JP2004150278A - Valve timing regulator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing regulator having a mechanism for preventing both rotors from being carelessly reengaged during relatively rotating after the rotors are unlocked. <P>SOLUTION: A radially slidable lock pin 51 of the valve timing regulator 1 is arranged in a lock pin containing hole 50 at a first rotor 10 side. A slider (closing member) 58 slidable along the axial direction of a slider containing hole 55 is arranged in the hole 55 of the rotor 30 side as the second rotor, and a bush 59 is press injected to a position near an outer peripheral surface 30f of the rotor 30 of the hole 55. An engaging hole 59a passing along the axial direction of the bush 59 and for allowing the pin 51 to be engaged is formed. The slider 58 hydraulically slides to push out the pin 51 engaged within the hole 59a and to close the hole 59a. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a valve timing adjusting device for adjusting the opening / closing timing of an intake valve or an exhaust valve which abuts on a cam fixed to an intake camshaft or an exhaust camshaft of an internal combustion engine such as an engine. It is.
[0002]
[Prior art]
The conventional valve timing adjustment device is integrally fixed to an end surface of an intake side or exhaust side camshaft and a first rotating body which is connected to a crankshaft of an engine by a power transmission member such as a chain and rotates synchronously with the crankshaft. And a second rotating body disposed so as to be relatively rotatable by a predetermined angle in the first rotating body.
[0003]
The first rotating body includes a housing having a sprocket portion that receives the rotational driving force of the crankshaft and a bearing portion that slides on an outer peripheral surface near an end surface of the intake or exhaust camshaft; And a cover for closing the hydraulic chamber of the case are integrated by a plurality of first fastening members. The hydraulic chamber of the case is formed by a plurality of shoes protruding inward in the radial direction inside the case.
[0004]
The second rotator is provided with a boss fixed to the end face of the intake or exhaust camshaft, and projects radially outward from the outside of the boss to rotate the hydraulic chamber toward the advance side of the second rotator. And a plurality of vanes partitioned into an advanced hydraulic chamber for receiving the hydraulic pressure to be applied and a retard hydraulic chamber for receiving the hydraulic pressure for rotating the second rotating body to the retard side. A first oil passage formed in the intake or exhaust camshaft is connected to the advance hydraulic chamber, and a second oil passage formed in the intake or exhaust camshaft is connected to the retard hydraulic chamber. Have been. The first oil passage and the second oil passage are connected to an oil pump and an oil pan via an oil control valve (hereinafter, referred to as OCV).
[0005]
For example, a lock pin that is urged radially inward by an urging means and protrudes toward the second rotator is provided on one shoe of the case of the first rotator. On the other hand, on the outer peripheral portion of the boss portion of the second rotating body, an engagement hole for receiving the engagement of the lock pin at the time of restricting the relative rotation between the first rotating body and the second rotating body, such as when the engine is stopped or started, is provided. Is formed. In addition, as a formation position of the engagement hole, a position where the second rotating body is most advanced with respect to the first rotating body (hereinafter, referred to as a most advanced position), and a position where the second rotating body is most advanced relative to the first rotating body. There is a delayed position (hereinafter referred to as a most retarded position) or a position between the most advanced position and the most retarded position (hereinafter referred to as an intermediate position).
[0006]
Next, the operation will be described.
First, when the engine is stopped or immediately after the engine is started, the oil in the advance-side hydraulic chamber and the retard-side hydraulic chamber of the valve timing adjustment device is supplied to the oil pan via the first oil passage, the second oil passage, the OCV, and the like. Since the lock pin is returned, the lock pin is engaged with the engagement hole by the urging force of the urging means, and the relative rotation between the first rotating body and the second rotating body is restricted (rotation restricted state. Say).
[0007]
Next, when the oil pump is operated by starting the engine, the oil is supplied to the advance hydraulic chamber or the retard hydraulic chamber of the valve timing adjusting device via the OCV. When the advance-side hydraulic pressure or the retard-side hydraulic pressure is applied to the lock pin, the lock pin is pushed back radially outward against the urging force of the urging member and comes out of the engagement hole. And the second rotating body can be relatively rotated by a predetermined angle by the advance-side hydraulic pressure or the retard-side hydraulic pressure (rotation restriction released state; also referred to as unlocked state). (For example, see Patent Document 1)
[0008]
[Patent Document 1]
Japanese Patent Application Laid-Open No. 2002-155713 (Claim 3, FIG. 3)
[0009]
[Problems to be solved by the invention]
However, since the conventional valve timing adjusting device has the above-described configuration, there are the following problems.
First, when performing intermediate holding control for holding the second rotating body at the intermediate position with respect to the first rotating body during the operation of the engine, the supply of both the advance hydraulic pressure and the retard hydraulic pressure is stopped by the OCV (actually, When only the advanced hydraulic pressure is applied), both the advanced hydraulic pressure and the retarded hydraulic pressure decrease, and the lock pin may advance inward in the radial direction due to the urging force of the urging member. Here, especially when the engaging hole is formed at the intermediate position, the intermediate holding control is performed near the engaging hole, the unlocked state cannot be held, and the lock pin is not inserted into the engaging hole. There is a problem that there is a risk of re-fitting.
[0010]
In the conventional valve timing adjusting device, the lock pin is pulled out of the engagement hole to release the rotation restriction by controlling both the advance-side hydraulic pressure and the retard-side hydraulic pressure, but during relative rotation, As the hydraulic chamber is enlarged due to the relative rotation between the first rotating body and the second rotating body, the lock release holding hydraulic pressure acting on the tip of the lock pin is reduced to about half of the hydraulic pressure supplied from the engine. If the lock pin is relatively rotated in the range over the engagement hole because the state cannot be maintained, the lock pin may be re-fitted into the engagement hole during the relative rotation and rotated to the target rotation position. There was a problem that it might not be possible.
[0011]
Further, it is difficult to detect the re-engagement of the lock pin into the engagement hole, and once in the engaged state, a control command for changing the relative angle between the two rotating bodies is input and the hydraulic pressure is supplied to the hydraulic chamber. Then, since the relative rotation operation of the second rotator with respect to the first rotator is faster than the unlocking operation of retracting the lock pin, prying occurs between the outer surface of the lock pin and the inner surface of the engagement hole. There is a problem that the lock may not be released smoothly.
[0012]
SUMMARY OF THE INVENTION The present invention has been made to solve the above-described problems, and provides a valve timing adjusting device having a mechanism for preventing an accidental re-fitting during the relative rotation of both rotating bodies after unlocking. The purpose is to:
[0013]
[Means for Solving the Problems]
A valve timing adjusting device according to the present invention is configured such that a first rotating body that rotates synchronously with a crankshaft of an internal combustion engine, and is fixed to an end face of an intake or exhaust camshaft and relatively rotatable within the first rotating body by a predetermined angle. A second rotator disposed, and one of the second rotator and the first rotator disposed at a predetermined position relative to the first rotator and the second rotator. A rotation restricting member that restricts the relative rotation of the two rotators when formed, and is formed on one of the other of the first rotator and the second rotator and controls the relative rotation of the two rotators. And an engagement hole that receives the engagement of the rotation restricting member and is closed after the relative rotation restriction of the two rotating bodies is released.
[0014]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment of the present invention will be described.
Embodiment 1 FIG.
1 is an axial sectional view showing an internal configuration of a valve timing adjusting device according to Embodiment 1 of the present invention, FIG. 2 is a radial sectional view taken along line II-II in FIG. 1, and FIG. FIG. 4 is an enlarged radial sectional view showing a locked state between the first rotating body and the second rotating body in the valve timing adjusting device shown in FIG. 2; FIG. 4 is a valve timing adjusting apparatus shown in FIG. 1 and FIG. FIG. 5 is an enlarged radial sectional view showing an unlocked state between a first rotating body and a second rotating body in the device, and FIG. 5 shows sliding of a lock member when unlocking the valve timing adjusting device shown in FIG. FIG. 6 is a radial cross-sectional view showing the state in an enlarged manner, and FIG. 6 is a schematic diagram showing the entire configuration of a hydraulic supply / discharge system incorporating the valve timing adjusting device shown in FIGS. 1 to 5.
[0015]
In the figure, reference numeral 1 denotes a valve timing adjusting device, which is connected to a crankshaft (not shown) of an engine (not shown) by a power transmission member (not shown) such as a chain and rotates in synchronization with the crankshaft. The rotating body 10 is integrally fixed to an end surface of an intake-side or exhaust-side camshaft (hereinafter, referred to as a camshaft) 20 with a bolt 21 and is disposed so as to be relatively rotatable within the first rotating body 10 by a predetermined angle. The second rotating body 30 is roughly configured. The valve timing adjusting device 1 controls the second rotating body 30 at the intermediate position between the most advanced position and the most retarded position, which is the relative position between the first rotating body 10 and the second rotating body 30. This is a so-called intermediate lock type that restricts rotation with respect to the one rotating body 10. As described later, a rotation restricting member that regulates relative rotation between the first rotating body 10 and the second rotating body 30 is a first rotating member. A so-called radial lock in which the valve timing adjusting device 1 is slidably disposed on the rotating body 10 side in the radial direction and an engagement hole for allowing engagement of the rotation restricting member is provided on the second rotating body 30 side. Configuration.
[0016]
The first rotating body 10 integrally has a sprocket portion 11a that receives the rotational driving force of the crankshaft, and a housing 11 that has a sliding contact portion 65 that is inwardly slidingly contacting an outer peripheral surface near an end surface of the camshaft 20, A plurality of (four in the first embodiment) shoes 12a, 12b, 12c, and 12d are provided adjacent to the housing 11 and project inward in the radial direction to form a plurality of spaces. It is roughly composed of a case 12 and a cover 13 for closing the space of the case 12, and is integrally fastened and fixed by bolts 14.
[0017]
As shown in FIG. 1, the second rotating body 30 has a boss portion 30 a integrally fastened and fixed to the end surface of the camshaft 20 with a bolt 21, and a plurality of radially outwardly protruding portions on the outer peripheral portion of the boss portion 30 a ( In the first embodiment, the rotor has four) vanes 30b, 30c, 30d, and 30e (hereinafter, the second rotating body 30 is referred to as a rotor 30). The vane 30b of the rotor 30 divides a space formed between the shoe 12d and the shoe 12a of the case 12 into an advanced hydraulic chamber 31a and a retarded atmospheric chamber 32a, and the vane 30c is connected to the shoe 12a and the shoe 12b. Is divided into an advance-side pressure chamber 31b and a retard-side hydraulic chamber 32b, and the vane 30d defines a space formed between the shoe 12b and the shoe 12c as the advance-side hydraulic chamber 31c. The vane 30e divides the space formed between the shoe 12c and the shoe 12d into the advance hydraulic chamber 31d and the retard hydraulic chamber 32d.
[0018]
Except for the shoe 12a of the case 12 according to the first embodiment, the tip of each of the shoes 12b, 12c, and 12d is provided between an advanced hydraulic chamber 31a and a retard hydraulic chamber 32d, as shown in FIG. Prevents the flow of hydraulic oil between the advance hydraulic chamber 31c and the retard hydraulic chamber 32b and between the advance hydraulic chamber 31d and the retard hydraulic chamber 32c, and maintains the pressure in each chamber. Sealing members 33a, 33b and 33c are provided. In addition, the tip of each of the vanes 30b, 30c, 30d, and 30e of the rotor 30 is provided between the advance hydraulic pressure chamber 31a and the retard hydraulic pressure chamber 32a, and between the advance hydraulic pressure chamber 31b and the retard hydraulic pressure chamber 32b. , Between the advance hydraulic chamber 31c and the retard hydraulic chamber 32c, and between the advance hydraulic chamber 31d and the retard hydraulic chamber 32d. Seal members 33d, 33e, 33f, and 33g for maintaining pressure are provided. For example, as shown in FIG. 2, the seal member 33 c is roughly composed of a flexible resin seal 34 and a leaf spring 35 that presses the seal 34 against the outer peripheral surface 30 f of the rotor 30. Has the same configuration.
[0019]
Further, between the shoe 12d of the case 12 and the vane 30b of the rotor 30, between the shoe 12b of the case 12 and the vane 30d of the rotor 30, and between the shoe 12c of the case 12 and the vane 30e of the rotor 30, An assist spring 37 held by each holder 36 is provided. The assist spring 37 moves the rotor 30 with respect to the case 12 against a valve reaction force received in a retarded direction (the direction of the arrow Y in FIG. 1) from the camshaft 20 when the engine is stopped or started without hydraulic pressure. It is always biased in the angular direction (the direction of arrow X in FIG. 1). The holder 36 improves the assemblability of the assist spring 37 and prevents interference between the plurality of assist springs 37.
[0020]
Inside the boss portion 30a of the rotor 30 and the camshaft 20, there is provided a first oil passage 38 which communicates with the advance hydraulic pressure chambers 31a, 31c and 31d to supply and discharge the hydraulic pressure, except for the advance hydraulic pressure chamber 31b. Except for the retard side pressure chamber 32a, there is provided a second oil passage 39 communicating with the retard side hydraulic chambers 32b, 32c and 32d to supply and discharge the hydraulic pressure. As shown in FIG. 6, the first oil passage 38 and the second oil passage 39 are configured to receive supply and discharge of oil pressure by an oil pump 41 and an oil pan 42 via an OCV 40. Although the hydraulic pressure is not supplied to the advance side pressure chamber 31b and the retard side pressure chamber 32a, as shown in FIG. 1, the advance side pressure chamber 31b and the retard side pressure chamber 32a are not supplied. Further, an advance-side drain passage 43 and a retard-side drain passage 44 for communicating oil to the atmosphere and discharging oil are provided.
[0021]
Among the shoes of the case 12, a lock pin housing hole 50 penetrating in the radial direction is formed in the shoe 12a sandwiched between the advance side pressure chamber 31b and the retard side pressure chamber 32a. A lock pin (rotation restricting member) 51 for restricting the relative rotation between the case 12 and the rotor 30 when the engine is stopped or started, and allowing the relative rotation when the engine is running. Are slidably disposed along the axial direction of the lock pin storage hole 50. The lock pin 51 is roughly composed of a cylindrical pin main body 51a and a bottomed hole 51b formed in the bottom of the pin main body 51a along the axial direction.
[0022]
A bush 52 having a bottomed hole 52a is inserted into the lock pin housing hole 50 near the outer peripheral surface of the case 12, and the bush 52 is orthogonal to the axial direction of the lock pin housing hole 50. It is positioned and fixed by a shaft 53 inserted along the direction. Between the bottomed hole 52a of the bush 52 and the bottomed hole 51b of the lock pin 51 opposed thereto, a coil spring 54 for constantly urging the lock pin 51 in the direction of arrow Z1 is provided. At the bottom of the bottomed hole 52a of the bush 52, a back pressure drain passage 52b for discharging back pressure generated in the lock pin storage hole 50 to the atmosphere when the lock pin 51 retreats in the direction of arrow Z2 is formed. I have.
[0023]
On the other hand, the outermost portion of the boss 30a of the rotor 30 is located at a most advanced position where the shoe 12a and the vane 30b of the rotor 30 are in contact with the shoe 12a of the case 12, and the shoe 12a and the vane 30c. A slider housing hole 55 for receiving the insertion of the lock pin 51 is formed along the radial direction at an intermediate position distant from any of the most retarded positions at which the slider contact is made. The slider housing hole 55 has an inner diameter slightly larger than the outer diameter of the lock pin 51. The slider housing hole 55 has a bottom portion 55a, and the bottom portion 55a is formed with one end of a third oil passage 56 for supplying hydraulic pressure into the slider housing hole 55. As shown in FIG. 6, the third oil passage 56 is provided with an oil pressure of the oil pump 41 and the oil pan 42 via an opening / closing control valve 57 independent of the first oil passage 38 and the second oil passage 39 via the OCV 40. It is configured to receive supply and discharge.
[0024]
A slider (closing member) 58 slidable along the axial direction of the slider storage hole 55 is provided in the slider storage hole 55, and is located at a position in the slider storage hole 55 near the outer peripheral surface 30 f of the rotor 30. The bush 59 is press-fitted. The slider 58 is a sliding member that pushes back the lock pin 51, which engages with the engagement hole 59a of the bush 59 pressed into the slider housing hole 55, in the direction of the arrow Z2 against the urging force of the coil spring 54. 51, a small-diameter portion 58a having an outer diameter substantially equal to the outer diameter of the pin body 51a, a large-diameter portion 58b located closer to the bottom portion 55a of the slider housing hole 55 than the small-diameter portion 58a, and a bottom portion of the large-diameter portion 58b. Even when the slider 55 is retracted and is in contact with the bottom 55a of the slider housing hole 55, the hydraulic pressure applied from the third oil passage 56 to the slider housing hole 55 quickly acts on the entire bottom of the slider 58. It is roughly constituted by a concave portion 58c for forming a space between the bottom of the slider 58 and the bottom 55a of the slider housing hole 55.
[0025]
The bush 59 is formed with an engagement hole 59a that penetrates along the axial direction and allows the lock pin 51 to be engaged. The inner peripheral surface of the engagement hole 59a has an inner diameter sufficient for the pin body 51a of the lock pin 51 and the small diameter portion 58a of the slider 58 to slide, and its axial length is the small diameter portion 58a of the slider 58. Is set so as to be substantially equal to the axial length. Therefore, as shown in FIG. 4, when the small-diameter portion 58a of the slider 58 slides in the direction of the arrow Z2 in the engagement hole 59a of the bush 59 by the hydraulic pressure, the sliding is caused by the large-diameter portion 58b of the slider 58 and the bush. When the slider 59 stops due to contact with the lower surface 59b, the distal end surface 58d of the small diameter portion 58a of the slider 58 and the upper surface 59c of the bush 59 are substantially flush. At this time, the outer peripheral surface 30f of the rotor 30, the upper surface 59c of the bush 59, and the distal end surface 58d of the slider 58 slide by the distal end surface 51c of the lock pin 51 when the lock pin 51 retreats in the direction of arrow Z1 (unlocked state). Therefore, it is ideal that the above-mentioned surfaces be flush with each other. However, in the actual assembling stage, it is necessary to consider an error in machining accuracy. That is, as shown in FIG. 5, the slider that slides inside the engagement hole 59 a of the bush 59 is stopped in the front slider housing hole 55 so that the upper surface 59 c of the bush 59 does not protrude from the outer peripheral surface 30 f of the rotor 30. When the tip surface 58d of the small diameter portion 58a of 58 is set to slightly project from the upper surface 59c of the bush 59, the upper surface 59c of the bush 59 is slightly recessed from the outer peripheral surface 30f of the rotor 30 and the tip surface 58d of the slider 58. However, since the width of the recess is much smaller than the width of the lock pin 51, the lock pin 51 does not enter or get caught in the recess, and the lock pin 51 on the outer circumferential surface 30 f of the rotor 30 does not. Can be smoothly slid. Further, as shown in FIG. 5, by forming the distal end surface 51c of the lock pin 51 as a curved surface that is convex with respect to the slider housing hole 55, the corner of the distal end surface 51c of the lock pin 51 can be caught in the recess. Therefore, it is possible to ensure the stability of the relative rotation between the case 12 and the rotor 30. If the upper surface 59c of the bush 59 and the tip surface 58d of the slider 58 are set to be flush with the outer peripheral surface 30f of the rotor 30 without considering the error in the processing accuracy, When the length of the small diameter portion 58a is shorter than the length of the engagement hole 59a of the bush 59, the tip surface 58d of the slider 58 is recessed from the upper surface 59c of the bush 59, and the lock pin 51 may fit into this recess. Occurs. Conversely, when the length of the small diameter portion 58a of the slider 58 is longer than the length of the engagement hole 59a of the bush 59, the distal end face 58d of the slider 58 projects beyond the outer peripheral surface 30f of the rotor 30 and the upper surface 59c of the bush 59. As a result, there is a possibility that the lock pin 51 is caught and hinders the relative rotation between the case 12 and the rotor 30.
[0026]
Next, the operation will be described.
First, when the engine is stopped, the oil pump 41 shown in FIG. 6 is not driven, so that the oil in the valve timing adjustment device 1, the first oil passage 38 and the second oil passage 39 flows down to the oil pan 42. ing. At this time, since the opening / closing control valve 57 is closed and the hydraulic pressure is not supplied to the third oil passage 56, the unlocking hydraulic pressure from the third oil passage 56 is not supplied into the slider housing hole 55, and The slider 58 in the hole 55 does not move with respect to the lock pin 51. Therefore, as shown in FIG. 3, the lock pin 51 slides in the direction of arrow Z1 by the urging force of the coil spring 54 and engages with the engagement hole 59a of the bush 59, so that the distal end surface 51c of the lock pin 51 is The slider 58 abuts on the distal end face 58 d of the small diameter portion 58 a and retracts it into the retraction space 55 b on the bottom 55 a side of the slider housing hole 55. Thereby, the relative rotation between the case 12 and the rotor 30 is restricted (locked state).
[0027]
Next, immediately after the engine is started, it is immediately after the oil pump 41 shown in FIG. 6 starts to be driven, and since the oil temperature is low and the viscosity is high, the first rotating body and the second rotating body of the valve timing adjusting device 1 Since it is difficult to control the relative rotation position of the slider at the target position, the open / close control valve 57 is closed, and the slider 58 does not operate with respect to the lock pin 51, and the locked state is maintained. In addition, since the hydraulic pressure is not supplied to the advance-side pressure chamber 31b and the retard-side pressure chamber 32a adjacent to the shoe 12a of the case 12 in which the lock pin 51 is provided, the shoe 12a No hydraulic pressure acts on the distal end surface 51c of the lock pin 51 through the clearance between the distal end surface and the outer peripheral surface 30f of the rotor 30. Therefore, also in this respect, there is no possibility that the locked state is inadvertently released. Even if oil enters the advance side pressure chamber 31b and the retard side pressure chamber 32a, the oil is quickly discharged through the advance side drain path 43 and the retard side drain path 44.
[0028]
Next, when the engine warm-up operation is completed, the oil temperature increases and the viscosity decreases. At this stage, it is sufficiently possible to control the relative rotation position between the first rotating body and the second rotating body in the valve timing adjustment device 1 at the target position. Here, when there is a control command, the open / close control valve 57 shown in FIG. 6 is switched from the closed state to the open state for supplying the hydraulic pressure to the third oil passage 56, and the hydraulic pressure (lock Release hydraulic pressure) is supplied to the inner space formed between the bottom 55a of the slider housing hole 55 and the recess 58c of the slider 58. As shown in FIG. 4, the slider 58 slides in the direction of arrow Z2 by the above-mentioned oil pressure until the large-diameter portion 58b of the slider 58 comes into contact with the lower surface 59b of the bush 59 and stops. It is retracted into the lock pin storage hole 50 against the urging force, and is pulled out from the engagement hole 59a of the bush 59 in the slider storage hole 55, and closes the engagement hole 59a of the bush 59 in the slider storage hole 55. At this time, when the lock pin 51 comes out of the engagement hole 50 completely, the engagement between them is released, and the relative rotation between the case 12 and the rotor 30 is permitted (unlocked state). As long as the unlocking oil pressure is supplied to the slider housing hole 55 through the third oil passage 56 while the opening / closing control valve 57 is in the open state, the unlocking state is set in the slider housing hole 55 by the slider 58 slid by the unlocking oil pressure. Since the engagement hole 59a of the bush 59 is closed, it is securely held.
[0029]
In addition, the third oil passage 56 includes advance-side hydraulic chambers 31a, 31c, and 31d in which hydraulic pressure changes due to a change in the relative angle between the case 12 and the rotor 30 during engine operation, and retard-side hydraulic chambers 32b, 32c. Since the first hydraulic passage 38 and the second hydraulic passage 39 communicating with the second hydraulic passage 32d and the second hydraulic passage 39 communicate with each other, a stable unlocking hydraulic pressure is applied to the slider 58 without being affected by the fluctuation of the hydraulic pressure. It is possible to continue.
[0030]
Further, the advance-side pressure chamber 31b and the retard-side pressure chamber 32a adjacent to the shoe 12a of the case 12 communicate with the atmosphere via the advance-side drain passage 43 and the retard-side drain passage 44, and the lock pin Since the space corresponding to the rear part of the lock pin 51 in the storage hole 50 communicates with the atmosphere through the air communication hole (not shown) of the bush 54 pressed into the lock pin storage hole 50, the slider 58 The sliding resistance received when sliding in the direction of arrow Z2 by the unlock hydraulic pressure from the third oil passage 56 is extremely small. Therefore, the slider 58 can slide quickly by the application of the unlocking oil pressure to push the lock pin 51 out of the engagement hole 59a and close the engagement hole 59a.
[0031]
Even if the unlocking hydraulic pressure applied to the slider 58 is the high oil temperature during engine operation and the minimum hydraulic pressure during low rotation, the slider 58 slides against the urging force of the coil spring 54 to unlock. For example, the urging force of the coil spring 54 is set so that the state can be maintained.
[0032]
Next, even during operation of the engine, the lock pin 51 is constantly urged in the direction of the arrow Z1 by the urging force of the coil spring 54, so that the vane 30b and the vane 30c of the rotor 30 when the case 12 and the rotor 30 rotate relative to each other. Is sliding on the outer peripheral surface 30f. On the other hand, since the engagement hole 59a is always closed by the slider 58, the re-fitting of the lock pin 51 to the engagement hole 59a is reliably prevented in any control state of the valve timing adjusting device 1. For example, when performing an intermediate holding control in which the relative angle between the case 12 and the rotor 30 is controlled such that the shoe 12a of the case 12 is held at an intermediate position away from any of the vanes 30b and the vanes 30c of the rotor 30. In this case, the lock pin 51 slides in the vicinity of the engagement hole 59a. In this case as well, since the engagement hole 59a is closed by the slider 58, the lock pin 51 is locked to the engagement hole 59a. Refitting of the pin 51 is reliably prevented.
[0033]
When the engine is stopped once, the oil in the first oil passage 38 and the second oil passage 39 and the like goes down to the oil pan 42, and the air stays in each oil passage. In this state, when the engine is restarted, the oil supplied from the first oil passage 38 or the second oil passage 39 into the valve timing adjusting device 1 is bitten by air even at high temperature and low viscosity. Therefore, it is difficult to control the valve timing adjustment device 1 to a position substantially intermediate between the most advanced position and the most retarded position. Also in this case, by closing the open / close control valve 57, the supply of the hydraulic pressure for unlocking the slider 58 can be stopped, and the locked state can be maintained. Next, by releasing the air trapped in the oil and then opening the opening / closing control valve 57, a hydraulic pressure for unlocking is supplied to the slider 58, and the lock pin 51 is pushed out from the engagement hole 59a to release the case. It is possible to control the rotor 30 at an arbitrary angle with respect to the rotor 12.
[0034]
As described above, according to the first embodiment, since the engagement hole 59a is configured to be closed immediately after the lock is released, the engine 12 in which the relative rotation between the case 12 and the rotor 30 is allowed. There is an effect that the re-fitting of the lock pin 51 to the engagement hole 59a can be reliably prevented during operation.
[0035]
According to the first embodiment, since the slider 58 is provided as a closing member for closing the engagement hole 59a, the engagement is performed immediately after the slider 58 pushes the lock pin 51 out of the engagement hole 59a and is unlocked. The mating hole 59a can be closed, and there is an effect that the re-fitting of the lock pin 51 to the engaging hole 59a can be reliably prevented during operation of the engine.
[0036]
According to the first embodiment, since the slider 58 is configured to be slidable in the axial direction of the engagement hole 59a as a closing member for closing the engagement hole 59a, the valve timing is adjusted in accordance with the sliding direction of the lock pin 51. Since the slider 58 can be accommodated inside the engagement hole 59a formed along the radial direction of the adjusting device 1, there is an effect that the radial size of the valve timing adjusting device 1 can be reduced.
[0037]
According to the first embodiment, since the slider 58 is configured to be slidable by hydraulic pressure as a closing member for closing the engagement hole 59a, the slider 58 can be operated by applying and releasing hydraulic pressure. This has the effect that the operational stability of the device can be ensured.
[0038]
According to the first embodiment, the third oil passage 56 that supplies the unlock hydraulic pressure (operating hydraulic pressure) acting on the slider 58 is connected to the case (first rotating body) 12 and the rotor (second rotating body) 30. The first oil passage 38 and the second oil passage 39 that supply the hydraulic pressure for relative rotation (advance-side oil pressure and retard-side oil pressure) are provided independently of each other. The slider 58 can be operated without being affected by the fluctuation generated in the angular hydraulic pressure, and the independent controllability of the unlocking operation by the slider 58 can be ensured.
[0039]
According to the first embodiment, the third oil passage 56 for supplying the unlock hydraulic pressure (operating hydraulic pressure) acting on the slider 58 is provided with the opening / closing control valve 57 for controlling the supply and stop of the unlock hydraulic pressure. With this configuration, it is possible to supply the unlock hydraulic pressure at an appropriate lock release timing according to the operating conditions of the engine, oil conditions, etc., and to securely maintain the unlocked state as long as the unlock hydraulic pressure is continuously supplied. There is an effect that can be.
[0040]
According to the first embodiment, since the slider 58 can be unlocked even at the lowest oil pressure during the operation of the engine, even if the unlock oil pressure applied to the slider 58 is the lowest oil pressure during the operation of the engine, the coil spring For example, it is possible to set the urging force of the coil spring 54 so that the slider 58 can be slid against the urging force of the coil 54 to maintain the unlocked state. There is an effect that the re-fitting of the lock pin 51 can be reliably prevented.
[0041]
According to the first embodiment, the engagement hole 59a is provided between the most advanced position and the most retarded position, which are relative positions of the rotor (second rotator) 30 with respect to the case (first rotator) 12. Since it is configured to be provided on the outer peripheral portion of the rotor 30, even when performing intermediate holding control in which the rotor 30 is controlled to an intermediate position with respect to the case 12, re-fitting of the lock pin 51 into the engagement hole 59a is not required. There is an effect that it can be reliably prevented.
[0042]
According to the first embodiment, since the lock pin 51 is pushed out from the engagement hole 59a to release the engagement of the lock pin 51 and the slider 58 for closing the engagement hole 59a is provided. Is versatile, and an increase in the number of parts can be suppressed.
[0043]
In the first embodiment, the valve timing adjusting device 1 is provided with the slider 58 that slides in the axial direction of the engagement hole 59a that allows the lock pin 51 that slides in the radial direction to be engaged. For example, a closing member that slides in a direction intersecting the axial direction of the engagement hole 59a and has a configuration like a slider used in a second embodiment described later may be adopted. Further, in the first embodiment, the left and right chambers of the lock pin are the air pressure chambers 32a and 31b, but may be hydraulic chambers.
[0044]
Embodiment 2 FIG.
7 is an axial sectional view showing an internal configuration of a valve timing adjusting device according to Embodiment 2 of the present invention, FIG. 8 is a radial sectional view taken along line VIII-VIII of FIG. 7, and FIG. 10 is an enlarged schematic perspective view showing a main part of FIG. 10, and FIG. 10 is an enlarged radial direction showing a locked state between the first rotating body and the second rotating body in the valve timing adjustment device shown in FIGS. FIG. 11 is a radial cross-sectional view showing, in an enlarged manner, an unlocked state between the first rotating body and the second rotating body in the valve timing adjusting device shown in FIGS. 7 to 9; FIG. 12 is a schematic diagram illustrating an overall configuration of a hydraulic supply / discharge system incorporating the valve timing adjustment device illustrated in FIGS. 6 to 11. Note that among the constituent elements of the second embodiment, those that are common to the constituent elements of the first embodiment are given the same reference numerals, and descriptions of those parts will be omitted.
[0045]
A feature of the second embodiment is that, similarly to the first embodiment, in a so-called intermediate lock type valve timing adjusting device, a rotation restricting member for restricting relative rotation between the first rotating body and the second rotating body is provided. A so-called axial lock configuration in which an axially slidable arrangement of the valve timing adjusting device is provided on the second rotating body side and an engagement hole for allowing engagement of the rotation restricting member is provided on the first rotating body side. And a closing member for closing the engagement hole is provided in the engagement hole so as to be slidable in a direction perpendicular to the axial direction of the engagement hole. This will be specifically described below.
[0046]
The first rotator 10 in the valve timing adjusting device 60 according to the second embodiment is disposed adjacent to the housing 11 and protrudes inward in the radial direction to form a plurality of spaces. A case 70 having a plurality of (four in the second embodiment) shoes 70a, 70b, 70c, and 70d, and a cover 13 for closing the space of the case 70, and are integrally fastened by bolts 14. Fixed.
[0047]
As shown in FIG. 7, the second rotator 80 has a boss 80a integrally fastened to the end face of the camshaft 20 with bolts 21 and a plurality of radially outwardly protruding portions (an outer periphery of the boss 80a). In the first embodiment, a rotor having four vanes 80b, 80c, 80d, and 80e (hereinafter, the second rotating body 80 is referred to as a rotor 80). The vane 80b of the rotor 80 partitions the space formed between the shoe 70d and the shoe 70a of the case 70 into an advanced hydraulic chamber 81a and a retard hydraulic chamber 82a, and the vane 80c is connected to the shoe 70a and the shoe 70b. Is divided into an advance-side hydraulic chamber 81b and a retard-side hydraulic chamber 82b, and the vane 80d defines a space formed between the shoes 70b and 70c with the advance-side hydraulic chamber 81c. The vane 80e divides the space formed between the shoe 70c and the shoe 70d into an advance hydraulic chamber 81d and a retard hydraulic chamber 82d.
[0048]
As shown in FIG. 7, the tip of each of the shoes 70a, 70b, 70c, and 70d of the case 70 according to the second embodiment has a retard angle between the retard hydraulic pressure chamber 82a and the advance hydraulic pressure chamber 81b. Operation between the side hydraulic chamber 82b and the advance hydraulic chamber 81c, between the retard hydraulic chamber 82c and the advance hydraulic chamber 81d, and between the retard hydraulic chamber 82d and the advance hydraulic chamber 81a. Seal members 33a, 33b, 33c, and 33d that prevent the flow of oil and maintain the pressure in each hydraulic chamber are provided. In addition, the leading ends of the vanes 80b, 80c, 80d and 80e of the rotor 80 are provided between the advance hydraulic chamber 81a and the retard hydraulic chamber 82a, the advance hydraulic chamber 81b and the retard hydraulic chamber 82b, respectively. , Between the advance hydraulic chamber 81c and the retard hydraulic chamber 82c and between the advance hydraulic chamber 81d and the retard hydraulic chamber 82d. Seal members 33e, 33f, 33g, and 33h for maintaining pressure are provided. For example, as shown in FIG. 8, the seal member 33 c is roughly composed of a flexible resin seal 34 and a leaf spring 35 that presses the seal 34 against the outer peripheral surface 30 f of the rotor 30. Has the same configuration.
[0049]
Also, between the shoe 70d of the case 70 and the vane 80b of the rotor 80, between the shoe 70a of the case 70 and the vane 80c of the rotor 80, between the shoe 70b of the case 70 and the vane 80d of the rotor 80, Between the shoe 70c and the vane 80e of the rotor 80, assist springs 37 respectively held by holders 36 are arranged. The assist spring 37 moves the rotor 80 with respect to the case 70 against a valve reaction force received in the retard direction (the direction indicated by the arrow Y in FIG. 7) from the camshaft 20 when the engine is stopped or started without hydraulic pressure. It is always biased in the angular direction (the direction of arrow X in FIG. 7).
[0050]
Inside the boss portion 80a of the rotor 80 and the camshaft 20, there is provided a first oil passage 38 which communicates with the advance hydraulic chambers 31b, 31c and 31d except for the advance hydraulic chamber 81a to supply and discharge hydraulic pressure. Except for the retard hydraulic pressure chamber 82a, there is provided a second hydraulic passage 39 communicating with the retard hydraulic pressure chambers 82b, 82c and 82d to supply and discharge the hydraulic pressure. As shown in FIG. 12, the first oil passage 38 and the second oil passage 39 are configured to receive supply and discharge of oil pressure by an oil pump 41 and an oil pan 42 via an OCV 40. In the second embodiment as well, similar to the first embodiment, no hydraulic pressure is supplied to the advance hydraulic chamber 81a and the retard hydraulic chamber 82a. A drain path (not shown) for communicating with the atmosphere and discharging oil is provided in each of the 81a and the retard hydraulic chamber 82a.
[0051]
Of the vanes of the rotor 80, a lock pin housing hole 90 having a bottom 90a in the axial direction of the valve timing adjustment device 60 is formed in the vane 80b sandwiched between the advance hydraulic chamber 81a and the retard hydraulic chamber 82a. ing. A lock pin (rotation restricting member) 91 in the lock pin storage hole 90 that restricts relative rotation between the case 70 and the rotor 80 when the engine is stopped or started, and permits the relative rotation when the engine is operating. Are slidably disposed along the axial direction of the lock pin storage hole 90. The lock pin 91 is roughly composed of a cylindrical pin main body 91a and a bottomed hole 91b formed in the bottom of the pin main body 91a along the axial direction. Note that the tip surface 91c of the pin body 91a is a curved surface that is convex with respect to an engagement hole described later for the same reason as the tip surface 51c of the pin body 51a in the first embodiment.
[0052]
A coil spring 54 that constantly urges the lock pin 91 in the arrow Z3 direction is disposed between the bottom 90a of the lock pin housing hole 90 and the bottomed hole 91b of the lock pin 91. In order to discharge back pressure generated at the rear portion of the lock pin 91 to the atmosphere when the lock pin 91 retreats in the direction of arrow Z4 against the urging force of the coil spring 54 at the bottom 90a of the lock pin storage hole 90. Back pressure drain passage 92 is formed.
[0053]
On the other hand, in the housing 11 as the first rotating body 10, it corresponds to the lock pin storage hole 90 formed in the vane 80b of the rotor 80 rotated to an intermediate position between the most advanced position and the most retarded position. At the position, a cylindrical engagement hole 93 extending in the axial direction of the valve timing adjustment device 60 and allowing the lock pin 91 to be inserted is formed. As shown in FIG. 9, the engaging hole 93 has a sliding groove 94 having a rectangular cross section which crosses the central portion of the engaging hole 93 in a direction perpendicular to the axial direction (radial direction of the housing 11). . The sliding groove 94 has an opening 94 a that opens toward the vane 80 b of the rotor 80 inside the housing 11 in the radial direction, and an opening 94 b that opens toward the third oil passage 56 provided in the camshaft 20. And a bottom 94c having a cross section smaller than the opening 94b on the radially outer side of the housing 11. In the sliding groove 94, a slider that receives the hydraulic pressure (unlocking hydraulic pressure) from the third oil passage 56 and slides in the direction of arrow Z <b> 2 to release the engagement of the lock pin 91 and close the engagement hole 93. (Closing member) 95 is provided.
[0054]
The slider 95 includes a rectangular head 95a having a rectangular cross section, a body 95b having a rectangular cross section having a longer axial length of the valve timing adjusting device 60 than the head 95a, and one surface of the body 95b on the rotor 80 side. And a slope 95c connecting the head 95a and one surface of the rotor 80 side, and a pressure receiving surface located on the camshaft 20 side of the body portion 95b and receiving the unlock hydraulic pressure from the third oil passage 56. , And a bottomed hole 95e formed in the upper surface of the head 95a. A coil spring 96 is provided between the bottomed hole 95e of the slider 95 and the bottom 94c of the slide groove 94 to constantly bias the slider 95 in the direction of arrow Z1.
[0055]
As shown in FIG. 8, a pressure drain passage 97 extending to the side of the housing 11 opposite to the rotor 80 is formed at the bottom 94c of the slide groove 94. When the slider 95 receives the unlocking hydraulic pressure from the third oil passage 56 on its bottom surface 95d and slides in the direction of arrow Z2 against the urging force of the coil spring 96, the pressure drain passage 97 This is for reducing the sliding resistance of the slider 95 by discharging air existing in the space between the portion 95a and the bottom 94c of the sliding groove 94 to the atmosphere.
[0056]
Next, the operation will be described.
First, when the engine is stopped, since the oil pump 41 shown in FIG. 12 is not driven, the oil in the valve timing adjustment device 1, the first oil passage 38 and the second oil passage 39 flows down to the oil pan 42. ing. At this time, since the opening / closing control valve 57 is closed and the hydraulic pressure is not supplied to the third oil passage 56, the unlocking oil pressure from the third oil passage 56 does not act on the bottom surface 95 of the slider 95. Therefore, as shown in FIGS. 9 and 10, the slider 95 slides in the direction of arrow Z1 by the urging force of the coil spring 96, and the bottom surface 95c is returned to the position of the opening surface 94b of the sliding groove 94. At this time, the bottom surface 95c of the slider 95 contacts the outer peripheral surface of the camshaft 20 where the third oil passage 56 opens. In this state, the head portion 95a of the valve timing adjusting device 60, which is shorter in the axial direction than the body portion 95b of the slider 95, is located in the engagement hole 93, and as shown in FIGS. Until the distal end surface 91c of the pin 91 contacts the side surface of the head 95a of the slider 95, the lock pin 91 that slides in the direction of arrow Z3 by the urging force of the coil spring 54 is allowed to enter the engagement hole 93. This restricts the relative rotation between the rotor 11 and the housing 11 or the case 70 as the first rotating body 10 (locked state).
[0057]
Next, immediately after the engine is started, it is immediately after the oil pump 41 shown in FIG. 12 starts to be driven, and since the oil temperature is low and the viscosity is high, the first rotating body and the second rotating body in the valve timing adjusting device 60 are changed. Since it is difficult to control the relative rotation position with respect to the target position, the opening / closing control valve 57 is closed, the slider 95 does not operate with respect to the lock pin 91, and the locked state is maintained.
[0058]
Next, when the engine warm-up operation is completed, the oil temperature increases and the viscosity decreases. At this stage, it is sufficiently possible to control the relative rotation position between the first rotating body and the second rotating body in the valve timing adjusting device 60 at the target position. Here, when there is a control command, the open / close control valve 57 shown in FIG. 12 is switched from the closed state to the open state for supplying the hydraulic pressure to the third oil passage 56, and the hydraulic pressure (lock Release hydraulic pressure) acts on the bottom surface 95d of the slider 95. As shown in FIG. 11, the slider 95 slides in the direction of the arrow Z2 due to the above hydraulic pressure. With the sliding of the slider 95, the tip end surface 91c of the lock pin 91 slides on the inclined portion 95c from the side surface of the head portion 95a of the slider 95 and comes into contact with the side surface of the trunk portion 95b. At this time, the lock pin 91 moves against the urging force of the coil spring 54 by a stroke corresponding to the dimensional difference in the axial length of the valve timing adjustment device 60 between the head 95a and the body 95b of the slider 95. It is returned in the Z4 direction. As a result, the lock pin 91 comes out of the engagement hole 93 (disengagement), so that relative rotation between the housing 11 or the case 70 as the first rotating body 10 and the rotor 80 is permitted (unlocked state). In this unlocked state, as long as the opening / closing control valve 57 is opened and the unlocking oil pressure is supplied through the third oil passage 56, the engagement hole 93 is closed by the slider 95 slid by the unlocking oil pressure. Will be retained.
[0059]
In addition, the third oil passage 56 includes advance-side hydraulic chambers 81b, 81c, and 81d in which hydraulic pressure changes due to a change in the relative angle between the case 70 and the rotor 80 during engine operation, and retard-side hydraulic chambers 82b, 82c. And 82d are independent of the first oil passage 38 and the second oil passage 39, so that a stable unlocking oil pressure is applied to the slider 95 without being affected by the fluctuation of the oil pressure. It is possible to continue.
[0060]
Further, when the slider 95 slides in the direction of the arrow Z2, air existing in the space between the head 95a of the slider 95 and the bottom 94c of the slide groove 94 is discharged to the atmosphere through the pressure drain path 97. The sliding resistance of the slider 95 is extremely small. Therefore, the slider 95 can slide quickly by application of the lock release hydraulic pressure to push the lock pin 91 out of the engagement hole 93 and close the engagement hole 93. Even if the unlocking hydraulic pressure applied to the slider 95 is the lowest hydraulic pressure during engine operation, the slider 95 can be slid against the urging force of the coil spring 54 to maintain the unlocked state, for example. The urging force of the coil spring 54 is set.
[0061]
Next, even during the operation of the engine, the lock pin 91 is constantly urged in the direction of arrow Z1 by the urging force of the coil spring 54, so that when the housing 11 as the first rotating body 10 and the rotor 80 rotate relative to each other, 11 on the side. On the other hand, since the engagement hole 93 is always closed by the slider 95, the re-fitting of the lock pin 91 into the engagement hole 93 is reliably prevented in any control state of the valve timing adjusting device 60. For example, the relative angle between the housing 11 or the case 70 as the first rotating body 10 and the case 70 and the rotor 80 is set such that the vane 80b of the rotor 80 is held at an intermediate position away from any of the shoes 70d and 70a of the case 70. When the controlled intermediate holding control is performed, the lock pin 91 slides in the vicinity of the engagement hole 93, but also in this case, the engagement hole 93 is closed by the slider 95. Therefore, re-fitting of the lock pin 91 to the engagement hole 93 is reliably prevented.
[0062]
When the engine is stopped once, the oil in the first oil passage 38 and the second oil passage 39 and the like goes down to the oil pan 42, and the air stays in each oil passage. In this state, when the engine is restarted, the oil supplied from the first oil passage 38 or the second oil passage 39 into the valve timing adjusting device 60 is bitten by air even at high temperature and low viscosity. Therefore, it is difficult to control the valve timing adjustment device 60 to a position substantially intermediate between the most advanced position and the most retarded position. Also in this case, by closing the open / close control valve 57, the supply of the hydraulic pressure for unlocking the slider 95 can be stopped, and the locked state can be maintained. Next, the air trapped in the oil is discharged, and then the opening / closing control valve 57 is opened to supply a hydraulic pressure for unlocking to the slider 95 to push out the lock pin 91 from the engagement hole 93 and to release the lock pin 91 from the engagement hole 93. The rotor 80 can be controlled at an arbitrary angle with respect to the housing 11 and the case 70 as one rotating body 10.
[0063]
As described above, according to the second embodiment, in addition to the various effects of the configuration in the first embodiment and the modifications thereof, the slider 95 is used as a closing member for closing the engagement hole 93 so that the shaft of the engagement hole 93 Since the slider 95 is slidable in a direction perpendicular to the direction, the slider 95 can be housed inside the engagement hole 93 formed along the axial direction of the valve timing adjustment device 60 in accordance with the sliding direction of the lock pin 91. Therefore, there is an effect that the axial size of the valve timing adjusting device 60 can be reduced. In the second embodiment, the slider 95 is configured to slide in the direction orthogonal to the axial direction of the engagement hole 93. However, the present invention is not limited to the orthogonal direction, and may be a direction intersecting the axial direction. Good.
[0064]
In the second embodiment, the valve timing adjusting device 60 is configured to include the slider that slides in a direction intersecting the axial direction of the engagement hole 93 that allows the lock pin 91 that slides in the axial direction. For example, a closing member that slides in the engaging hole 93 in the axial direction of the engaging hole 93 and has a configuration such as the slider 51 used in the first embodiment may be used.
[0065]
In the first and second embodiments, the so-called intermediate lock type valve timing adjusting devices 1 and 60 have been disclosed. However, in the present invention, the second rotating body is moved relative to the first rotating body at the most advanced position. The present invention is also applicable to a most advanced angle lock type that restricts rotation and a most retarded angle lock type that restricts rotation of the second rotating body with respect to the first rotating body at the most retarded position.
[0066]
In the first and second embodiments, the sliders 58 and 95 that slide by hydraulic pressure are used to close the engagement holes 59a and 93. However, the present invention is applicable to the use of the above-described closing member. The configuration is not limited, and any configuration may be adopted as long as it is means for preventing re-fitting of the lock pins 51 and 91 for restricting the relative rotation between the first rotating body 10 and the second rotating bodies 30 and 80. For example, other means such as a diaphragm whose film surface moves up and down in the engagement holes 59a and 93 by hydraulic pressure may be employed to close the engagement holes 59a and 93.
[0067]
Further, in the first and second embodiments, the supply and the stop of the unlock hydraulic pressure to the sliders 58 and 95 as the closing members are controlled by the opening and closing operation of the oil passage of the opening and closing control valve 57. However, immediately after the start of the engine, the hydraulic pressure application timing to be applied to the sliders 58 and 95 for pulling out the lock pins 51 and 91 from the hydraulic pressure supply timing required for the relative rotation between the first rotary body 10 and the second rotary bodies 30 and 80 is set. As a method of delaying and keeping the lock pins 51, 91 in the engagement holes 59a, 93 for a predetermined time, the length of the oil passage of the third oil passage 56 is increased, or a restriction is provided in the third oil passage 56. It is possible to appropriately adopt a method as needed.
[0068]
【The invention's effect】
As described above, according to the present invention, the first rotating body that rotates synchronously with the crankshaft of the internal combustion engine, and is fixed to the end surface of the intake or exhaust camshaft and can relatively rotate within the first rotating body by a predetermined angle. A second rotator disposed in the first rotator, and a relative position between the first rotator and the second rotator disposed at one of the second rotator and the first rotator. A rotation restricting member that restricts the relative rotation of the two rotators when it becomes, and a rotation restriction member formed on one of the first rotator and the second rotator and restricting the relative rotation of the two rotators. And an engagement hole that receives the engagement of the rotation restricting member and is closed after the relative rotation restriction of the two rotating bodies is released. Of the rotation restricting member into the engagement hole which is closed There is an effect that it is possible to reliably prevented.
[Brief description of the drawings]
FIG. 1 is an axial sectional view showing an internal configuration of a valve timing adjusting device according to Embodiment 1 of the present invention.
FIG. 2 is a radial sectional view taken along line II-II of FIG.
FIG. 3 is an enlarged radial sectional view showing a locked state between a first rotating body and a second rotating body in the valve timing adjusting device shown in FIGS. 1 and 2;
FIG. 4 is an enlarged radial cross-sectional view showing an unlocked state between a first rotating body and a second rotating body in the valve timing adjusting device shown in FIGS. 1 and 2;
5 is an enlarged radial sectional view showing a sliding state of a lock member when the valve timing adjusting device shown in FIG. 4 is unlocked.
FIG. 6 is a schematic diagram showing an overall configuration of a hydraulic supply / discharge system incorporating the valve timing adjusting device shown in FIGS. 1 to 5;
FIG. 7 is an axial sectional view showing an internal configuration of a valve timing adjusting device according to Embodiment 2 of the present invention.
FIG. 8 is a radial sectional view taken along line VIII-VIII in FIG. 7;
FIG. 9 is a schematic perspective view showing an enlarged main part of FIG. 8;
FIG. 10 is an enlarged radial sectional view showing a locked state between a first rotating body and a second rotating body in the valve timing adjusting device shown in FIGS. 7 to 9;
11 is an enlarged radial cross-sectional view showing an unlocked state between a first rotating body and a second rotating body in the valve timing adjusting device shown in FIGS. 7 to 9; FIG.
FIG. 12 is a schematic diagram showing the overall configuration of a hydraulic supply / discharge system incorporating the valve timing adjusting device shown in FIGS. 6 to 11;
[Explanation of symbols]
Reference Signs List 1 valve timing adjusting device, 10 first rotating body, 11 housing, 11a sprocket section, 12 case, 12a, 12b, 12c, 12d shoe, 13 cover, 14 bolt, 20 camshaft, 21 bolt, 30 rotor (second rotating Body), 30a boss portion, 30b, 30c, 30d, 30e vane, 30f outer peripheral surface, 31a, 31c, 31d advance-side hydraulic chamber, 31b advance-side pressure chamber, 32a retard-side pressure chamber, 32b, 32c, 32d Retard-side hydraulic chamber, 33a, 33b, 33c, 33d, 33e, 33f, 33g, 33h seal member, 34 seal, 35 leaf spring, 36 bolt, 37 assist spring, 38 first oil passage, 39 second oil passage, 40 OCV, 41 oil pump, 42 oil pan, 43 advance side drain path, 44 retard side drain path, 50 lock Pin storage hole, 51 lock pin (rotation restricting member), 51a pin main body, 51b bottomed hole, 51c tip surface, 52 bush, 52a bottomed hole, 52b back pressure drain portion, 53 shaft, 54 coil spring, 55 slider Storage hole, 55a bottom, 56 third oil passage, 57 open / close control valve, 58 slider (closing member), 59 bush, 59a engagement hole, 60 valve timing adjustment device, 65 sliding contact portion, 70 case, 70a, 70b, 70c, 70d Shoe, 80 rotor (second rotating body), 80a boss, 80b, 80c, 80d, 80e vane, 81a advance hydraulic chamber, 81b, 81c, 81d advance hydraulic chamber, 82a retard hydraulic Chamber, 82b, 82c, 82d Hydraulic chamber on retard side, 90 lock pin storage hole, 90a bottom, 91 lock pin (rotation restricting member), 91a Pin body, 91b bottomed hole, 91c tip surface, 92 back pressure drain passage, 93 engagement hole, 94 sliding groove, 94a, 94b opening, 94c bottom, 95 slider (closing member), 95a head, 95b trunk Part, 95c inclined part, 95d bottom surface, 95e bottomed hole, 96 coil spring, 97 pressure drain path.

Claims (10)

A first rotator that rotates synchronously with a crankshaft of the internal combustion engine, a second rotator fixed to an end surface of an intake or exhaust camshaft and disposed relatively rotatable within the first rotator by a predetermined angle; When the relative position between the first rotator and the second rotator reaches a predetermined position, the relative rotation of the two rotators is provided on one of the second rotator and the first rotator. A rotation restricting member for restricting movement, formed on one of the other of the first rotating body and the second rotating body, and receiving engagement of the rotation restricting member when restricting relative rotation of the two rotating bodies; A valve timing adjusting device comprising: an engagement hole that is closed after the relative rotation of the two rotating bodies is released. The valve timing adjusting device according to claim 1, further comprising a closing member that closes the engagement hole. The valve timing adjusting device according to claim 2, wherein the closing member is a member that slides in the axial direction of the engagement hole. 3. The valve timing adjusting device according to claim 2, wherein the closing member is a member that slides in a direction intersecting the axial direction of the engagement hole. The valve timing adjusting device according to claim 2, wherein the closing member is slidable by hydraulic pressure. 6. The valve timing according to claim 5, wherein an oil passage for supplying a hydraulic pressure for operating the closing member is provided independently of an oil passage for supplying a hydraulic pressure for relative rotation between the first rotating body and the second rotating body. Adjustment device. 7. The valve timing adjusting device according to claim 6, wherein a valve for controlling supply and stop of the operating hydraulic pressure of the closing member is provided in the hydraulic pressure supply oil passage for operating the closing member. 6. The valve timing adjusting device according to claim 5, wherein the closing member is capable of releasing the regulation of the relative rotation between the first rotating body and the second rotating body even at the lowest oil pressure during the operation of the internal combustion engine. 9. The engagement hole according to claim 1, wherein the engagement hole is provided between a most advanced position and a most retarded position, which are relative positions of the second rotator with respect to the first rotator. Item 2. The valve timing adjusting device according to Item 1. A first rotator that rotates synchronously with a crankshaft of the internal combustion engine, a second rotator fixed to an end surface of an intake or exhaust camshaft and disposed relatively rotatable within the first rotator by a predetermined angle; When the relative position between the first rotator and the second rotator reaches a predetermined position, the relative rotation of the two rotators is provided on one of the second rotator and the first rotator. A rotation restricting member that restricts movement, and is formed on one of the other of the first rotator and the second rotator and receives the engagement of the rotation restrictor when the relative rotation of the two rotators is restricted. A valve timing comprising: an engagement hole; and a closing member that pushes the rotation restricting member out of the engagement hole to release the engagement of the rotation restriction member and closes the engagement hole. Adjustment device.

Images