JPH09250310A - Valve timing changing device for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve timing changing device for an internal combustion engine in which the number of parts can be reduced, and the work efficiency in the assembling work can be enhanced. SOLUTION: A phase changing mechanism 11 is provided with a housing 28 and a vane 29 provided to the inside thereof. The housing 28 is fixed to a driven gear 22 that has been provided to the outer circumference of a camshaft 12 so as to be integrally rotatable. A through hole 42 is formed inside the vane 29. A locking pin 43 is arranged inside the through hole 42, and also a spring 48 for energizing the pin 43 toward the driven gear 22 is arranged. On the side surface of the driven gear 22, a locking hole 49 for inserting time locking pin 43 is formed. A ring-shaped groove 51 is formed on the side surface of the vane 29, and the groove 51 is communicated with the inside of the through hole 42 by means of a communicating groove 52. In the cover 38 for covering the vane 29 and the side surface of the housing 28, an air vent hole 38a for communicating with the ring-shaped groove 51 and the outside is formed.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve timing changing device for changing the opening / closing timing of intake / exhaust valves provided in a cylinder of an internal combustion engine during operation of the engine.

[0002]

2. Description of the Related Art As a technique relating to a valve timing changing device for changing the opening / closing timing of intake / exhaust valves provided in a cylinder of an internal combustion engine, Japanese Patent Laid-Open No. 1-9250
Japanese Patent No. 4 discloses a "valve opening / closing timing control device". This valve opening / closing timing control device, as shown in FIG.
Internal rotor 1 provided at the tip of camshaft 101
02 and a timing pulley 103 rotatably fitted on the rotor 102. Internal rotor 1
A plurality of vanes 105 extending in the radial direction are fixed to the outer peripheral portion of 02. A plurality of oil grooves 106 are formed on the inner peripheral portion of the timing pulley 103.
5 are arranged in the groove 106, respectively.

Further, two insertion holes 111 and 112 extending in the radial direction are formed inside the timing pulley 103, and the lock pin 11 is provided in the insertion holes 111 and 112.
3, 114 are provided in a state of being urged by springs 115, 116 toward the axial center of the camshaft 101. Further, locking holes 117 and 118 into which the lock pins 113 and 114 are fitted are formed on the outer peripheral portion of the inner rotor 102. Then, by inserting the lock pins 113 and 114 into the locking holes 117 and 118,
The relative rotation of the internal rotor 102 and the timing pulley 103 is restricted so that the valve opening / closing timing is maintained in either the advanced state or the delayed state.

In the above-mentioned valve opening / closing timing control device of the prior art, the lock pins 113 and 114 for restricting the relative rotation between the internal rotor 102 and the timing pulley 103 move in the radial direction of the camshaft 101 and the locking hole 117. , 1
By being fitted in 18, the relative rotation between the internal rotor 102 and the timing pulley 103 is regulated. The lock pins 113, 114 and the locking holes 117,
It is conceivable to change the configuration of 118 to a configuration in which the lock pin 201 is locked in the locking hole 203 by moving in the axial direction of the cam shaft 202, as shown in FIG. 14, for example.

More specifically, the camshaft 20 will be described.
A timing pulley 204 is rotatably fitted around the outer circumference of the camshaft 2, and the pulley 204 is attached to the camshaft 202.
It is fixed to the housing 205 which is fixed to the tip of the. The vane 206 is fixed to the tip of the camshaft 202 so as to rotate integrally with the camshaft 202.
And the side surface on the front end side of the housing 205 (left side surface in FIG. 14)
The cover 207 is integrally rotatably fixed to the tip end portion of the cam shaft 202 by a bolt 208 so as to cover the.

Further, as shown in FIG. 15, a through hole 210 extending in the axial direction of the camshaft 202 is formed in a part of the vane 206, and the lock pin 201 is coaxially arranged in the through hole 210. Is slidably disposed on the.
A locking hole 203 into which the lock pin 201 can be fitted is formed in the timing pulley 204, and the pin 201 is provided between the lock pin 201 and the cover 207 in the direction of the locking hole 203. A biasing spring 211 is provided.

Oil for supplying the lock pin 201 against the urging force of the spring 211 is supplied into the locking hole 203 and the space 212 formed between the through hole 210 and the lock pin 201. It is supposed to be done.

In the valve timing changing device constructed as described above, depending on the hydraulic pressure of the oil supplied to the locking hole 203 or the space 212 and the urging force and size of the spring 211, the lock pin is changed. 201 is a locking hole 20
It is possible to switch between a state in which it is fitted in the inside of the 3 and locked, and a state in which the locking is released. Therefore, similarly to the valve opening / closing timing control device, the relative rotation between the vane 206 and the timing pulley 204 can be restricted to maintain the valve opening / closing timing at a predetermined timing.

Here, the gap formed between the outer peripheral side surface of the lock pin 201 and the inner peripheral side surface of the through hole 210 is within a range that does not hinder the movement of the lock pin 201 from the viewpoint of preventing oil leakage. It is desirable to be as small as possible.

However, when the gap is set small, when the lock pin 201 moves in the through hole 210, the pin 201, the through hole 210, and the cover 207.
The lock pin 2 is driven by the pressure of air in a space 213 surrounded by and (hereinafter, this space is referred to as a “back pressure chamber”).
The movement of 01 may be hindered.

Therefore, in the above valve timing changing device, as shown in FIGS. 14 to 16, the cover 207 is provided with the air hole 2 that communicates the outside with the inside of the through hole 210.
14 are formed. Then, when the lock pin 201 moves, air is supplied from the hole 214 into the back pressure chamber 213, or air in the back pressure chamber 213 is discharged to the outside through the air hole 214. Has become. As a result, the pressure of the air in the back pressure chamber 213 is maintained at a substantially constant value, and as described above, the pressure of the air in the back pressure chamber 213 hinders the movement of the lock pin 201. It can be prevented.

[0012]

However, in the above valve timing changing device, the position of the air hole 214 formed in the cover 207 is, of course, the position of the through hole 2.
It must correspond to the position of the hole 210 so as to communicate with 10. However, the cover 207 is attached to the bolt 20.
When the cam shaft 202 is fixed to the tip end portion of the cam shaft 202 by means of 8, the positional deviation may occur between the air hole 214 and the through hole 210 as shown by the broken line in FIG. Therefore,
When assembling the cover 207, the cover 20
7 and the vane 206 need to be positioned, which reduces the work efficiency.

Further, the cover 20 is made of a member such as a knock pin.
Although it is conceivable to prevent the positional deviation as described above by adopting the configuration in which the relative rotation between the No. 7 and the vane 206 is adopted, such a configuration undesirably causes an increase in the number of parts.

The present invention has been made in view of the above circumstances, and an object thereof is to reduce the number of parts and to improve the work efficiency during the assembling work. An object is to provide a valve timing changing device for an engine.

[0015]

In order to achieve the above object, the invention according to claim 1 is rotatable about the same axis of rotation, one of which is arranged on the inner side of the other. A rotating body and a second rotating body; a cover that is fixed to the first rotating body so as to rotate integrally therewith and covers side portions of the both rotating bodies; and a concave portion and a convex portion formed on inner and outer peripheral portions of the both rotating bodies, And a pressure chamber defined by the cover, and a fluid supply means for supplying a fluid of a predetermined pressure to the pressure chamber, for opening and closing a crankshaft of an internal combustion engine and a valve of the engine. One of the cam shafts is drivingly connected to the first rotating body, and the other of the two shafts is drivingly connected to the second rotating body, and by the pressure of the fluid supplied to the pressure chamber by the fluid supply means. Relative rotation of the two rotating bodies Accordingly, it is possible to change the opening / closing timing of the valve by changing the rotation phase of the camshaft with respect to the crankshaft, and the insertion hole extending in the direction of the rotation axis is formed in the first rotating body. At the same time, a locking portion is formed in the second rotating body, and the movable member arranged in the insertion hole is moved in the rotation axis direction to lock the same member by the locking portion to rotate the both members. In a valve timing changing device for an internal combustion engine in which a rotational phase of a camshaft with respect to a crankshaft is maintained at a predetermined phase by restricting relative rotation of a body, a contact surface between the first rotating body and a cover is provided. An air space that extends in the circumferential direction of the rotation axis and communicates with the insertion hole is formed in the space, and air that opens in the communication space in the cover and communicates the space with the outside of the cover. That the formation of the one in which the gist thereof.

The invention according to claim 2 is, in the valve timing changing device for an internal combustion engine according to claim 1, characterized in that the communication space is formed in an annular shape around the position of the rotation axis. It is a thing.

(Operation) The operation of the invention described in claims 1 and 2 will be described below. In the invention described in claims 1 and 2, the fluid is supplied from the fluid supply means to the pressure chamber, and the pressure of the fluid causes the two rotating bodies to rotate relative to each other. The rotation phase of the camshaft with respect to the crankshaft is changed by this relative rotation, and the opening / closing timing of the valve is changed.

Further, the movable member arranged in the insertion hole of the first rotating body moves in the direction of the rotation axis of both rotating bodies, so that the same member engages with the locking portion formed on the second rotating body. Be locked. As a result, the relative rotation of the two rotating bodies is restricted, the rotational phase of the camshaft with respect to the crankshaft is maintained at a predetermined phase, and the valve opening / closing timing is maintained at a predetermined timing.

A communication space extending in the circumferential direction of the rotation axis is formed between the contact surface of the first rotating body and the cover, and the space forms an air hole formed in the insertion hole and the cover. Are communicated. Therefore, when the movable member moves in the insertion hole, air is introduced into the insertion hole from the outside or the air in the insertion hole is discharged to the outside through the communication space and the air hole. As described above, since the movement of the air between the insertion hole and the outside is allowed, the movement of the movable member is not hindered by the pressure of the air in the insertion hole.

Further, in the invention described in claims 1 and 2, since the communication space has a shape extending in the circumferential direction of the rotation axis, the work of aligning the air hole with the insertion hole is performed. When this is done, a positional deviation corresponding to the length of the communication space in the circumferential direction is allowed. Therefore, the work of aligning the air hole with the insertion hole is facilitated.

Further, a positioning member such as a knock pin for positioning the cover and the first rotating body is unnecessary.
According to the invention of claim 2, in addition to the above-mentioned action,
Since the communication space is formed in an annular shape centered on the position of the rotation axis, it is not necessary to align the air hole and the insertion hole when fixing the cover.

[0022]

BEST MODE FOR CARRYING OUT THE INVENTION

(First Embodiment) A first embodiment in which the present invention is embodied as a valve timing changing device provided in a multi-cylinder gasoline engine as an internal combustion engine will be described below.

FIG. 1 shows an intake side camshaft 1 provided with a phase changing mechanism (hereinafter referred to as "VVT mechanism") 11.
2, each hydraulic chamber 13, 1 provided in the VVT mechanism 11
4 (not shown in the figure), an oil pump 15 for supplying oil as a fluid to the hydraulic chambers 13 and 14 through hydraulic passages P1 and P2 described later, and the hydraulic passages P1 and P1.
An oil control valve (hereinafter referred to as "OCV") 16 provided in the middle of P2, an electronic control unit (hereinafter referred to as "ECU") 17 for controlling the OCV 16 according to an operating state of the engine, and the like are shown. FIG. In addition, in the present embodiment, the intake side camshaft 12 corresponds to the camshaft in the first aspect of the invention.

Journal 12 of intake side camshaft 12
The a is rotatably supported by the upper end surface of the cylinder head 18 and the bearing cap 19. As shown in FIG. 3, four pairs of cams 20 are formed on the outer peripheral portion of the intake side camshaft 12 on the base end side (right side in FIG. 1). An upper end of an intake valve (not shown) provided for each cylinder is in contact with each cam 20.
The intake valve is opened and closed by the rotation of.

In the intake side camshaft 12, a diameter-expanded portion 21 is formed at a portion on the tip side of the portion supported by the cylinder head 18 and the bearing cap 19. An annular driven gear 22 is rotatably fitted on the outer periphery of the enlarged diameter portion 21. A plurality of outer teeth 22a are formed on the outer peripheral portion of the driven gear 22, and the outer teeth 22a are, as shown in FIG. 3, the outer teeth 24a of the drive gear 24 provided on the exhaust side camshaft 23.
Are engaged. As with the intake side camshaft 12, four pairs of cams 25 are formed on the exhaust side camshaft 23. An exhaust valve (not shown) is opened and closed by these cams 25.

A cam pulley 26 is fixed to the end of the exhaust side cam shaft 23, and a timing belt 27 is hung on the pulley 26. Timing belt 2
7 is mounted on a crank pulley (not shown) attached to a crankshaft (not shown) of the engine.

When the operation of the engine is started, the rotational driving force of the crankshaft is transmitted to the exhaust side camshaft 23 via the cam pulley 26, and the rotational driving force is applied to the drive gear 24 and the driven gear 22.
Is transmitted to the intake side camshaft 12 via.

FIG. 4 is a sectional view taken along the line IV-IV of FIG. 1 (note that FIG. 1 corresponds to the sectional view taken along the line I-I of FIG. 4). As shown in FIG. 1 and FIG. 4, the VVT mechanism 11 provides a housing 28, a vane 29 as a first rotating body arranged in the housing 28, and a rotational force in the axial direction of the intake side camshaft 12. It is provided with an advance side hydraulic chamber 13 and a retard side hydraulic chamber 14 for imparting and rotating the vane 29.

The housing 28 has a substantially disk shape as a whole, the side surface of which is abutted against the tip side surface of the driven gear 22 (left side surface in FIG. 1), and a plurality of bolts 30 form the gear 22. It is fixed to. Therefore, the housing 28 and the driven gear 22 are connected to the intake camshaft 1
It is possible to rotate integrally with 2 as the rotation axis. In the present embodiment, the housing 28 and the driven gear 2
Reference numeral 2 corresponds to the second rotating body.

As shown in FIG. 4, the vanes 29 are arranged inside the housing 28. This vane 29
The vane 29 includes an annular fixing portion 31 located at the center of the vane 29, and four pressure receiving portions 32 as convex portions formed on the outer peripheral portion of the fixing portion 31. Each pressure receiving portion 32 is
The intake-side camshaft 12 radially extends in the radial direction, and as shown in FIG. 4, the entire camshaft 12 has a substantially cross shape.

Inside the housing 28, at positions separated by a predetermined distance in the circumferential direction of the intake side camshaft 12,
Four protrusions 3 protruding toward the axis of the shaft 12
3 are formed. The inner peripheral surface of each of these protruding portions 33 is in sliding contact with the outer peripheral surface of the fixed portion 31. Each protrusion 33
A groove portion 34 as a concave portion is provided between the pressure receiving portions 32, and the pressure receiving portions 32 are arranged in the groove portions 34.

The outer peripheral surface of each pressure receiving portion 32 is in sliding contact with the inner peripheral surface of the housing 28. An outer peripheral groove 35 having a rectangular cross section is formed on the outer peripheral portion of each pressure receiving portion 32, as shown in FIGS. 4 and 8. A seal member 36 is disposed in the outer peripheral groove 35 as shown in FIG. 6, and the seal member 36 is biased toward the outer peripheral side by a leaf spring 37. As a result, the seal member 36 seals between the outer peripheral surface of the pressure receiving portion 32 and the inner peripheral surface of the housing 28.
The movement of oil between the advance side hydraulic chamber 13 and the retard side hydraulic chamber 14 is restricted.

A cover 38 having a cylindrical shape with a bottom so as to cover the side surfaces of the housing 28 and the vanes 29 on the tip side.
Is provided. A mounting hole 39 is formed in the center of the cover 38, and a center hole 40 is formed in the center of the fixing portion 31. A mounting bolt 84 is inserted into the mounting hole 39 and the center hole 40, and the bolt 84
One end of is screwed into the bolt hole 41 of the camshaft 12. By this screwing, the cover 38 and the vane 29 are attached.
Is fixed to the tip of the intake side camshaft 12.
The vane 29 and the intake-side camshaft 12 are engaged with each other by a knock pin (not shown), and both 29 and 12 rotate integrally. The cover 38 is fixed to the vane 29 by the tightening force of the mounting bolt 84. Therefore, the vane 29 and the cover 38 rotate integrally with the intake-side camshaft 12 as the rotation axis.

Inside the housing 28, four spaces are formed which are surrounded by the side surfaces of the cover 38 and the expanded diameter portion 21 and the inner peripheral wall of each groove portion 34. Furthermore, each space is further divided into two pressure chambers by each pressure receiving portion 32 arranged in the groove portion 34. The pressure chamber formed on the same side as the rotation direction (shown in FIG. 4) of the intake side camshaft 12 is a retard side hydraulic chamber 14 and is formed on the side opposite to the rotation direction. The pressure chamber thus set is the advance side hydraulic chamber 13.

Oil is supplied to the inside of each of the hydraulic chambers 13 and 14 through hydraulic passages P1 and P2, and the vane 29 has a hydraulic pressure of the oil supplied to each of the hydraulic chambers 13 and 14. Depending on its size, it can rotate in both directions around the intake-side camshaft 12.

When the vane 29 rotates in the same direction as the rotation direction of the intake camshaft 12 (hereinafter, this rotation direction is referred to as "advancing rotation direction"), the intake cam fixed to the vane 29 is rotated. The rotation phase of the shaft 12 is advanced with respect to the driven gear 22, and the opening / closing timing of the intake valve is advanced.

On the other hand, when the vane 29 rotates in the direction opposite to the rotation direction of the intake side camshaft 12 (hereinafter, this rotation direction is referred to as the "retarded rotation direction"), the rotation phase of the intake side camshaft 12 is increased. Is delayed with respect to the driven gear 22, and the opening / closing timing of the intake valve is delayed.

As shown in FIG. 6, a through hole 42 having a circular cross section extending in the axial direction of the intake camshaft 12 is formed in one of the pressure receiving portions 32, and the lock pin 43 is provided in the hole 42. Is provided. More specifically, the through-hole 42 has a step portion 42a in the middle thereof, and has a shape in which a portion on the tip side (left side in FIG. 6) of the step portion 42a is expanded in diameter. In this embodiment, the through hole 42 corresponds to the insertion hole in the present invention, and the lock pin 43 corresponds to the movable member.

The lock pin 43 has a cylindrical shape with a bottom, and a diameter-expanded portion 43a is formed at the tip end side portion thereof. The lock pin 43 moves in the axial direction of the intake-side camshaft 12 with its outer peripheral surface slidingly contacting the inner peripheral surface of the through hole 42.

The annular space surrounded by the inner peripheral side surface of the enlarged diameter portion of the through hole 42 and the outer peripheral side surface of the lock pin 43 causes hydraulic pressure for releasing the locked state of the lock pin 43. A chamber 44 is formed. The hydraulic chamber 44 communicates with an advance side annular passage 46, which will be described later, via a first pressure oil passage 45 formed inside the vane 29. Oil can be supplied.

A storage space 47 extending in the axial direction is formed inside the lock pin 43, and a spring 48 serving as a biasing means is arranged in the space 47. The lock pin 43 is biased toward the base end side of the intake side camshaft 12 by the spring 48. The back pressure chamber 42b is formed by the inner wall surface of the accommodation space 47, the inner side surface of the through hole 42, and the space covered by the cover 38.
Are formed.

On the tip side surface of the driven gear 22,
At the position facing the base end face of the lock pin 43, the pin 4
Locking hole 49 as a locking portion into which the base end portion of 3 can be fitted.
Are formed. When the lock pin 43 biased by the spring 48 is fitted into the locking hole 49, the relative rotation between the vane 29 and the driven gear 22 is restricted. As a result, the vane 29 rotates integrally with the driven gear 22 and the housing 28. In the present embodiment, the lock pin 43, the through hole 42, the spring 48, and the locking hole 49 constitute a rotation restricting means.

The locking hole 49 is, as shown in FIGS. 8 and 9,
A second pressure oil passage 50 formed on the side of the pressure receiving portion 32 communicates with one of the retard side hydraulic chambers 14, and a portion of the oil inside the retard side hydraulic chamber 14 is in the hole 49. Is available.

When the lock pin 43 is locked in the locking hole 49, both the vane 29 and the housing 28 are held in the positional relationship shown in FIG. That is, vane 2
9 is arranged inside the housing 28 at a position where the rotation phase of the intake side camshaft 12 is most delayed with respect to the housing 28 (hereinafter, the position of the vane 29 is referred to as “the most retarded angle position”).

As shown in FIGS. 4 to 7, an annular groove 51 is formed on the side surface of the fixing portion 31 on the tip side so as to surround the mounting bolt 84. The annular groove 51 has an annular shape centered on the axial center of the intake camshaft 12. Also, on the tip side surface of the vane 29,
A communication groove 52 extending in the radial direction of the intake camshaft 12 is formed. The inner peripheral side of the communication groove 52 communicates with the inside of the annular groove 51. When the lock pin 43 moves to the base end side (right side in FIG. 6) by the urging force of the spring 48, the communication groove 52 allows the annular groove 51 and the back pressure chamber 42b to communicate with each other. There is. Incidentally, in FIG. 6, the space surrounded by the inner peripheral wall of the annular groove 51 and the cover 38 in the present embodiment corresponds to the communication space of the present invention.

Further, as shown in FIGS. 1 and 10, an air hole 38a is formed in the cover 38 at a position covering the annular groove 51, and the annular groove 5 is formed by the air hole 38a.
The inside of 1 communicates with the outside of the cover 38. Therefore, the communication of the air between the inside of the through hole 42 and the outside is allowed through the communication groove 52, the annular groove 51, and the air hole 38a.

Next, the advance side, the retard side hydraulic passages P1 and P2 forming pressure passages for supplying oil to the advance side hydraulic chamber 13 and the retard side hydraulic chamber 14, and the OCV 16
The configuration of the above will be described.

As shown in FIG. 1, the advance side head oil passage 53 and the retard side head oil passage 5 are provided inside the cylinder head 18.
4 are formed. Each of the head oil passages 53 and 54 is
An oil pan 57 can be connected via the CV 16, the oil filter 55, the oil pump 15, and the oil strainer 56. When the oil pump 15 is driven with the operation of the engine, the oil stored in the oil pan 57 is sucked by the pump 15. Then, the oil is introduced into the oil pump 15 via the oil strainer 56, and is pressurized and discharged from the pump 15. Then, the discharged oil collects the oil filter 55.
Via the OCV 16 through the head oil passages 53, 5
4 is selectively pumped.

Oil grooves 58 and 59 are formed in the upper end portion of the cylinder head 18 and the bearing cap 19 corresponding to the opening positions of the head oil passages 53 and 54, respectively. The journal 12a is formed by the oil grooves 58 and 59.
The outer peripheral part of is surrounded.

Inside the intake side camshaft 12, a retard side shaft oil passage 60 extending in the axial direction thereof is formed. The tip end side of the retard side shaft oil passage 60 communicates with the bolt hole 41. A peripheral groove 61 extending in the circumferential direction is formed on the outer peripheral portion of the enlarged diameter portion 21.
And the tip end side of the retard angle side shaft oil passage 60 are connected by a communication oil passage 62.

A retard angle oil hole 63 extending in the radial direction of the intake camshaft 12 is formed inside the journal 12a. The retard side shaft oil passage 60 has the retard side oil hole 6
3 communicates with the one oil groove 59. Therefore,
The oil in the retard side head oil passage 54 is supplied into the retard side shaft oil passage 60 via the oil groove 59 and the retard side oil hole 63.

An advancing side shaft oil passage 64 is formed inside the intake side camshaft 12 and extends in a direction inclined with respect to the axial direction thereof. Further, an advance angle oil hole 65 extending in the radial direction of the intake camshaft 12 is formed inside the journal 12a. The advance side shaft oil passage 6
The base end side of No. 4 communicates with the other oil groove 58 through the advance side oil hole 65. Then, the advance side shaft oil passage 6
The oil in the advance-side head oil passage 53 is supplied to the inside of No. 4 through the oil groove 58 and the advance-side oil hole 65.

Inside the driven gear 22, as shown in FIGS. 4 and 5, four retard side supply passages 66 extending radially are provided.
Are formed. The inner peripheral side of each retard angle side supply oil passage 66 communicates with the circumferential groove 61, and the outer peripheral side of each oil passage 66 opens to each retard angle side hydraulic chamber 14 described above. The oil supplied from the retard side shaft oil passage 60 into the circumferential groove 61 through the communication oil passage 62 is supplied into each retard side hydraulic chamber 14 via the retard side supply passage 66. .

Further, as shown in FIG. 1, a cylindrical projecting portion 67 projecting toward the distal end side is formed on the side surface on the distal end side of the expanded diameter portion 21. A stepped portion 68 is formed on the side surface of the vane 29 on the base end side so as to surround the protruding portion 67. The space formed by the inner peripheral wall of the step portion 68 and the projecting portion 67 and the enlarged diameter portion 21 forms a ring-shaped advance-side annular passage 46. The tip side of the advance side shaft oil passage 64 is open to the advance side annular passage 46.

Further, as shown in FIGS. 4 and 5, four vane-side supply oil holes 69 extending radially are formed inside the vane 29, and the inner peripheral side of the oil holes 69 is the above-mentioned. It communicates with the advance-side annular passage 46. Also, each advance side supply oil hole 6
The outer peripheral side of 9 is open to each advance side hydraulic chamber 13 described above. Therefore, the oil supplied into the advance-side shaft oil passage 64 is supplied to the advance-side hydraulic chambers 1 through the advance-side supply oil holes 69.
It is designed to be supplied within 3.

The advance-side head oil passage 53 and the oil groove 5 described above.
8, the advance-side oil hole 65, the advance-side shaft oil passage 64, the advance-side annular passage 46, and the advance-side supply oil hole 69 constitute the advance-side hydraulic passage P1 and the retard-side head oil. Path 54,
Oil groove 59, retard side oil hole 63, retard side shaft oil passage 60,
The communication oil passage 62, the circumferential groove 61, and the retard side supply passage 66 constitute a retard side hydraulic passage P2. In the present embodiment, the hydraulic pressure passages P1 and P2 are set by the OCV 16.
To supply oil from the oil pump 15 into the hydraulic chambers 13 and 14 by switching the communication state between the oil pump 15 and the oil pan 57, or to the hydraulic chambers 13 and 1 respectively.
The oil is discharged from the inside of No. 4 and returned to the oil pan 57. Incidentally, each of the hydraulic passages P1 and P2, the oil pump 1
5, the OCV 16 and the oil pan 57 constitute a fluid supply means.

The OCV 16 is duty-controlled for its opening degree so that the advance side and retard side hydraulic chambers 13,
The hydraulic pressure supplied to 14 is controlled. Hereinafter, the configuration of the OCV 16 will be described.

As shown in FIG. 1, the casing 70 constituting the OCV 16 has first to fifth ports 71 to 75. The first port 71 is in communication with the retard angle side head oil passage 54, and the second port 72 is in communication with the advance angle side head oil passage 53. Also, the third and fourth ports 73, 7
4 is connected to the oil pan 57, and the fifth port 75 is connected to the discharge side of the oil pump 15 via the oil filter 55.

Inside the casing 70, a skewered spool 76 is provided. The spool 76 has four cylindrical valve bodies 77, and can reciprocate in the axial direction. Further, in the casing 70, an electromagnetic solenoid 78 for moving the spool 76 between the first operating position shown in FIG. 1 and the second operating position shown in FIG.
Is provided. A spring 79 is provided inside the casing 70, and the spring 79 urges the spool 76 toward the first operating position.

The OCV 16 is the ECU 1 shown in FIG.
7 is controlled. This ECU 1
Reference numeral 7 denotes a rotation speed sensor 80 and an intake pressure sensor 81 for detecting the operating state of the engine, and a crank angle sensor 8 for detecting the rotation phase of the intake side camshaft 12.
2 and the cam angle sensor 83 are connected, and the ECU 17
Detects the operating state of the engine and the rotation phase of the intake camshaft 12 based on the detection signals of the sensors 80 to 83. Then, the ECU 17 determines the deviation between the actual rotation phase of the intake side camshaft 12 and the target rotation phase that matches the operating state of the engine, and the OCV 16 and the VVT mechanism 11 are controlled so that the deviation becomes a predetermined value or less. To control.

Next, the operation of this embodiment configured as described above will be described. When the operation of the engine is started, the oil pump 15 is driven to
The oil is discharged from. The discharged oil is the OCV16
Is supplied from one of the head oil passages 53, 54 selected by the above into the hydraulic chambers 13, 14 of either the advance side hydraulic chamber 13 or the retard side hydraulic chamber 14. At this time, oil is supplied to the inside of the hydraulic chamber 44 or the locking hole 49 through the first pressure oil passage 45 or the second pressure oil passage 50.

When the oil pressure inside the oil pressure chamber 44 or the locking hole 49 increases above a predetermined value, the lock pin 43 moves toward the tip side of the intake camshaft 12 against the biasing force of the spring 48 by the oil pressure. Moving. By this movement, the locked state of the vane 29 is released as shown in FIG. 6, and the vane 29 can be rotated relative to the housing 28.

As described above, when the locked state of the lock pin 43 is released, the lock pin 43 moves in the through hole 42 toward the tip side (left side in FIG. 7), and the volume of the back pressure chamber 42b is reduced. Decrease. As a result, the air in the back pressure chamber 42b is discharged to the outside through the communication groove 52, the annular groove 51 and the air hole 38a.

When the lock pin 43 moves to the base end side, the volume of the back pressure chamber 42b increases. as a result,
In the back pressure chamber 42b, an air hole 38a, an annular groove 51,
Also, external air is introduced through the communication groove 52.

Then, as shown in FIG.
9, the discharge side of the oil pump 15 communicates with the advance-side head oil passage 53, and the retard-side head oil passage 54 communicates with the oil. The pan 57 is communicated. Therefore, each advance side hydraulic chamber 13
Is supplied via the advance hydraulic passage P1, while the oil in each retard hydraulic chamber 14 is returned to the oil pan 57 via the retard hydraulic passage P2.

As a result, the pressure receiving portion 32 is urged by the hydraulic pressure in each advance side hydraulic chamber 13 which is relatively increased compared to the hydraulic pressure in each retard side hydraulic chamber 14, so that the vane 29 is moved to the housing 28. On the other hand, it rotates in the direction shown by the arrow in FIG. By rotating the vane 29 with respect to the housing 28 in this way, the rotation phase of the intake camshaft 12 advances from the driven gear 22, and as a result, the opening / closing timing of the intake valve is advanced.

On the other hand, as shown in FIG.
When the spool 76 is arranged at the first operating position by the urging force of the above, the discharge side of the oil pump 15 communicates with the retard head oil passage 54, and the advance head oil passage 53 and the oil pan 57 are connected. Communicated. Accordingly, oil is supplied to each of the retard hydraulic chambers 14 through the retard hydraulic passage P2, while oil in each of the advance hydraulic chambers 13 is returned to the oil pan 57 through the advance hydraulic passage P1. It is.

As a result, the pressure receiving portion 32 has a relatively increased hydraulic pressure in each advance side hydraulic chamber 13 and a corresponding one in each retard side hydraulic chamber 1.
The vane 29 rotates in the direction shown by the arrow in FIG. By rotating the vane 29 with respect to the housing 28 in this way, the rotation phase of the intake camshaft 12 is delayed relative to that of the driven gear 22, so that the opening / closing timing of the intake valve is delayed.

As described above, the intake side camshaft 1
When the rotation phase of the OCV 16 is changed and the deviation between the rotation phase and the target rotation phase adapted to the operating state of the engine becomes equal to or smaller than a predetermined value, the ECU 17 sets the first port 71 and the second port 72 of the OCV 16 to both ports. The spool 7 is moved so that 71 and 72 are closed by the valve body 77.
The position of the spool 6 is controlled (hereinafter, the position of the spool 76 is referred to as an “intermediate holding position”). Thus, the spool 76
When the position of the hydraulic chamber 13 becomes the "intermediate holding position",
No oil is supplied to No. 4 or oil is not discharged from each hydraulic chamber 13, 14. As a result, since the vane 29 is held from both sides by the hydraulic pressure in the hydraulic chambers 13 and 14, the rotation of the vane 29 is restricted and the housing 28
The position of the vane 29 in the rotational direction with respect to is fixed. As a result, the current opening / closing timing of the intake valve is maintained until the OCV 16 is controlled by the ECU 17 and the rotational phase of the intake side camshaft 12 is changed again.

As described above, in the valve timing changing device according to this embodiment, the opening / closing timing of the intake valve is changed continuously (steplessly) by controlling the opening degree of the OCV 16, and the opening / closing timing is changed. Can be held.

Further, in this embodiment, when the engine is in a predetermined operating state, the lock pin 43 is locked in the locking hole 49, so that the vane 29 and the housing 28 are relatively rotated. It is regulated, and the position of the vane 29 in the rotation direction is fixed to the above-mentioned “most retarded position”.

More specifically, when the engine is stopped, the spool 76 of the OCV 16 moves to the first operating position shown in FIG. 1 by the urging force of the spring 79. As a result, each advance-side hydraulic chamber 13 communicates with the oil pan 57 through the advance-side hydraulic passage P1, and each retard-side hydraulic chamber 14 communicates with the discharge side of the oil pump 15 through the retard-side hydraulic passage P2. To be done. Then, when the rotation of the crankshaft is stopped, the discharge of oil from the oil pump 15 is stopped, and further,
The rotation of the intake camshaft 12 also stops. At this time, the vane 29 rotates in the retard rotation direction with respect to the driven gear 22, and the rotation phase thereof is delayed. As a result, the position of the vane 29 in the rotational direction with respect to the housing 28 becomes the "most retarded position" shown in FIG. This is because oil is no longer discharged from the oil pump 15, so that the hydraulic pressures in the advance-side hydraulic chambers 13 and the retard-side hydraulic chambers 14 decrease, and the vanes 29 are held by the hydraulic pressures in the hydraulic chambers 13 and 14. Because it will disappear.

Further, when the drive of the oil pump 15 is stopped, the hydraulic pressure in the hydraulic chamber 44 and the locking hole 49 decreases. As a result, the lock pin 43 moves to the base end side of the intake side camshaft 12 by the urging force of the spring 48, and the base end side portion thereof engages with the locking hole 4 as shown in FIG.
It is fitted into the inside of the container 9.

By locking the lock pin 43 in the locking hole 49, the vane 29 and the driven gear 2 are locked.
The relative rotation with respect to 2 is regulated. As a result, the opening / closing timing of the intake valve is fixed to the state that is most delayed with respect to the rotation phase of the crankshaft. Then, in the present embodiment, the operation of the engine is restarted, and the opening / closing valve timing of the intake valve is held in the most delayed state until the hydraulic pressure in each hydraulic passage P1, P2 becomes equal to or higher than a predetermined value.

The present embodiment described above has the following features. (A) In the present embodiment, the annular groove 51 has an annular shape centered on the rotation axis of the intake camshaft 12.

Therefore, when the cover 38 and the vane 29 are attached to the intake side camshaft 12 by the attachment bolts 84, the air hole 38a of the cover 38 and the annular groove 5 are attached.
There is no need to align with 1.

That is, since the annular groove 51 has a shape extending in the axial direction of the intake side camshaft 12, when the cover 38 is attached, as shown by the broken line in FIG. Even if the positions of the vane 38 and the vane 29 are deviated from each other, the inside of the annular groove 51 and the outside of the cover 38 are always communicated by the air hole 38a.
As described above, according to the present embodiment, the work of aligning the air hole 38a and the annular groove 51 is not necessary, so that the work efficiency in the work of assembling the valve timing changing device can be improved.

In addition, since it is not necessary to align the air hole 38a with the annular groove 51, a positioning member such as a knock pin is unnecessary, and the number of parts can be reduced.
Manufacturing costs can be reduced.

(B) In the present embodiment, even if the positions of the cover 38 and the vane 29 in the rotational direction are displaced, the inside of the annular groove 51 and the outside of the cover 38 are always communicated by the air holes 38a. . Therefore, the lock pin 4
When 3 moves in the through hole 42, the air is reliably moved between the back pressure chamber 42b and the outside of the cover 38.

Therefore, in order to prevent the oil from leaking from the hydraulic chamber 44 and the locking hole 49, the gap between the outer peripheral wall of the lock pin 43 and the inner peripheral wall of the through hole 42 is made as small as possible. Even in such a case, the movement of the lock pin 43 is not hindered by the pressure of air in the back pressure chamber 42b.

Therefore, according to the present embodiment, it is possible to suppress the oil from leaking from the hydraulic chamber 44 or the locking hole 49, and further, the lock pin 4 in the through hole 42.
3 can be moved smoothly.

(C) In the present embodiment, from the start of the engine operation until the oil pressure in the advance hydraulic passage P1 or the retard hydraulic passage P2 increases to a predetermined value or more, That is, the position of the vane 29 is fixed to the "most retarded position" until the hydraulic pressure exceeds the biasing force of the spring 48.

That is, when the hydraulic pressure of the oil in the hydraulic passages P1 and P2 is lowered immediately after the engine is started and the vane 29 cannot be held by the hydraulic pressure, the lock pin 43 is used. Relative rotation between the vane 29 and the housing 28 is restricted. Therefore, it is possible to prevent the vane 29 from vibrating and colliding with the housing 28 due to the torque fluctuation generated in each intake side camshaft 12, or the abnormal noise caused by the collision.

(Second Embodiment) Next, a second embodiment of the present invention will be described with reference to FIG. In this embodiment, the exhaust side camshaft 23 has the VV
The configuration is different from that in the first embodiment in that the T mechanism 11 is provided.

Incidentally, the VVT mechanism 11 in this embodiment,
And the configuration of the advance side and retard side hydraulic passages P1 and P2 for supplying oil to the advance side and retard side hydraulic chambers 13 and 14 formed in the mechanism 11 or the OCV 16 and the like. Is the same as that of the first embodiment, the same reference numerals are given to the same configurations and the description thereof is omitted.

As shown in FIG. 11, a cam pulley 26 is integrally rotatably fixed to one end of the exhaust side cam shaft 23, and a timing belt 27 is hung around the outer periphery of the pulley 26. On the exhaust side camshaft 23,
The timing belt 27 is adapted to transmit the rotational driving force of the crankshaft.

VV is attached to the other end of the exhaust side camshaft 23.
The T mechanism 11 is attached. The mechanism 11 is replaced with the driven gear 22 described in the first embodiment,
A drive gear 91 as a second rotating body is provided. Further, external teeth 92a are provided on the end of the intake side camshaft 12.
Is provided with a driven gear 92.
2 is meshed with the outer teeth 91a of the drive gear 91.

According to the present embodiment having the above-mentioned structure, the rotational driving force of the crankshaft is the exhaust side camshaft 23.
And is also transmitted from the shaft 23 to the intake side camshaft 12 via the drive gear 91 and the driven gear 92. Then, the intake side camshaft 12
The intake valve (not shown) is opened / closed by the cam 20 in accordance with the rotation. In the present embodiment, the intake camshaft 12 corresponds to the camshaft of the present invention.

Further, the relative rotation phase of the drive gear 91 with respect to the exhaust side cam shaft 23 is changed by the VVT mechanism 11. Therefore, the rotation phase of the intake camshaft 12 is changed, and the opening / closing timing of the intake valve is changed.

The present embodiment has the same configuration as that of the first embodiment except that the valve opening / closing timing of the intake camshaft 12 not provided with the VVT mechanism 11 is changed. There is. Therefore, this embodiment is
The operation is similar to that of the above-described embodiment, and has the same features as the features (a) to (c) described above.

Each of the embodiments described above can be implemented by changing the configuration as follows. (1) In each of the above embodiments, the annular groove 51 having an annular shape constitutes the communication space of the present invention, but the communication space is not limited to the configuration shown in the above embodiments. For example, the communication space may be formed by the oil groove 93 having a semicircular arc shape as shown in FIG.
In the case where the oil groove 93 is provided, it is necessary to align the cover 38 with the vane 29. However, since the positional deviation between the air hole 38a and the oil groove 93 is allowed within a range of about 180 ° in the rotation direction, the positioning work is extremely easy and a positioning member such as a knock pin is newly required. It will never happen.

(2) In each of the above embodiments, the vane 29
Although the annular groove 51 is formed on the side surface on the tip side of the above, the groove may be formed on the side surface of the cover 38 facing the side surface on the tip side of the vane 29.

(3) In the first embodiment, the vane 29 and the cover 38 are fixed to the intake side camshaft 12, and the housing 28 is fixed to the driven gear 22 or the drive gear 91. It is also possible to have a different configuration. That is, the vane 29 is driven by the driven gear 2
The housing 28 and the cover 38 are fixed to the intake-side camshaft 12 so as to be integrally rotatable, while being fixed to the drive gear 91 or the drive gear 91 so as to be integrally rotatable. And
A hole corresponding to the through hole 42 is formed in the housing 28, a lock pin is arranged in the hole, and the lock pin is locked by the locking hole 49. Even with such a configuration, the same operation and effect as those of the above embodiment can be obtained.

(4) In each of the above embodiments, the locking portion in the present invention is configured by the locking hole 49. However, the locking hole 49 is omitted, and the end face of the lock pin 43 on the proximal end side is driven by the driven gear 22. Alternatively, the relative rotation between the vane 29 and the housing 28 may be restricted by pressing the tip end side surface with the biasing force of the spring 48. In addition, a plurality of lock pins 43 and locking holes 49
The rotation of the vane 29 and the housing 28 may be restricted by the above.

(5) In each of the above embodiments, the hydraulic chambers are provided on both sides of the pressure receiving portion in the rotating direction of the vane 29. However, the hydraulic chambers may be provided on only one side. For example, the retard side hydraulic chamber 14, the retard side hydraulic passage P2 for supplying oil to the chamber 14, and the second retard side hydraulic chamber P2 for supplying oil into the locking hole 49.
The pressure passage 50 is omitted, and an elastic member such as a coil spring or a leaf spring for urging the vane 29 in the retard angle rotation direction is disposed in the space corresponding to the retard angle side hydraulic chamber 14.
Then, when advancing the valve opening / closing timing, the vane 29 is rotated in the advancing rotation direction by the hydraulic pressure of the advancing hydraulic chamber 13, and is brought into contact with the protruding portion 33 as shown in FIG. On the contrary, when the valve opening / closing timing is delayed, the supply of oil into the advance-side hydraulic chamber 14 is stopped, and the vane 29 is rotated in the retard rotation direction by the elastic member. Lock pin 43 at the most retarded position
Is locked in the locking hole 49 to restrict the rotation of the vane 29 with respect to the housing 28.

With such a configuration, the valve opening / closing timing of the intake valve can be selectively changed to two timings corresponding to the position of the vane 29 shown in FIGS. 4 and 5.

(6) In each of the above embodiments, the driven gear 22 or the drive gear 91 is changed to a cam pulley, and the VVT mechanism 11 is changed to a structure in which a timing belt is hung on the pulley, and the pulley is used as a crankshaft. The rotary driving force may directly drive the rotation.

(7) In each of the above-mentioned embodiments, the structure in which the four pressure receiving portions 32 are formed in the vane 29 is adopted, but it is also possible to adopt a structure in which the pressure receiving portions 32 are three or less, or five or more. it can. When the number of the pressure receiving portions 32 is smaller than that in each of the above-described embodiments, the configuration of each of the hydraulic passages P1 and P2 can be simplified. A large rotating torque can be applied.

(8) In each of the above embodiments, the housing 28 and the driven gear 22 are formed as separate members, but it is also possible to integrally form both members 28 and 22, for example. Similarly, the intake side camshaft 12
And the vane 29 may be integrally configured.

(9) In each of the above embodiments, the VVT mechanism 11 may be employed in which the cam pulley 26 is changed to a timing sprocket and the timing belt 27 is changed to a timing chain.

(10) In each of the above embodiments, the opening / closing timing of the intake valve is changed, but the opening / closing timing of the exhaust valve may be changed.
Further, the VVT mechanism 11 may be provided on both the intake side camshaft 12 and the exhaust side camshaft 23, and the valve opening / closing timings of both the intake valve and the exhaust valve may be changed.

Although the respective embodiments embodying the present invention have been described, the technical ideas which can be grasped from the respective embodiments will be described below together with the effects thereof. (A) In the valve timing changing device for an internal combustion engine according to claim 1 or 2, the locking portion formed on the second rotating body is a locking hole that is recessed in the moving direction of the movable member. Characterize.

With this structure, when the movable member moves in the insertion hole, a part of the movable member is locked in the locking hole. Therefore, relative rotation between the first rotating body and the second rotating body can be reliably regulated.

[0104]

As described in detail above, according to the invention described in claims 1 and 2, between the contact surface of the first rotating body and the cover, the circumferential direction of the rotating shaft center of the both rotating bodies is defined. A communication space extending to the first rotation body is formed so that the communication hole communicates with the air hole of the cover. Therefore, when the cover is attached to the first rotating body, a positional deviation corresponding to the length in the circumferential direction is allowed between the air hole and the insertion hole. As a result, the work of aligning the air hole and the insertion hole becomes easy, and the work efficiency at the time of assembling the valve timing changing device can be improved.

Furthermore, since a positioning member such as a knock pin for positioning the cover and the first rotating body is not necessary, the number of parts can be reduced. As a result, the manufacturing cost of the valve timing changing device can be reduced.

In particular, according to the second aspect of the invention, since the communication space is formed in an annular shape centered on the position of the rotation axis, the work of aligning the air hole and the insertion hole is unnecessary, and the assembly is eliminated. The work efficiency of the attaching work can be further improved.

[Brief description of drawings]

FIG. 1 is a sectional view showing an intake camshaft, a VVT mechanism, and the like.

FIG. 2 is a partial cross-sectional view showing an OCV.

FIG. 3 is a plan view showing an intake side, an exhaust side camshaft and the like.

4 is a sectional view taken along line IV-IV in FIG.

FIG. 5 is a sectional view showing a vane, a housing and the like.

FIG. 6 is an enlarged cross-sectional view showing a lock pin, a communication path, and the like.

FIG. 7 is an enlarged sectional view showing a lock pin, a communication path, and the like.

FIG. 8 is an enlarged cross-sectional view showing an enlarged pressure receiving portion.

FIG. 9 is a sectional view taken along line IX-IX of FIG. 8;

FIG. 10 is a side view showing the positional relationship between air holes and annular grooves.

FIG. 11 is a plan view showing an intake side, an exhaust side camshaft and the like.

FIG. 12 is a side view showing an oil groove and an air hole in another embodiment.

FIG. 13 is a cross-sectional view showing a valve opening / closing timing changing device in the prior art.

FIG. 14 is a cross-sectional view showing a valve timing changing device in the prior art.

15 is a partially enlarged sectional view of FIG.

16 is a left side view of FIG.

[Explanation of symbols]

11 ... Phase change mechanism, 12 ... Intake side cam shaft (cam shaft), 13 ... Advance side hydraulic chamber (pressure chamber), 14 ... Retard side hydraulic chamber (pressure chamber), 15 ... Oil pump (fluid supply means) , 16 ... OCV (fluid supply means), 18 ... Cylinder head (constituting a part of internal combustion engine), 22 ... Driven gear (second rotary body), 28 ... Housing (second rotary body), 29 ... Vane (first 1 rotating body), 38 ... cover, 3
8b ... Air hole, 42 ... Through hole (insertion hole), 43 ... Lock pin (movable member), 49 ... Locking hole (locking part), 51 ... Annular groove (communication space), 57 ... Oil pan (fluid supply) Means), 91 ... Drive gear (second rotary body), 93 ... Oil groove (communication space), P1 ... Advance side hydraulic passage (fluid supply means), P2 ... Delay side hydraulic passage (fluid supply means).

Claims (2)

[Claims] 1. Rotating about the same axis of rotation,
A first rotating body and a second rotating body, one of which is disposed on the inner side of the other, a cover fixed to the first rotating body so as to be rotatable integrally therewith, and covering side portions of the both rotating bodies; Of the internal combustion engine, which includes a pressure chamber defined by the concave and convex portions formed on the inner and outer peripheral portions and the cover, and a fluid supply unit for supplying a fluid of a predetermined pressure to the pressure chamber. One of a crankshaft and a camshaft for opening and closing a valve of the engine is drivingly connected to the first rotating body, and the other of the shafts is a second one.
The rotational phase of the camshaft with respect to the crankshaft is changed by rotating the two rotating bodies relative to each other by the pressure of the fluid that is drivingly connected to the rotating body and is supplied to the pressure chamber by the fluid supply means, thereby opening / closing the valve. The first rotating body is formed with an insertion hole extending in the direction of the rotation axis, and the second rotating body is formed with a locking portion.
A cam with respect to the crankshaft by moving a movable member arranged in the insertion hole in the direction of the rotation axis and locking the member at the locking portion to restrict relative rotation of the two rotating bodies. A valve timing changing device for an internal combustion engine, wherein a rotation phase of a shaft is maintained at a predetermined phase, the valve timing changing device extending in a circumferential direction of the rotation axis between a contact surface between the first rotating body and a cover. A valve timing changing device for an internal combustion engine, wherein a communication space communicating with the hole is formed and an air hole is formed in the cover to communicate with the communication space and the outside of the cover. 2. The valve timing changing device for an internal combustion engine according to claim 1, wherein the communication space is formed in an annular shape around the position of the rotation axis.