passage hole 23 having a larger diameter than the guide hole 22 is formed so as to open toward the front end. In addition, the front end face of the eccentric rotary gear 8 that slides on the front cover 14 has a smaller number (ten) of the first supply / discharge port 24 and the second supply / discharge port, respectively, than the passage groove 20 of the front cover 14 by one. 25
Are provided at substantially equal intervals in the circumferential direction and alternately.

The first supply / discharge port 24 is constituted by a groove extending substantially radially from the opening of the passage hole 23.
The second supply / discharge port 25 is formed by an elongated groove extending substantially in the radial direction on the end face of the eccentric rotary gear 8. Each second supply / discharge port 25 has one end of a passage hole 26 axially passing through the root of the large-diameter portion of the eccentric rotary gear 8 (near the connection with the small-diameter portion). The second supply / discharge port 25 communicates with the annular groove 27 formed on the back surface of the large diameter portion through each of the passage holes 26.

As shown in FIGS. 9 to 11, the rotor 10 has a large diameter at the front end and a small diameter at the rear end, similarly to the eccentric rotary gear 8, and a large diameter portion at the front end has a substantially cylindrical shape. And the second internal teeth 9 are formed on the inner peripheral surface thereof. The second internal teeth 9 have seven tooth surfaces, one more than the second external teeth 7 of the eccentric rotary gear 8, and the tooth surface shape is the same as that of the second external teeth 7 in the trochoid curve. Is formed.

At a center position on the rear end side of the rotor 10, there is formed a passage hole 29 communicating with the internal passage 28 of the camshaft 1 (see FIG. 1).
0 through the plurality of communication holes 30 formed in the second internal teeth 9.
Is communicated with the inner space 31 of the second member. Therefore, the hydraulic oil supplied from the external pipe to the internal passage 28 of the camshaft 1 passes through the passage hole 29, the communication hole 30, and the internal space 31 as shown by arrows in FIG. Groove 2
7 (see FIGS. 7 and 8), and further from the annular groove 27 through the passage hole 26 to the second supply / discharge port 25 on the front end face of the eccentric rotary gear 8.

The rotor 10 is integrally connected to an end of the camshaft 1 by a cam bolt 18 as shown in FIG. 1. The head of the cam bolt 18 is sealed in a through hole 19 of the front cover 14. In this state, the fitting is slidably fitted, and a connection hole 32 is formed in the head portion thereof to communicate the external pipe with the passage hole 23 of the eccentric rotary gear 8. Therefore, the hydraulic oil supplied from the external pipe to the connection hole 32 of the cam bolt 18 is introduced into the first supply / discharge port 24 through the passage 23 as indicated by an arrow in FIG.

Here, the first internal teeth 4 of the housing 5 are
As shown in FIG. 12 and FIG.
The first external teeth 6 and the second external teeth 7 of the eccentric rotary gear 8 are also formed concentrically. Therefore, the inner contact point P of the first inner tooth 4 at the outermost diameter position on the first outer tooth 6 is equal to the inner contact point P of the second inner tooth 9 at the outermost diameter position on the second outer tooth 7. It is always located on the same side of the rotation center O with respect to the contact point P '. Note that, in FIG.
, The center of rotation of the eccentric rotary gear 8 is indicated by reference symbol O ′.

A plurality of working chambers 11 are formed between the first internal teeth 4 of the housing 5 and the first external teeth 6 of the eccentric rotary gear 8 as described above. Numeral 11 indicates that the volume gradually increases and decreases with the eccentric rotation of the eccentric rotary gear 8. Each of the working chambers 11 constitutes a first working area a substantially half along the circumferential direction starting from the inner contact point P at the outermost diameter position on the first external teeth 6 and forming a first working area a. One half constitutes the second operating area b. Then, the first operation area a
And the second operating region b move in the circumferential direction along with the movement of the inner contact point P on the first external teeth 6 accompanying the turning of the eccentric rotary gear 8.

The turning of the eccentric rotary gear 8 is performed in the first operation area a.
This is achieved by introducing high-pressure hydraulic oil into one of the second operating region b and the second operating region b.
(B), high-pressure hydraulic oil is introduced into its operating area a.
When (b) is to be enlarged, the inner contact point P moves to one side along the circumferential direction and the eccentric rotary gear 8 turns (revolves) to the same side as shown in FIGS. At this time, the eccentric rotary gear 8 rotates (rotates) in the direction opposite to the turning direction with respect to the housing 5. When the high-pressure hydraulic oil is supplied to the other operation area b (a), the eccentric rotary gear 8 further rotates in the opposite direction to the above according to the same principle.

Here, a plurality of spaces similar to the working chamber 11 are formed between the second external teeth 7 of the eccentric rotary gear 8 and the second internal teeth 9 of the rotor 10. It merely serves as a passage connecting the internal passage 28 of the camshaft 1 and the second supply / discharge port 25, and is not directly related to the eccentric rotation of the eccentric rotary gear 8 or the like.

The supply and discharge of hydraulic oil to and from the first operating area a and the second operating area b are performed by hydraulic distribution means 12, which, as shown in FIG. A first hydraulic passage 33 including a connection hole 32 of the eccentric rotary gear 8 and a passage hole 23 of the eccentric rotary gear 8;
Internal passage 28, passage hole 29 of rotor 10, communication passage 3
0, a second hydraulic passage 34 including an annular groove 27 of the eccentric rotary gear 8, a passage hole 26, and the like.
4, a supply passage 35 and a discharge passage 36 are provided with an electromagnetic switching valve 37.
Connected through. An oil pump 39 for pumping hydraulic oil in an oil pan 38 is provided in the supply passage 35, and an end of the discharge passage 36 is connected to the oil pan 3.
8. The electromagnetic switching valve 37 is controlled by the controller 40.
To 0, various signals indicating the operating state of the engine are input.

The hydraulic pressure distribution means 12 further includes a passage groove 20 formed on the inner end face of the front cover 14,
A first supply / discharge port 24 and a second supply / discharge port 25 are formed on the end face of the rotor 10, and a substantially half of the passage groove 20 is formed in the circumferential direction in accordance with the rotational position of the rotor 10 with respect to the front cover 14. The remaining approximately half of the passage groove 20 is connected to the second supply / discharge port 25 through the supply / discharge port 24 so that hydraulic oil is appropriately supplied / discharged to the first operation area a and the second operation area b. Has become. The supply and discharge of hydraulic oil to and from the first operating area a and the second operating area b are switched by the operation of the electromagnetic switching valve 37.

Next, the operation of the valve timing control device 2 will be described.

Now, the housing 5 and the rotor 10 are connected as shown in FIG.
13 and 15, the first hydraulic passage 33 is moved to the supply passage 35 side by the control of the electromagnetic switching valve 37 (see FIG. 1) from this state, and the second hydraulic passage 34 Are connected to the discharge passage 36, respectively, the high-pressure hydraulic oil in the supply passage 35 is introduced from the first hydraulic passage 33 to the first supply / discharge port 24 of the eccentric rotary gear 8, while the second supply / discharge port 25 communicates with the discharge passage 36 through the second hydraulic passage 34 (see FIG. 1). 15 to 19.
The middle and high pressure parts to which hydraulic oil is introduced are shown with cross hatching.

At this time, the passage groove 2 of the front cover 14
0 of the first supply / discharge port 24
, And the remaining approximately half is in communication with the second supply / discharge port 25, so that the first supply / discharge port 24 High-pressure hydraulic oil is supplied via the second operating area b, comprising the remaining half of the operating chamber group.
5 is discharged.

Then, at this time, the first operation area a is gradually expanded by the high-pressure hydraulic oil, and as shown in FIGS. 16 to 19, the first operation area a at the outermost diameter position on the first external teeth 6 is sequentially increased. The inner contact P and the inner contact P ′ at the outermost diameter position on the second outer teeth 7 move in the circumferential direction, so that the eccentric rotary gear 8 turns, and at this time, the eccentric rotary gear 8 5, the rotor 10 rotates in the direction opposite to the turning direction (rotation), and the rotor 10 rotates in the same direction as the turning direction with respect to the eccentric rotary gear 8. Therefore, the rotor 10 is rotated by the difference between the rotation angle of the rotor 10 with respect to the eccentric rotation gear 8 and the rotation angle of the eccentric rotation gear 8 with respect to the housing 5.
To rotate.

When the rotor 10 rotates by a set angle with respect to the housing 5 as shown in FIG. 19, the relative rotation between the two is restricted by rotation restricting means (not shown). The relative rotation operation of the camshaft 1 is completed. As a result, the opening / closing timing of the engine valve is changed. When returning the rotation phase of the chain sprocket 3 and the camshaft 1 to the original,
Under the control of the electromagnetic switching 37, the second hydraulic passage 34 communicates with the supply passage 35 and the first hydraulic passage 33 communicates with the discharge passage 36, and high-pressure hydraulic oil is introduced into the second operating region b. The rotor 10 is relatively rotated in the opposite direction with respect to the housing 5 by discharging the hydraulic oil in the first operation area a.

The valve timing control device 2 can change the opening / closing timing of the engine valve as described above. However, the torque between the housing 5 and the eccentric rotary gear 8 and between the eccentric rotary gear 8 and the rotor 10 can be changed. Since the transmission is performed through the tooth surface having a trochoidal curve, which is a form of a generating curve, all the tooth surfaces are in linear contact with each other, and as a result, generation of abnormal noise such as rattling noise is reliably suppressed. You.

The reaction force from the engine valve is applied to the camshaft 1
As shown in FIG. 20, the reaction force is applied to the eccentric rotary gear 8 from the second internal teeth 9 of the rotor 10 to the second external teeth 7 of the eccentric rotary gear 8 as shown in FIG. It acts as a force F1 for turning. However, at this time, the first external teeth 6 which are meshing portions with the housing 5 of the eccentric rotary gear 8 and the second external teeth 9 which are meshing portions with the rotor 10 are on the same side with respect to the rotation center O. Thus, a reaction force F2 acts on the first internal teeth 4 to the first external teeth 6 in a direction that prevents the eccentric rotary gear 8 from turning.

Therefore, even if the reaction force F1 acts on the camshaft 1 in either the front or rear direction in the rotational direction from the engine valve, the reaction force F2 acts on the second external teeth 7 from the second internal teeth 9.
As a result, the eccentric rotary gear 8 is prevented from turning, and fluttering between the housing 5 and the rotor 10 due to the reaction force from the engine valve is reliably prevented. Therefore, in the valve timing control device 2, the generation of abnormal noise can be reliably prevented, and the delay of the valve timing changing operation due to fluttering can be eliminated.

When the second external teeth 7 at the rear end of the housing of the eccentric rotary gear 8 are formed to have a diameter larger than that of the first external teeth 6 at the front end of the housing, the eccentric rotary gear 8 is also connected to the engine valve in the same manner as described above. Although it is possible to prevent flutter caused by the reaction force,
When the second external teeth 7 are formed to have a smaller diameter than the first external teeth 6 as in the valve timing control device 2 of this embodiment, the outer diameter of the housing 5 is made smaller, and the vehicle mountability is improved. Can be. That is, the second inner teeth 9 of the rotor 10 are arranged in the outer peripheral area of the second outer teeth 7, and the spacer ring 15 is arranged in the outer peripheral area of the second inner teeth 9. By setting the diameter of the teeth 7 to be smaller than that of the first external teeth 6, it is possible to avoid an increase in the diameter of the spacer ring 15.

Further, in the case where the hydraulic distribution means 12 is constituted by utilizing the sliding contact portion between the inner end face of the housing 5 (front cover 14) and the front end face of the eccentric rotary gear 8 as in this embodiment, Since there is no need to add a special component, there is an advantage that an increase in manufacturing cost due to an increase in the number of components can be suppressed.

The embodiments of the present invention are not limited to those described above. For example, in the above embodiment, the tooth surfaces of the internal teeth 4, 9 and the external teeth 6, 7 are defined by a trochoid curve. Although the shape is formed, the shape is not limited to forming a trochoid curve, and may be a shape forming another generating curve such as an involute curve or a cycloid curve.
In the above embodiment, the housing 5 is moved to the driving force transmitting member (chain sprocket 3) side, and the rotor 1
0 is integrated with the camshaft 1 side, however, conversely, the housing 5 may be integrated with the camshaft 1 side, and the rotor 10 may be integrated with the driving force transmitting member side.

[0042]

As described above, the invention according to claim 1 is
Normal valve timing control performed by introducing hydraulic oil into the operating region since the first external teeth and the second external teeth, which are the meshing portions between the housing side and the rotor side of the eccentric rotary gear, are always eccentric to the same side. Sometimes, the eccentric rotary gear can be eccentrically rotated, but when the reaction force from the engine valve is input to the eccentric rotary gear through the rotor or the housing,
Eccentric rotation of the eccentric rotary gear can be reliably prevented by engagement of the first internal teeth with the first external teeth and engagement of the second internal teeth with the second external teeth. Therefore, according to the present invention, even when the supply hydraulic pressure is low, it is possible to reliably prevent the device from fluttering due to the reaction force from the engine valve, thereby further improving quietness. At the same time, the operation responsiveness during the valve timing control can be improved.

According to the second aspect of the present invention, the maximum diameter of the housing can be reduced, so that the entire apparatus can be made compact and the vehicle mountability can be improved.

According to the third aspect of the present invention, since the hydraulic pressure switching means is constituted by utilizing the sliding surface between the end face of the eccentric rotary gear and the housing, the number of parts is not increased and the manufacturing cost is reduced. Can be.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing an embodiment of the present invention and corresponding to a section taken along line GG of FIG. 12;

FIG. 2 is an exploded perspective view showing the same embodiment.

FIG. 3 is a sectional view of a housing component showing the embodiment.

FIG. 4 is a view taken in the direction of arrow C in FIG. 3 showing the same embodiment;

FIG. 5 is a view taken in the direction of an arrow D in FIG. 3 showing the same embodiment.

FIG. 6 is a front view of the eccentric rotary gear showing the embodiment.

FIG. 7 is an exemplary cross-sectional view of the same embodiment taken along line EE of FIG. 6;

FIG. 8 is a rear view of the eccentric rotary gear showing the embodiment.

FIG. 9 is a front view of the rotor showing the same embodiment.

FIG. 10 is an exemplary sectional view of the same embodiment taken along line FF of FIG. 9;

FIG. 11 is a rear view of the rotor showing the embodiment.

FIG. 12 is a sectional view of the same embodiment, taken along line AA of FIG. 1;

FIG. 13 is a sectional view of the same embodiment, taken along line BB of FIG. 1;

FIG. 14 is a perspective view in which the flow of hydraulic oil according to the embodiment is shown.

FIG. 15 is a schematic diagram (A) showing a meshing state of each tooth at an operation reference position of the embodiment, and substantially corresponds to a cross section taken along line AA in FIG. 1 showing a switching state of an oil passage; FIG. 2 also shows a schematic diagram (B) of FIG.

FIG. 16 is a view similar to FIG. 15 when the eccentric rotary gear operates eccentrically by 30 ° from the operation reference position of the embodiment.

FIG. 17 is a view similar to FIG. 15 when the eccentric rotary gear is eccentrically operated by 60 ° from the operation reference position of the embodiment.

FIG. 18 is a view similar to FIG. 15 when the eccentric rotary gear operates eccentrically by 120 ° from the operation reference position of the embodiment.

FIG. 19 is a view similar to FIG. 15 when the eccentric rotary gear operates eccentrically by 180 ° from the operation reference position of the embodiment.

FIG. 20 is a schematic view showing a force acting between each tooth surface of the embodiment.

[Description of Signs] 1 ... Camshaft 2 ... Valve Timing Control Device 3 ... Chain Sprocket (Drive Force Transmission Member) 4 ... First Internal Teeth 5 ... Housing 6 ... First External Teeth 7 ... Second External Teeth 8 ... Eccentric rotating gear 9 ... Second internal teeth 10 ... Rotor 11 ... Working chamber 12 ... Hydraulic distribution means 20 ... Path groove 24 ... First supply / discharge port 25 ... Second supply / discharge port 37 ... Electromagnetic switching valve P ... Outermost Inner contact at radial position a: first operating area b: second operating area

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Shigeaki Yamamuro 1370 Onna, Atsugi-shi, Kanagawa Prefecture Inside Unisia Gex Co., Ltd. Terms (reference) 3G018 AB02 AB16 BA09 CA08 CA20 DA11 DA28 DA29 DA49 DA65 DA70 DA74 DA75 FA01 FA07 GA03 GA32

Claims (3)

[Claims] 1. A driving force transmitting member driven by a crankshaft of an internal combustion engine, and a driving cam on an outer periphery for operating an engine valve so that the driving force transmitting member can relatively rotate as required. A camshaft that is assembled and is driven to rotate by receiving power from the driving force transmission member; and a first internal tooth having an inner periphery formed with a generating curve, and one of the driving force transmission member and the camshaft. And a housing that rotates integrally with the first outer teeth, and has first outer teeth formed of a generation curve meshing with the first inner teeth formed on the outer peripheral portion and having one fewer teeth than the first inner teeth. A second outer tooth formed of a generating curve on an outer periphery of a portion axially separated from the first outer tooth, the second outer tooth being eccentrically rotatable while meshing the first outer tooth with the first inner tooth; Eccentric rotation housed in housing A generating gear, which is rotatably attached to the other of the driving force transmitting member and the camshaft, and has an inner peripheral portion having one more tooth than the second external tooth and meshing with the external tooth. A second internal tooth consisting of: a rotor that allows eccentric rotation of the eccentric rotary gear by meshing between the second external tooth and the second internal tooth; and the first internal tooth and the first external tooth. A plurality of working chambers formed such that the volume gradually increases and decreases with the eccentric rotation of the eccentric rotary gear with respect to the housing; and at the outermost diameter position on the first external teeth of the eccentric rotary gear. First
Starting from the internal contact point of the internal teeth of the first working area, a first working area consisting of substantially half of the working chamber groups arranged on one side in the circumferential direction, and a second working area consisting of the remaining substantially half of the working chamber groups. A valve timing control device for an internal combustion engine, comprising: hydraulic pressure distribution means for supplying and discharging hydraulic pressure. 2. The eccentric rotary gear according to claim 2, wherein the housing is attached to the driving force transmitting member and the rotor is integrally attached to the camshaft, and the driving force transmitting member is disposed at an end of the housing near the camshaft. 2. The valve timing control device for an internal combustion engine according to claim 1, wherein the teeth are disposed closer to the camshaft than the first external teeth, wherein the second external teeth of the eccentric rotary gear have a smaller diameter than the first external teeth. 3. A valve timing control device for an internal combustion engine, wherein the valve timing control device is formed as follows. 3. A plurality of passage grooves, one ends of which are in communication with the bottoms of the first internal teeth, are provided substantially radially on the surface of the housing on which the end faces of the eccentric rotary gears are in sliding contact, while the end faces of the eccentric rotary gears are provided. In addition, the number of the first
The supply / discharge port and the second supply / discharge port are arranged at substantially equal intervals in the circumferential direction,
The hydraulic pressure distribution means is provided by alternately providing a switching valve for selectively switching the connection between the first supply / discharge port and the second supply / discharge port between a supply passage and a discharge passage. The valve timing control device for an internal combustion engine according to claim 1 or 2.