JP2003343217A - Valve-timing adjusting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve-timing adjusting device, in which if necessary, rotations of a 1st rotary body and a 2nd rotary body are positively controlled, and if unnecessary, the rotation control is stably released without depending on changes of state in an internal combustion engine. <P>SOLUTION: When a notch 19c of a holding pin 19 meshes with a ring groove 12b of a lock pin 12 in a lock-release state, where the lock pin 12 comes out of a fitting hole 17, the holding pin 19 stops sliding of the lock pin 12. When a vane of a case 2 comes into contact with a shoe of a case 2 at the top retard- position, a slide part 19b of the pin 19 is depressed to release the lock-up of the lock pin 12 by the holding pin 19. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve timing adjusting device for controlling the opening / closing timing of either or both of an intake valve and an exhaust valve of an internal combustion engine (hereinafter referred to as engine).

[0002]

2. Description of the Related Art Conventionally, various proposals have been made as valve timing adjusting devices. Most of these are hydraulic valve timing adjusting devices, which include a housing integrally having a sprocket that rotates in synchronization with the rotational drive force from the crankshaft of the engine, and a plurality of hydraulic chambers positioned and fixed in the housing. And a rotor having a plurality of shoes that form a plurality of shoes and a plurality of vanes that are rotatably accommodated in the case and that partition the plurality of hydraulic chambers into an advance side hydraulic chamber and a retard side hydraulic chamber. And a lock mechanism for restricting relative rotation between the rotor and the case at a position corresponding to a reference position when the engine is started. The lock mechanism includes, for example, a fitting hole formed in the boss portion of the rotor, a lock pin that can be fitted in the fitting hole and is slidably housed in a housing hole formed in the shoe of the case, and The coil spring is roughly composed of a coil spring which is arranged between the lock pin and the bottom of the accommodation hole and always biases the lock pin toward the fitting hole.

In an operating region where the hydraulic pressure is not sufficiently secured, such as when the engine is started, if the relative rotation between the rotor and the case is not restricted, it is defined by the shoe of the case and the vane of the rotor. The rotor may flutter within a certain operating angle range, and abnormal noise may occur, or the timing may not be adjusted, which may deteriorate engine startability. Therefore, it is necessary to reliably restrain the rotor with respect to the housing and the case that rotate in synchronization with the crankshaft by the lock pin of the lock mechanism to restrict the relative rotation of the two.

Between the hydraulic chambers and the oil pump,
An oil control valve (hereinafter referred to as OCV) is provided. By the valve opening / closing control of the OCV, the necessary hydraulic pressure is controlled to be supplied to and discharged from the hydraulic chamber. That is, when hydraulic pressure is supplied to the retard side hydraulic chamber, the rotor rotates relatively to the case relative to the retard side, and when hydraulic pressure is supplied to the advance side hydraulic chamber, the rotor advances to the case side. Rotate relative to. In this way, the rotor operates by a predetermined angle with respect to the case, so that the phase of the camshaft with respect to the crankshaft can be variably controlled, whereby the valve opening / closing timing can be appropriately controlled according to the operating condition. .

In order for the rotor and the case to rotate relative to each other in this manner, it is necessary that the lock pin is reliably released from the fitting hole. This is because if the lock pin is not reliably released, twisting will occur between the rotor and the lock pin when the rotor rotates with respect to the case due to the supply and discharge of hydraulic pressure to the hydraulic chamber, and the rotor will operate. become unable.
That is, not only the desired valve timing cannot be adjusted, but if such a phenomenon continues for a long time, the durability of the lock pin may be affected.

Various measures have been taken in order to solve such inconveniences. For example, Japanese Patent No. 3033582 discloses a valve timing adjusting device that releases and holds a lock pin with hydraulic pressure on both the advance side and the retard side. In this case, the lock pin is urged in the releasing direction by the hydraulic pressures on both the advance side and the retard side, so that if either hydraulic pressure is sufficiently supplied, the lock pin is surely released and held. It will be.

[0007]

However, since the conventional valve timing adjusting device according to the above-mentioned patent is constructed as described above, for example, when the hydraulic pressure of the supply source decreases due to a change in the operating state of the engine, or when the oil pressure at the supply source decreases, When the supplied hydraulic pressure is switched between the angle side and the retard angle side, the pressure in the hydraulic chamber also decreases, so there is a possibility that the lock pin may be fitted when not intended.

Further, in Japanese Patent Laid-Open No. 2000-291414, a piston for holding the lock pin at an intermediate position of engagement is provided, and the piston is fitted in the fitting hole with a slight gap in preparation for the next releasing operation. A valve timing adjustment device is disclosed. In this case, since it is released from the half-fitted state, the release performance is improved, but on the contrary, even when the lock pin needs to be securely fitted, such as when the engine is stopped or when the engine is started, it can be released by the piston in the releasing direction. Since it is biased, it may not be possible to reliably fit it.

The present invention has been made in order to solve the above problems, and the rotation of the first rotating body and the second rotating body is performed when necessary without being influenced by the change in the state of the internal combustion engine. It is an object of the present invention to provide a valve timing adjusting device capable of reliably controlling the valve timing and stably releasing the release state of the rotation restriction when unnecessary.

[0010]

A valve timing adjusting device according to the present invention includes a first rotating body that rotates in synchronization with a crankshaft of an internal combustion engine, a second rotating body that rotates in synchronization with a camshaft of the internal combustion engine, and a first rotating body. A rotation restricting mechanism that restricts relative rotation between the first rotating body and the second rotating body, and a release state holding mechanism that mechanically holds the restriction released state of the rotation restricting mechanism.

In the valve timing adjusting device according to the present invention, the rotation restricting mechanism is provided in any one of the advance side hydraulic chamber and the retard side hydraulic chamber formed between the first rotating body and the second rotating body. The rotation restriction is released by one of the hydraulic pressures.

In the valve timing adjusting device according to the present invention, the release state holding mechanism is rotated by contact between the first rotating body and the second rotating body at the reference position of the first rotating body with respect to the second rotating body. The holding of the regulation release state of the regulation mechanism is released.

In the valve timing adjusting device according to the present invention, the release state holding mechanism is provided with the holding member for holding the deregulated state of the rotation restricting mechanism and the holding member in the direction for maintaining the holding state by the holding member. And a biasing means for biasing.

In the valve timing adjusting device according to the present invention, the urging force of the urging means of the release state holding mechanism is set to be larger than the maximum hydraulic pressure of the internal combustion engine which acts on the tip of the holding member of the release state holding mechanism. It is composed.

[0015]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described below. Embodiment 1. FIG. 1 shows the internal structure of the valve timing adjusting device according to the first embodiment, and shows a radial cross section showing a state in which the second rotary body is constrained to the most retarded angle position as a reference position with respect to the first rotary body. 2 is a diagram and FIG. 2 is I of FIG.
FIG. 4 is an axial cross-sectional view taken along line I-II, FIG. 3 is an enlarged radial cross-sectional view showing a main part of FIG. 1, and FIG. 4 is a perspective view showing a main part of FIG. 3. FIG. 5 is a radial cross-sectional view showing an internal configuration of the valve timing adjusting device according to the first embodiment and showing a state in which the second rotating body is rotated to the most advanced position with respect to the first rotating body, 6 is an axial sectional view taken along the line VI-VI of FIG. 5, FIG. 7 is an enlarged radial sectional view showing an essential part of FIG. 5, and FIG. 8 shows an essential part of FIG. It is a perspective view.

In the figure, reference numeral 1 is a housing (first rotating body). The housing 1 transfers rotational driving force from a crankshaft (not shown) of an engine (not shown) to an intake side camshaft (not shown) or an exhaust side camshaft (not shown) and a timing chain (not shown). ) Is integrally provided with a chain sprocket portion 1a for transmitting the rotational drive force of the engine via the housing 1 and a valve timing adjusting device is fastened to the camshaft by a bolt (not shown). (Not shown), so that they can rotate in synchronization with each other. A case (first rotating body) 2 is positioned and fixed to the housing 1. The case 2 has a plurality of (four in the first embodiment) shoes 2a to 2d for projecting radially inward from the inner periphery thereof to form a plurality of hydraulic chambers.

Reference numeral 3 denotes a rotor (second rotating body) fastened and fixed to the end of a camshaft (not shown) with bolts (not shown). The rotor 3 has a boss portion 3a located at the center.
And a plurality of hydraulic chambers projecting radially outward from the outer periphery of the boss portion 3a and formed by the case 2 are divided into an advancing-side hydraulic chamber 4 and a retarding-side hydraulic chamber 5 (the first embodiment). 4) vanes 3b to 3e. Recesses 6 are formed along the axial direction at the protruding tips of the vanes 3b to 3e of the rotor 3. A resin-made seal member 7 that slides in close contact with the inner peripheral surface of the case 2 in the recess 6, and a seal member 7 integrally fixed to the seal member 7 and constantly biasing the seal member 7 toward the inner peripheral surface of the case 2. The leaf spring 8 is inserted. The seal member 7 and the leaf spring 8 constitute a sealing mechanism which prevents mutual oil flow between the advance side hydraulic chamber 4 and the retard side hydraulic chamber 5 and holds the pressure in each hydraulic chamber. It should be noted that the advance side hydraulic chamber 4 in the first embodiment is formed of the advance side hydraulic chambers 4a to 4d, and the retard side hydraulic chamber 5 is formed of the retard side hydraulic chambers 5a to 5d.

Further, the oil seal between the tip portions of the shoes 2a to 2d of the case 2 and the outer peripheral surface of the boss portion 3a of the rotor 3 is provided by appropriately setting the clearance between the respective components.

The advance side hydraulic chamber 4 and the retard side hydraulic chamber 5 are
Of the two axial end faces of the case 2 and the rotor 3, respectively, they are sealed by a cover (first rotating body) 9 arranged on the axial end face on the opposite side to the housing 1 side. The cover 9 includes the case 2, the housing 1, and the plurality of bolts 1
The first rotary body is fastened by 0 and rotates in synchronization with a crankshaft (not shown).

In the first embodiment, one shoe 2a of the case 2 has a housing hole (rotation restricting mechanism) penetrating in the radial direction.
11 is formed. The accommodation hole 11 is a two-stage hole having a different inner diameter, and has a small-diameter portion 11a having a small inner diameter formed near the inner circumference of the case 2 and an inner diameter of the small-diameter portion 11a formed near the outer circumference of the case 2 from the small diameter portion 11a. Also has a large diameter portion 11b having a large inner diameter.

A lock pin (rotation restricting mechanism) 12 is housed in the housing hole 11. Lock pin 12 is hole 1
1 is a stepped pin with a different outer diameter,
The front small-diameter portion 12a having an outer diameter capable of sliding in the first small-diameter portion 11a, a ring groove (released state holding mechanism) 12b formed on the outer periphery of the front small-diameter portion 12a, and the front small-diameter portion 12a. A rear large diameter portion 12c located rearward and having an outer diameter capable of sliding in the large diameter portion 11b of the accommodation hole 11, and a rear end recess 12d formed at the rear end of the rear large diameter portion 12c.
It is composed of and. In addition, when the lock pin 12 is advanced to the maximum extent and the tip portion of the lock pin 12 projects from the small diameter portion 11a of the accommodation hole 11 to the inside of the case 2 and comes into contact with a fitting hole described later, the diameter of the accommodation hole 11 is large. A certain amount of clearance is provided between the front end surface of the portion 11b and the front end surface of the rear large diameter portion 12c of the lock pin 12 in order to form a lock release hydraulic chamber described later. On the contrary, the lock pin 12
The lock pin 12 can be retracted in the accommodation hole 11 to such an extent that the tip portion of the lock pin 12 is completely immersed in the accommodation hole 11.

A lock pin 12 and a stopper 13 for preventing a coil spring, which will be described later, from protruding are fitted into the outermost portion of the large-diameter portion 11b of the accommodation hole 11 and are prevented from coming off by a pin 14. The stopper 13 has a central concave portion 13a, and a drain hole 15 for discharging air and leaked oil remaining behind the lock pin 12 to the outside of the apparatus when the lock pin 12 is retracted is provided in the central portion of the central concave portion 13a. It is formed so as to penetrate in the axial direction.

A coil spring 16 is arranged between the rear recess 12d of the lock pin 12 and the central recess 13a of the stopper 13 to constantly bias the lock pin 12 forward of the housing hole 11. It should be noted that the lock pin 12 causes the spring 1 to move by the hydraulic pressure supplied to the valve timing adjusting device.
It is possible to retreat against the biasing force of 6.

A fitting hole 17 for receiving the fitting of the front small diameter portion 12a of the lock pin 12 is formed in the outer peripheral portion of the boss portion 3a of the rotor 3. A predetermined clearance is set between the fitting hole 17 and the front small-diameter portion 12a of the lock pin 12, and the front small-diameter portion 12a of the lock pin 12 has a predetermined pin angle defined by the clearance. The fitting hole 17 is fitted smoothly. Further, in the first embodiment, the fitting hole 17 is provided at a position corresponding to the outer peripheral portion of the boss portion 3a so that the reference position at the time of engine start with respect to the case 2 of the rotor 3 is, for example, the most retarded position. .

A holding groove (released state holding mechanism) 18 is formed on the end surface of the shoe 2a of the case 2 in the axial direction of the cover 9 along the direction orthogonal to the extending direction of the accommodation hole 11.
The holding groove 18 is a two-step groove having the same depth (in the apparatus axial direction in FIG. 1) and different widths (in the apparatus radial direction in FIG. 1). The holding groove 18 has a large width in the first groove 18a and the first groove 18a. The second groove 1 which is continuously formed and has a width smaller than that of the first groove 18a.
And 8b. One end of the second groove 18b is configured to open into the advance-side hydraulic chamber 4a adjacent to the shoe 2a of the case 2. Such a holding groove 18
A slidable holding pin (holding member of the released state holding mechanism) 19 is accommodated therein. As shown in FIGS. 1 and 3, the holding pin 19 includes a flange portion 19a that can be accommodated in the first groove 18a of the holding groove 18, the width of the flange portion 19a, and the groove width of the ring groove 12b of the lock pin 12. A sliding portion 19b having a smaller width and capable of being housed in the second groove 18b, and an inner diameter slightly larger than the outer diameter of the front small diameter portion 12a of the lock pin 12 formed on the central side portion of the sliding portion 19b. The semi-circular cutout recessed portion 19c has a schematic configuration. Holding groove 18
Between the one wall portion of the first groove 18a and the collar portion 19a of the holding pin 19, a coil spring for constantly urging the holding pin 19 toward the advance side hydraulic chamber 4a side (biasing means of the release state holding mechanism).
20 are provided.

As shown in FIG. 1, when the rotor 3 is at the most retarded position with respect to the case 2, the vanes 3 of the rotor 3 are located.
Simultaneously with the contact of b with the shoe 2a of the case 2, the contact surface of the vane 3b and the end surface of the sliding portion 19b of the holding pin 19 contact. By this contact, the sliding portion 19b of the holding pin 19
From the state in which the tip end of the projection protrudes from the contact surface of the shoe 2a toward the advance side hydraulic chamber 4a side, it is pushed back against the urging force of the coil spring 20, and the end portion of the end portion of the holding groove 18 advances from the advance side hydraulic chamber 4a. It does not project to the side. In this state, the circular arc center of the cutout recess 19c of the holding pin 19 and the lock pin 1
Since the center of the circular arc of the front small diameter portion 12a of 2 is the concentric position, the lock pin 12 can freely move without being restricted by the holding pin 19.

Further, as shown in FIG. 5, when the rotor 3 is not in the most retarded position with respect to the case 2, that is, when the rotor 3 is in the advanced state, the vane 3b of the rotor 3 has the shoe 2 of the case 2.
Separate from a. Due to this separation, the sliding portion 19b of the holding pin 19 is moved forward by the urging force of the coil spring 20,
The tip portion thereof projects from the holding groove 18 to the advance side hydraulic chamber 4a side. In this state, as shown in FIG. 7 and FIG.
The cutout recess 19c of the holding pin 19 is in a state where the center of the arc is displaced from the front small diameter portion 12a of the lock pin 12 and the ring groove 12b. Therefore, the holding pin 19 can stop the lock pin 12 from sliding by engaging the notch recess 19 c with the ring groove 12 b of the lock pin 12.

Next, each oil passage formed in the valve timing device will be described. The housing 1 is formed with a plurality of (four in the first embodiment) advance-side oil passages 21a to 21d that obliquely penetrate from the camshaft bearing portion 1b to the rotor sliding surface 1c. Further, the boss portion 3a of the rotor 3 is formed with a plurality of lag side oil passages 22a to 22d that penetrate in the radial direction. The advance side oil passages 21a to 21d and the retard side oil passages 22a to 22d.
Is switched between oil supply / discharge (hereinafter referred to as supply / discharge) by an OCV (not shown), and oil supply / discharge of the advance-side hydraulic chambers 4a to 4d and retard-side hydraulic chambers 5a to 5d is performed. The phase of a camshaft (not shown) can be changed by controlling the hydraulic pressure of the and rotating the rotor 3 by a predetermined angle.

A through hole 23 is formed in the shoe 2a of the case 2 along the axial direction of the apparatus, and the rotor sliding surface 1c of the housing 1 adjoins the shoe 2a of the case 2 on the retard angle side hydraulic chamber. Groove passage 2 for communicating 5a with through hole 23
4 are formed. Also, the large diameter portion 11b of the accommodation hole 11
Between the front end surface of the lock pin 12 and the front end surface of the rear large-diameter portion 12c of the lock pin 12, there is formed a lock release hydraulic chamber 25 that can communicate with the retard side hydraulic chamber 5a via the through hole 23 and the groove passage 24. ing. When the oil pressure in the retard side hydraulic chamber 5a is supplied to the unlocking hydraulic chamber 25 via the groove passage 24 and the through hole 23, the hydraulic pressure is changed by the difference in diameter between the rear large diameter portion 12c and the front small diameter portion 12a of the lock pin 12. Is received by the ring-shaped pressure receiving surface generated from the coil spring 16 and reaches a predetermined hydraulic pressure, the coil spring 16
Against the urging force of the lock pin 12, the lock pin 12 retracts in the accommodation hole 11 outward in the radial direction of the device, and releases the rotor restriction state. Here, when the lock pin 12 is released by receiving hydraulic pressure, the rotor 3 receives the hydraulic pressure on the retard angle side and is securely held at the most retarded angle position. There is a predetermined clearance between the portion 12a and the fitting hole 17 in the rotor 3. Therefore, no twisting occurs between the lock pin 12 and the fitting hole 17, and the lock pin 12 can be reliably released.

Next, the operation will be described. First, as the control pattern of the valve timing adjusting device, an advance mode in which the valve is rotated in the advance direction from the most retarded position, which is a reference position at the time of starting the engine, and conversely, rotation is performed in the retard direction from the advance position. There are a retard angle mode and an intermediate holding mode for holding the intermediate advanced position.

When the engine is started, the rotation driving force is transmitted to the housing 1 through the timing chain (not shown) by the rotation of the crankshaft (not shown), and the housing 1 and the case 2 are first rotated. Next, as an initial state, the lock pin 12 is released, and the rotor 3
Is in a position other than the most retarded position and the holding pin 19 is projected to the advance side hydraulic chamber 4a by the urging force of the coil spring 20, the case 2 rotates so that the rotor 3 is relatively retarded. The holding pin 19 is pushed back against the biasing force of the coil spring 20 by the rotor abutting force at the time of contact with the case 2 at the most retarded position, and the holding pin 19 slides. The position where the tip of the portion 19b does not protrude from the most retarded contact surface, that is, the cutout concave portion 1 of the holding pin 19
9c and the front small diameter portion 12a of the lock pin 12 are moved to a position where they coincide with each other. As a result, the lock pin 12 is released from the holding restriction by the holding pin 19 and can slide.
The urging force of the coil spring 16 moves the inside of the accommodation hole 11 inward in the radial direction of the device, and the front small diameter portion 12a thereof engages with the fitting hole 17. As a result, the rotor 3 is securely fixed to the case 2, and the camshaft (not shown) is also integrated with the case 2 to start synchronous rotation with the crankshaft (not shown). Therefore, the rotor 3 and the cam shaft (not shown) integrated therewith are securely locked to the case 2, so that the rotor 3 does not flutter due to a cam load when the engine is started, and noise or startability is generated. Can be prevented from worsening.

When the engine is ignited, it goes through the peak rotation speed at the time of complete explosion, and then settles down to the idle rotation speed according to the conditions at that time. At this time, the OCV (not shown) is controlled so that the oil passage is on the retard side, and hydraulic pressure is supplied to the retard side hydraulic chamber 5. Therefore, since the rotor 3 is held at the most retarded position and is in contact with the shoe 2a at the same position, the holding pin 19 is held in the direction not restricting to the lock pin releasing state side, and the lock pin 12 is It is movable. In this state, hydraulic pressure is supplied to the unlocking hydraulic chamber 25 via each oil passage, and the lock pin 12 reliably moves to the unlocked state.

Next, in order to change the opening / closing timing of the intake valve or the exhaust valve as the operating state changes, the OC
When a command is input to V (not shown), an OCV (not shown) valve opens a passage on the advance side, and oil is supplied to the advance side oil passages 21a to 21d. Therefore, since the lock pin 12 is in the unlocked state by the preceding retard side hydraulic pressure, the hydraulic pressure is supplied to the advance side hydraulic chamber 4, and the rotor 3 starts relative rotation in the advance direction (advance). Angle mode). When the rotor 3 slightly rotates relative to each other and moves away from the most retarded contact surface of the shoe 2a of the case 2, the holding pin 19 moves to the coil spring 20.
The urging force of the above causes it to project into the advance-side hydraulic chamber 4a. When the holding pin 19 moves in this direction with the lock pin 12 released, as shown in FIGS. 7 and 8, the arc center of the cutout recess 19c is displaced from the axial center of the lock pin 12. The ring groove 1 in which the sliding portion 19b of the holding pin 19 is formed on the circumference of the front small diameter portion 12a of the lock pin 12.
By engaging with 2b, it is possible to hold the lock pin 12 in the rotor regulation released state. Once the lock pin 12 is released, the unlocked state can be reliably maintained under any engine condition until the rotor 3 contacts the most retarded position.

If the sliding portion 19b of the holding pin 19 projects into the advance-side hydraulic chamber 4a, the hydraulic pressure in the advance-side hydraulic chamber 4a is transferred to the tip surface of the sliding portion 19b of the holding pin 19. In the first embodiment, it is assumed that the maximum hydraulic pressure of the engine (for example, 700 kP is assumed).
The relationship between the load of the coil spring 20 and the cross-sectional area of the holding pin 19 is set so that the holding pin 19 does not retract even when a pressure of about a) is received. That is, the coil spring 2
The biasing force based on the load of 0 is set to be larger than the engine maximum hydraulic pressure that acts on the tip surface of the holding pin 19. Therefore, the operation of the holding pin 19 is not affected by the hydraulic pressure at all,
It depends only on the contact force of the rotor 3 and the biasing force of the coil spring 20.

Next, when the operating state further changes and a command is input to the OCV (not shown) in order to return the opening / closing timing of the valve to the reference position, the valve of the OCV (not shown) passes through the retard side. open. When it is switched to the retard side, the oil pressure is passed from the retard oil passages 22a to 22d through the passage formed in the camshaft (not shown) to the corresponding retard hydraulic chambers 5a to 5d. Is supplied. The rotor 3 is driven by the hydraulic pressure supplied from the retard side hydraulic chambers 5a to 5d.
Starts rotating in the retard direction with respect to the case 2. At the same time, the oil pressure is supplied to the unlocking hydraulic chamber 25 via the groove passage 24 and the through hole 23, so that the rotor 3 returns to the most retarded position, and the vane 3b of the rotor 3 is the most retarded position of the shoe 2a of the case 2. Contact the corner contact surface. Due to this abutment, the holding pin 19 is pushed back against the biasing force of the coil spring 20, and the holding state of the lock pin by the holding pin 19 is released. However, the hydraulic pressure in the retard angle side hydraulic chamber 5d is supplied to the lock releasing hydraulic chamber 25 via the groove passage 24 and the through hole 23, and the deregulated state of the lock pin 12 is continuously maintained by this hydraulic pressure.

Next, when the engine is stopped, the oil pump (not shown) is stopped. Therefore, the advance side hydraulic chambers 4a to 4d and the retard side hydraulic chambers 5a to 5d in the valve timing adjusting device are further stopped. Oil remaining in the oil passage is OC
It flows down to an oil pan (not shown) through V (not shown) and an oil pump (not shown). As a result, the retard side hydraulic chamber 5a applied to the unlock hydraulic chamber 25
When the hydraulic pressure of is gradually decreased and falls below the biasing force of the coil spring 16, the lock pin 12 is not locked by the holding pin 19 and therefore moves forward to fit into the fitting hole 17 on the rotor 3 side. The relative rotation between the rotor 3 and the case 2 is restricted.

As described above, according to the first embodiment, since the holding pin 19 for mechanically holding the unlocked state of the lock pin 12 is provided, the hydraulic pressure fluctuation depending on the engine state is prevented. There is an effect that the regulation release state of the lock pin 12 can be stably held without being affected. For this reason, it is possible to prevent the lock pin 12 that has been released once from being fitted into the fitting hole 17 again unintentionally due to fluctuations in hydraulic pressure, and the lock pin 12 is prevented from being caught in the fitting hole 17. 3 can be reliably operated, and the careless fitting operation of the lock pin 12 is reduced, so that the number of times of operation of the lock pin 12 can be reduced, and the reliability against wear of the lock pin 12 and the fitting hole 17 is improved. it can. Furthermore, this function can be achieved with a simple structure.

In the first embodiment, when the engine start reference position of the rotor 3 with respect to the case 2 is set to the most retarded position, the unlocking hydraulic pressure of the lock pin 12 is supplied from the retarded hydraulic chamber 5a which is easy to apply. Since it is configured as described above, there is an effect that it is possible to realize both the lock releasing property that can be surely unlocked when necessary and the release state holding property that can reliably hold the lock released state by the holding pin 19 or the like. is there. In the first embodiment, the retard side hydraulic pressure is used as the lock release hydraulic pressure, but the advance side hydraulic pressure may be used as the lock release hydraulic pressure when the engine start reference position is set to the most advanced position. .

In the first embodiment, the holding pin 19 and the like are configured to release the lock pin 12 in the unlocked state when the rotor 3 and the case 2 contact each other at the engine start reference position. The holding of the lock pin 12 in the unlocked state by the holding pin 19 or the like can be reliably released at the reference position. As a result, there is an effect that the unlocked state of the lock pin 12 can be stably maintained without being affected by the hydraulic pressure fluctuation depending on the engine state.

In the first embodiment, the holding pin 19 and
Coil spring 20 that constantly urges this holding pin 19
Since the release state holding mechanism has a simple structure, it is possible to minimize the cost increase associated with the installation of the release state holding mechanism.

In the first embodiment, the biasing force of the coil spring 20 is set to be larger than the engine maximum hydraulic pressure acting on the tip of the holding pin 19,
Even if the engine maximum oil pressure acts on the tip of the holding pin 19,
Since the operation of the holding pin 19 is not affected, the effect of hydraulic pressure on the operation of the holding pin 19 can be avoided.

Embodiment 2. FIG. 9 shows an internal structure of the valve timing adjusting device according to the second embodiment, and shows a radial cross section showing a state in which the second rotary body is constrained to the most retarded position as a reference position with respect to the first rotary body. Is a figure,
10 is an axial cross-sectional view taken along the line XX of FIG. 9, and FIG. 11 shows that the second rotating body in the valve timing adjusting device shown in FIG. 9 is restrained at the most advanced position with respect to the first rotating body. It is a radial direction sectional view which shows the state rotated without being carried out, and FIG. 12 is an axial direction sectional view seen in the XII-XII line of FIG. Among the constituent elements of the second embodiment, the first embodiment
The same symbols are attached to the same components as
The description of that part is omitted.

The feature of the second embodiment lies in that the moving direction of the lock pin in the rotation restricting mechanism is the axial direction of the apparatus.

The characteristic structure will be described below. The vane 3b of the rotor 3 has a housing hole 50 formed in the axial direction of the device.
A small-diameter spring holding hole 51 is formed in the accommodation hole 50 on the inner side of the cover 9. The lock pin 12 is a straight pin and is movable in the accommodation hole 50 in the device axial direction. A coil spring 16 that constantly biases the lock pin 12 toward the housing 1 is disposed between the rear end recess 12d of the lock pin 12 and the spring holding hole 51. A fitting hole 17 is formed in the rotor sliding surface 1c of the housing 1, and the lock pin 12 can be fitted into the fitting hole 17 to restrict relative rotation between the housing 1 and the rotor 3. .

An unlocking hydraulic chamber 52 having an inner space having a semicircular cross section is formed on the rotor sliding surface 1c adjacent to the fitting hole 17.
Is formed, and an oil groove 53 that connects the lock release hydraulic chamber 52 and the retard side hydraulic chamber 5a is formed.
When the hydraulic pressure in the retard side hydraulic chamber 5 a is introduced into the fitting hole 17 via the oil groove 53 and the lock releasing hydraulic chamber 52, the retard side hydraulic pressure is applied to the tip surface of the lock pin 12. This applied hydraulic pressure causes the lock pin 12 to withdraw from the fitting hole 17 against the biasing force of the coil spring 16 and release the rotation restriction of the rotor 3, as shown in FIGS.

A through hole 54 is formed at the bottom of the spring holding hole 51 toward the cover 9 side end surface of the rotor 3. From this through hole 54, an oil groove 55 formed on the cover side end surface of the rotor, The oil groove 56 of the cover 9 and the path of the oil passage in the device mounting bolt (path shown by arrow A in FIG. 10)
The air behind the lock pin and leaked oil can be discharged with.

Further, in the vane 3b of the rotor 3, a holding hole 57 is formed in the vicinity of the receiving hole 50 along the direction orthogonal to the lock pin moving direction (device axial direction), and this holding hole 57 is formed. , Holding pin 19 and coil spring 20
Has been inserted. The sliding portion 19b of the holding pin 19 is formed with a semicircular or crescent-shaped notch recess 19c. The sliding portion 19b of the holding pin 19 is the lock pin 1
By engaging with the ring groove 12b formed on the outer periphery of the lock pin 2, it is possible to reliably hold the lock pin 12 in the released state as shown in FIGS. 11 and 12.

As described above, according to the second embodiment, the configuration is basically the same as that of the first embodiment except that the moving direction of the lock pin 12 is the device axial direction. Similar to the first aspect, there is an effect that the deregulated state of the lock pin 12 can be stably maintained without being influenced by the hydraulic pressure fluctuation depending on the engine state.

[0049]

As described above, according to the present invention, the first rotating body that rotates in synchronization with the crankshaft of the internal combustion engine,
A second rotating body that rotates in synchronization with the camshaft of the internal combustion engine;
Since the rotation restricting mechanism that restricts the relative rotation between the first rotating body and the second rotating body and the release state holding mechanism that mechanically holds the deregulated state of the rotation restricting mechanism are configured. By the release state holding mechanism, the release state of the rotation restricting mechanism can be stably maintained without being affected by the hydraulic pressure fluctuation depending on the internal combustion engine state. There is an effect that it can be surely prevented.

According to the present invention, the rotation restricting mechanism includes the first
Since the rotation restriction is released by the hydraulic pressure of one of the advance side hydraulic chamber and the retard side hydraulic chamber formed between the rotating body and the second rotating body, the rotation regulating mechanism is provided. There is an effect that the restriction can be surely released by the hydraulic pressure on the side where the rotation restriction can be easily released by.

According to this invention, the release state holding mechanism is
The first rotation body and the second rotation body are brought into contact with each other at the reference position of the first rotation body with respect to the second rotation body, so that the holding of the regulation release state of the rotation regulation mechanism is released. It is possible to reliably release the holding of the restriction release state of the rotation restricting mechanism by the release state holding mechanism at the reference position for performing the restriction. Accordingly, there is an effect that the deregulated state of the rotation restricting mechanism can be stably maintained without being affected by the hydraulic pressure fluctuation depending on the internal combustion engine state.

According to the present invention, the release state holding mechanism is
Since the holding member that holds the restriction release state of the rotation restricting mechanism and the biasing unit that constantly biases the holding member in the direction of maintaining the holding state by the holding member, the release state holding mechanism has a simple structure. Therefore, there is an effect that the cost increase due to the installation of the release state holding mechanism can be suppressed to the minimum.

According to this invention, the urging force of the urging means of the release state holding mechanism is set to be larger than the maximum hydraulic pressure of the internal combustion engine which acts on the tip of the holding member of the release state holding mechanism. Even if the maximum hydraulic pressure of the internal combustion engine acts on the tip of the holding member, it does not affect the operation of the holding member, so that the effect of the hydraulic pressure on the operation of the holding member can be avoided.

[Brief description of drawings]

FIG. 1 is a radial direction showing an internal configuration of a valve timing adjusting device according to a first embodiment and showing a state in which a second rotary body is constrained to a maximum retard position as a reference position with respect to a first rotary body. FIG.

FIG. 2 is an axial sectional view taken along line II-II of FIG.

FIG. 3 is a radial cross-sectional view showing an enlarged main part of FIG.

FIG. 4 is a perspective view showing a main part of FIG.

FIG. 5 is a radial cross-sectional view showing an internal configuration of the valve timing adjusting device according to the first embodiment and showing a state in which the second rotating body is rotated to the most advanced position with respect to the first rotating body. .

6 is an axial sectional view taken along line VI-VI in FIG.

7 is a radial cross-sectional view showing an enlarged main part of FIG.

FIG. 8 is a perspective view showing a main part of FIG.

FIG. 9 is a radial direction showing an internal configuration of the valve timing adjusting device according to the second embodiment and showing a state in which the second rotating body is constrained with respect to the first rotating body at the most retarded position as a reference position. FIG.

FIG. 10 is an axial cross-sectional view taken along the line XX of FIG.

11 is a radial cross-sectional view showing a state in which the second rotating body in the valve timing adjusting device shown in FIG. 9 is rotated with respect to the first rotating body without being constrained to the most advanced position.

12 is an axial sectional view taken along line XII-XII in FIG.

[Explanation of symbols]

1 housing (first rotating body), 2 case (first rotating body), 3 rotor (second rotating body), 4 advance angle side hydraulic chamber,
5 Retardation-side hydraulic chamber, 6 Recessed portion, 7 Seal member, 8 Leaf spring, 9 Cover (first rotating body), 10 Bolt, 11
Housing hole (rotation restriction mechanism), 12 Lock pin (rotation restriction mechanism), 13 Stopper, 14 pin, 15 Drain hole, 16 Coil spring, 17 Fitting hole, 18
Holding groove (released state holding mechanism), 19 holding pin (holding member of released state holding mechanism), 20 coil spring (biasing means of released state holding mechanism), 21a to 21d advance side oil passage, 22a to 22d retarded angle Side oil passage, 23 through hole,
24 groove passage, 25 lock release hydraulic chamber, 50 housing hole, 51 spring holding hole, 52 lock release hydraulic chamber, 53 oil groove, 54 through hole, 55 oil groove, 56 oil groove, 57 holding hole.

Claims (5)

[Claims] 1. A first rotating body that rotates in synchronization with a crankshaft of an internal combustion engine, a second rotating body that rotates in synchronization with a camshaft of the internal combustion engine, and a relative relationship between the first rotating body and the second rotating body. A valve timing adjusting device comprising: a rotation restricting mechanism that restricts a rotation; and a release state holding mechanism that mechanically holds a restriction release state of the rotation restricting mechanism. 2. The rotation restricting mechanism restricts rotation by the hydraulic pressure of either one of the advance side hydraulic chamber and the retard side hydraulic chamber formed between the first rotating body and the second rotating body. The valve timing adjusting device according to claim 1, wherein the valve timing adjusting device is configured to be released. 3. The release state holding mechanism holds the deregulation state of the rotation restricting mechanism by abutting the first rotating body and the second rotating body at the reference position of the first rotating body with respect to the second rotating body. The valve timing adjusting device according to claim 1, wherein the valve timing adjusting device is configured to be released. 4. The release state holding mechanism includes a holding member that holds the deregulated state of the rotation restricting mechanism, and a biasing unit that constantly biases the holding member in a direction to maintain the holding state of the holding member. The valve timing adjusting device according to claim 1, further comprising: 5. The urging force of the urging means of the release state holding mechanism is set to be larger than the maximum hydraulic pressure of the internal combustion engine that acts on the tip of the holding member of the release state holding mechanism. Valve timing adjustment device.