JP2001050019A - Valve timing adjuster for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable a plunger to follow the sharp advance of the vane body caused by reaction force of torque from an engine valve as well as to improve control response and level of quietness. SOLUTION: A tip of plunger 14 is abutted by pressing to a separation wall portion 13 of a housing 2 via a shoe 67, by mounting the plunger 14 slidably to a vane body 4 connected to a cam shaft and introducing pressure in an advance angle side hydraulic chamber 27 into a pressure chamber 47 in the plunger 14 when advance angle side rotation is controlled. The tip of the shoe 14 is made to always contact the separation wall portion 13 in a plane by mounting the shoe 67 at the tip of the plunger so that the neck of the shoe is swingable. When the plane contact portion of the shoe 67 is trying to separate from the separation wall portion 13, the separation is inhibited by pressure decrease in the surrounding area and viscosity of the operation oil. Therefore, the plunger 14 is made to reliably work following the rotation of the vane body 4.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a so-called vane type valve timing control device for varying the opening / closing timing of an intake side or exhaust side engine valve of an internal combustion engine in accordance with an operating condition.

[0002]

2. Description of the Related Art As a conventional valve timing control device, for example, one disclosed in Japanese Patent Application Laid-Open No. 8-121123 is known.

[0003] In brief, this valve timing control device is configured such that a cylindrical housing is integrally mounted on a timing pulley which is a driving rotary member which is driven to rotate by a crankshaft of an engine, and a camshaft is provided in the housing. A vane body fixed to an end of the housing is rotatably housed, and a substantially trapezoidal partition wall portion protruding inward in the radial direction is formed on the inner peripheral surface of the housing. An advance-side hydraulic chamber and a retard-side hydraulic chamber are defined between the vane blades. The hydraulic pressure is relatively supplied to and discharged from each of the hydraulic chambers on the advance side and the retard side according to the engine operating state, and the drive hydraulic pressure causes the vane body to rotate forward and reverse, thereby causing the timing pulley and the camshaft to rotate. By changing the relative rotation phase, the opening and closing timing of the intake valve is made variable.

It is well known that the camshaft generates positive and negative (forward rotation, reverse rotation) rotation fluctuation torque (alternating torque) due to the spring force of the valve spring during operation of the engine. However, when the rotation fluctuation torque acts during the rotation driving of the vane body to the advance side or the retard side (during forward / reverse rotation control), the driving oil pressure of the vane body becomes a reaction force of the rotation fluctuation torque. When the vane loses and is pushed back, the rotational behavior of the vane becomes unstable. That is, when the vane body rotates, for example, to the advance side,
The drive oil pressure supplied to the advance side hydraulic chamber loses the reaction force of the positive fluctuating torque, and the forward and reverse rotations (forward and backward) to the advance side and the retard side as shown by the broken line (a) in FIG. Rotate to the advance side while repeating. Therefore, the camshaft also rotates forward,
Since the rotation relative to the timing pulley is performed while repeating the reverse rotation, the responsiveness of the valve timing control, which is the opening / closing timing control of the engine valve, is reduced.

[0005] In particular, in the low-medium rotation region of the engine where the supply oil pressure is low, it is desired to improve the responsiveness of the device when changing the valve timing from the retard control to the advance control.

Therefore, a pilot check valve comprising a check valve and a pilot valve is provided inside the vane body as in the technique described in Japanese Patent Application Laid-Open No. 8-121123. A device has been devised which restricts the reverse flow of the drive hydraulic pressure supplied to the hydraulic chamber on the side or the retard side into the oil passage to prevent the vane from reversing due to fluctuating torque.

[0007]

However, in this conventional example, although the backflow of the driving oil pressure in each hydraulic chamber is prevented by using a pilot check valve, the pilot check valve is not provided in each hydraulic chamber. However, there is a possibility that the operation accuracy may be reduced due to a decrease in the holding capacity of the hydraulic pressure in the hydraulic chamber. In other words, a small gap is formed between the housing and the vane body that slides and rotates inside the housing, while a small gap is formed between the housing and the adjacent hydraulic chambers in order to ensure good sliding rotation of the vane body. Causes a large differential pressure. For this reason, the hydraulic pressure supplied to one hydraulic chamber may leak through the minute gap into the other hydraulic chamber. As a result, the check function of the pilot check valve (the function of closing the hydraulic chamber on the side receiving the torque reaction force from the engine valve) is reduced, and the return of the vane body caused by the torque reaction force of the engine valve is effectively prevented. Could not be stopped.

In addition, the seal member for maintaining the oil tightness in the housing is deteriorated by long-term use.
Even if a hydraulic pressure leaks from each hydraulic chamber due to this deterioration, the check function of the pilot check valve may be reduced.

As a result, the same technical problem as before, such as a decrease in the control response of the valve timing, is brought about.

Therefore, the present applicant has devised a valve timing control device capable of solving such a problem, and has filed Japanese Patent Application No. Hei.
No. 120259 (filed on April 30, 1998).

[0011] The apparatus according to the earlier application is such that a plunger is slidably attached to one of a vane body attached to one of a camshaft and a driving rotary body, and a tubular member attached to the other side. When controlling the forward / reverse rotation of the vane body with respect to the cylindrical member, the distal end of the plunger is pressed against the other side (opposite member facing the other side) of the vane body and the cylindrical member, so that the engine valve is controlled. The basic structure restricts return of the vane body due to torque reaction.

In this application, as an example of the device, a plunger is slidably housed in a mounting hole of a vane body, and a pressure chamber in the plunger is provided with a check valve when the vane body is controlled to rotate on the advance side. And a low-pressure passage (low-pressure advance hydraulic chamber) through a pressure control spool disposed in the plunger when the vane body is controlled to rotate on the retard side. Are disclosed.

In this device, during the retard rotation control in which the retard hydraulic chamber becomes high in pressure, the pressure chamber communicates with the low-pressure advance hydraulic chamber by operating the pressure control spool to freely move the plunger back and forth. On the other hand, during the rotation control on the advance side, the pressure control spool closes the discharge passage portion, and the high-pressure hydraulic oil in the hydraulic chamber on the advance side opens the check valve and is introduced into the pressure chamber. The discharge of hydraulic oil from the chamber is prevented by the function of the check valve. Therefore,
During advance rotation control in which a positive torque reaction force is transmitted from the engine valve to the vane body, the plunger acts on the plunger to restrict return of the vane body.

In this valve timing control device, a spring for urging the plunger in the projecting direction is interposed between the bottom of the mounting hole of the vane body and the plunger. Even if the plunger receives a fluctuating torque and suddenly rotates in the advance direction, the plunger receives the urging force of the spring and immediately follows this, thereby maintaining the contact between the plunger and the housing. It has become.

In this valve timing control device, it is difficult to set a spring interposed between the mounting hole and the plunger. If the setting of the spring force of the spring is too small, the vane body is controlled during the advance-side rotation control. When the plunger rotates rapidly, the tip of the plunger separates from the housing, and during that separation, the projecting force of the plunger cannot be obtained, and the control responsiveness of the valve timing is reduced.
When the tip of the plunger again contacts the housing, a collision sound is generated. Conversely, if the biasing force of the spring is too large, a large oil pressure against the force of the spring must be used for the retard rotation control, resulting in a large power loss.

Therefore, the present invention enables the plunger to reliably follow the rapid advance of the vane body due to the torque reaction force from the engine valve, and does not cause a problem such as an increase in power loss or the like. It is an object of the present invention to provide a valve timing control device for an internal combustion engine capable of improving the performance and quietness.

[0017]

Means for Solving the Problems As means for solving the above-mentioned problems, the invention described in claim 1 is for driving a rotating rotary body driven by a crankshaft of an engine and operating an engine valve on the outer periphery. A camshaft that has a driving cam and is mounted so that the driving rotator can rotate relative to each other if necessary, and that receives power from the driving rotator and rotates in a driven manner; and a camshaft and the driving rotator And a vane body having at least one blade portion radially extending radially outward from a rotation center portion and a member on the other side of the camshaft and the driving rotary member. And a plurality of partition walls extending on the inner peripheral surface in the direction of the center of rotation of the vane body. The plurality of partition walls advance to both sides in the rotation direction of each blade of the vane body. A tubular member forming a side hydraulic chamber and a retard side hydraulic chamber; and a hydraulic member that sucks and discharges a hydraulic pressure relatively to the advance side hydraulic chamber and the retard side hydraulic chamber to reverse the vane body relative to the cylindrical member. A hydraulic circuit to rotate, and a regulating mechanism that regulates return of the vane body due to torque reaction force from the engine valve when rotating the vane body in one direction with respect to the cylindrical member,
The regulating mechanism is configured to press the distal end side of a plunger slidably attached to one of the vane body and the cylindrical member to the other member of the vane body and the cylindrical member. In the valve timing control device for an internal combustion engine, the pressing portion at the tip of the plunger is brought into surface contact with the member on the other side.

In the case of the present invention, since the pressing portion at the tip of the plunger comes into surface contact with the vane body and the member on the other side of the cylindrical member, the hydraulic oil entering the surface contact portion and its surroundings The hydraulic oil in the region functions to prevent separation between the pressing portion at the tip of the plunger and the member on the other side. That is,
When the vane body is rapidly displaced in the advancing direction due to the torque reaction force from the engine valve during the rotation control of the vane body, the member on the other side tries to separate from the pressing portion at the tip of the plunger, At this time, separation of the plunger from the member on the other side is prevented by the pressure drop generated around the pressing portion and the viscosity of the hydraulic oil. In addition, since the pressing portion at the tip of the plunger and the member on the other side are in surface contact, the surface pressure between the two is reduced, and the member on the other side is stably supported by the plunger.

According to a second aspect of the present invention, in the first aspect of the present invention, a contact surface between the pressing portion at the tip of the plunger and the pressing portion of the other member is formed flat. I did it.

In the case of the present invention, since the two are in flat contact with each other, the support of the member on the other side by the plunger is stabilized, and the machining of the contact surface is also facilitated.

According to a third aspect of the present invention, in the second aspect of the present invention, a pressing member is swingably attached to the tip of the plunger, and the pressing member is brought into planar contact with the other member. I did it.

In the case of the present invention, when the relative angle between the plunger and the other member changes with the relative rotation of the tubular member and the vane body, the pressing member swings according to the change in the angle. The planar contact between the pressing member and the other member is maintained.

According to a fourth aspect of the present invention, in the first aspect of the present invention, the tip of the plunger is swung by a pressing member in contact with the member on the other side via an elastic member. It was movably mounted.

In the case of the present invention, since the force of the elastic member acts to maintain the angle of the pressing member at the initial angle, the pressing member always flexibly follows the angle change of the other member. As a result, the pressing member comes into stable contact with the other member.

[0025]

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

First, a first embodiment shown in FIGS. 1 to 10 will be described. Although the valve ting control device of this embodiment is applied to the intake valve side of the internal combustion engine, it can be applied to the exhaust valve side in a similar manner.

As shown in FIG. 2, the valve timing control device includes a timing sprocket 1 as a driving rotating body which is driven to rotate by a crankshaft (not shown) of an engine via a timing chain made of synthetic resin, and the timing sprocket. 1, a housing 2 as a tubular member integrally attached to a front end of the camshaft 3, a camshaft 3 assembled so as to be able to rotate relative to the timing sprocket 1 if necessary, and an end of the camshaft 3. A vane body 4 fixed to the housing 2 and rotatably accommodated in the housing 2, a hydraulic circuit 5 for rotating the vane body 4 forward and reverse by hydraulic pressure, and a positive rotation fluctuation torque acting on the camshaft 3 ( A regulating mechanism 6 for regulating the return of the vane body 4 due to the torque in the direction opposite to the rotation direction of the camshaft 3). That.

As shown in FIGS. 2 and 4, the timing sprocket 1 has teeth 1a on its outer periphery with which the timing chain meshes, and its front end has a front cover 8 and a rear cover 9 on the front and rear end surfaces of a cylindrical body 7. Is fixed by bolts 10. In addition, a fitting hole 12 having a stepped diameter into which a sleeve 11 to be described later is fitted is formed at a central position inside the timing sprocket 1 so as to penetrate therethrough.

The cylindrical body 7 of the housing 2 has four trapezoidal partition walls 13 projecting from the inner peripheral surface thereof at 90 ° intervals, and one of the partition walls 13 has a regulating mechanism 6. A flat surface 13a with which the tip of the plunger 14 abuts is provided. A holding groove 15 is formed in the center of the tip of each partition 13 along the axial direction, and a sealing member 16 and a leaf spring 17 for pressing the sealing member 16 inward are formed in the holding groove 15.
Is housed.

On the other hand, the camshaft 3 is rotatably supported at the upper end of a cylinder head 18 via a cam bearing 19, and a drive cam (not shown) for opening an intake valve via a valve lifter at a predetermined position on the outer peripheral surface. Are integrally provided, and a flange portion 20 is integrally provided at the front end. The vane body 4 accommodated in the housing 2 is fixed to the flange 20 together with the sleeve 11 by fixing bolts 21.

The vane body 4 has the fixing bolt 2
1 is provided with an annular rotor portion 22 through which the blade 1 is inserted, and four blade portions 23 radially projecting from the outer peripheral surface of the rotor portion 22 at 90 ° intervals. 3 of the four blades 23
One is formed in a rectangular shape having the same thickness, and the other is formed in a rectangular shape thicker than these. Each of these blade portions 23 is disposed between adjacent partition portions 13, 13 of the housing 2. I have. A holding groove 24 is formed at the tip of each blade 23 along the axial direction. The holding groove 24 has a sealing member 25 that is in close contact with the inner peripheral surface of the housing 2, and the sealing member 25 has Pressing leaf springs 26 are fitted and held, respectively. A space between the side surface on one side of each blade portion 23 of the vane body 4 and the partition wall portion 13 facing the partition wall portion 13 is an advance-side hydraulic chamber 27, and the other side surface of each blade portion 23 and the partition wall portion 13 facing the same. The interval is between the retard hydraulic pressure chambers 28. Therefore, in this device, the advance side hydraulic chamber 27
And a pair of retard hydraulic chambers 28 are provided in total.

Further, as shown in FIG. 2, the hydraulic circuit 5 sucks and discharges a hydraulic pressure to and from the advance hydraulic chamber 27, and sucks and discharges a hydraulic pressure to the retard hydraulic chamber 28. There are two hydraulic passages, a second hydraulic passage 30. A supply passage 31 and a drain passage 32 are connected to the two hydraulic passages 29, 30 via electromagnetic switching valves 33 for passage switching, respectively. An oil pump 35 for feeding oil in an oil pan 34 is provided in the supply passage 31, and an end of the drain passage 32 communicates with the oil pan 34.

The first hydraulic passage 29 is formed in the cylinder head 18 with a first hydraulic passage 29 formed inside the axis of the camshaft 3.
A passage portion 36, a first oil passage 38 branched and formed in the head portion 37 through the inner axial direction of the fixing bolt 21 and communicating with the first passage portion 36, a small-diameter outer peripheral surface of the head portion 37 and a vane An annular oil chamber 40 formed between the inner peripheral surface of the bolt insertion hole 39 of the body 4 and communicating with the first oil passage 38; and an annular oil chamber 40 formed substantially radially in the rotor portion 22 of the vane body 4. And four branch passages 41 communicating the advance hydraulic chambers 27 with each other.

On the other hand, the second hydraulic passage 30 is formed in a crank shape from the sleeve 11 to the rear cover 9 by a second passage portion 42 formed inside the cylinder head 18 and one side inside the camshaft 3. The second passage portion 42 and a second oil passage 43 that communicates with each of the retard hydraulic pressure chambers 28 are formed.

The electromagnetic switching valve 33 has a four-port
It is a position type, in which the hydraulic passages 29, 30 and the supply passage 31 and the drain passage 32 are relatively switched by the displacement of an internal valve body.
The displacement of the valve body is controlled by the control signal from the control unit 4. The controller 44 detects a current operation state by a signal from a crank angle sensor for detecting an engine speed or an air flow meter for detecting an intake air amount, and controls the timing sprocket 1 based on signals from the crank angle sensor and the cam angle sensor. The relative rotation position with respect to the camshaft 3 is detected.

As shown in FIGS. 1 and 5, the restricting mechanism 6 has a mounting hole 45 formed in one of the blade portions 23 of the vane body 4 having a large thickness so as to face the advance hydraulic chamber 27. Plunger support block 4 press-fitted and fixed in this mounting hole 45.
6, the plunger 14 slidably fitted on the support block 46, and the plunger 14
A check valve 48 that permits only the flow of hydraulic oil into the pressure chamber 47 in the inside;
And a pressure control spool 51 that appropriately opens and closes a connection path 50 that communicates with the pump 9 by hydraulic pressure.

The plunger support block 46 is formed in a bottomed cylindrical shape having a plunger receiving hole 52 opening to the advance hydraulic pressure chamber 27 and a thick bottom wall 53. , A spool receiving hole 54 that opens on the opposite side to the plunger receiving hole 52 is formed, and the connection path 50 is connected to the plunger receiving hole 52 through the spool receiving hole 54.
And the low pressure passage 49 is communicated with the bottom of the base.
The low pressure passage 49 is always in communication with a drain passage (not shown) in the housing 2.

The pressure control spool 51 is accommodated in the spool accommodation hole 54 together with the spring 57. The pressure control spool 51 is formed in a cylindrical shape with a bottom and is urged by the spring 57 in a direction in which the connection path 50 is always opened.
4, the connection path 50 is opened and closed by its peripheral wall. In the bottom wall of the plunger support block 46, a pressure introduction path 59 formed in the blade section 23 of the vane body 4 and a communication path 60 communicating the bottom in the spool receiving hole 54 are formed. The passage 59 is connected to the annular oil chamber 40, which is the upstream passage of the advance hydraulic chamber 27. For this reason, the pressure of the annular oil chamber 40 acts on the end face of the pressure control spool 51 via the communication path 60 and the pressure introduction path 59. Therefore, when the annular oil chamber 40 is in a low pressure state, the pressure control spool 51 receives the force of the spring 57 to open the connection path 50. It is displaced in a direction opposing the force, thereby closing the connection 50.

On the other hand, as shown in FIG. 5, the plunger 14 has a concave portion 6 at its base end accommodated in the support block 46.
1 is formed, and a substantially spherical head portion 64 is formed at the distal end portion via a tapered portion 62 and a neck portion 63.
The pressure chamber 47 is formed between the concave portion 61 of the plunger 14 and the bottom of the plunger receiving hole 52. A substantially T-shaped introduction path 65 is formed in the plunger 14 and communicates the pressure chamber 47 with the outer peripheral surface of the neck 63. Through this introduction path 65, hydraulic oil in the advance hydraulic chamber 27 is supplied to the pressure chamber 47. 47
Is to be introduced within. The neck 63 is
The plunger 14 always faces the advance side hydraulic chamber 27 irrespective of the advance / retreat position of the plunger 14.

Further, a spring 66 for constantly urging the plunger 14 in the direction of the plane 13 a of the partition wall 13 is provided in the concave portion 61, and the hydraulic oil in the introduction passage 65 is circulated from the advance hydraulic chamber 27. A check valve 48 that restricts only to the direction toward the pressure chamber 47 is provided.

The head 64 of the plunger 14
A shoe 67 as a pressing member made of an iron-based material having high wear resistance, such as S, SCM, or SCr, is swingably mounted. Specifically, a spherical concave portion 68 is formed on the back surface of the shoe 67, and the head 64 of the plunger 14 is slidably fitted into the concave portion 68, and in this state, the peripheral edge of the concave portion 68 comes off. It is crimped for stopping. And the tip of the shoe 67 is formed flat,
The flattened distal end surface 67a is always in contact with the flat surface 13a of the partition wall 13.

Hereinafter, the operation of the present embodiment will be described.

At the time of engine start and idling operation,
The electromagnetic switching valve 3 is controlled by a control signal from the controller 44.
6, the supply passage 31 communicates with the second hydraulic passage 30, and the drain passage 32 communicates with the first hydraulic passage 29, as shown in FIG. Therefore, the hydraulic pressure pumped from the oil pump 35 is supplied to the retard hydraulic chamber 28 through the second hydraulic passage 30, and the advanced hydraulic chamber 27 is maintained at the low pressure state as when the engine is stopped. Thereby, the blade portion 23 of the vane body 4 is maintained in a state where it is maximally displaced in the direction of the advance side hydraulic chamber 27 (in the retard direction) as shown in FIGS.

Accordingly, the relative rotation position between the timing sprocket 1 and the camshaft 3 is held on the retard side,
The opening / closing timing of the intake valve is controlled to the retard side. This allows
The combustion efficiency of the engine is improved, so that the engine rotation can be stabilized and the fuel efficiency can be improved.

Here, as shown in FIG. 1, the regulating mechanism 6 has a low hydraulic pressure (drain pressure) acting on the end face of the pressure control spool 51 through the pressure introducing passage 59.
The pressure control spool 51 opens the connection path 50 while being displaced toward the bottom of the housing hole 54 by the force of the spring 57, and the pressure chamber 47 in the plunger 14 is maintained at a low pressure state. Therefore, at this time, the advance-side hydraulic chamber 2
Combined with the low pressure (drain pressure) of 7, the plunger 14 causes the shoe 67 to contact the flat surface 13 a of the partition wall 13 only by the urging force of the spring 66.

Thereafter, when the vehicle starts and the engine shifts from the low-speed low-load region to the normal operation in the medium-speed medium load region, the electromagnetic switching valve 33 is operated by the control signal from the controller 44 as shown in FIG. Then, the supply passage 31 and the first hydraulic passage 29 are communicated with each other, and the drain passage 32 and the second hydraulic passage 30 are communicated with each other. As a result, the oil pressure in the retard hydraulic chamber 28 is returned from the drain passage 32 to the oil pan 34 through the second hydraulic passage 30 and the pressure in the retard hydraulic chamber 28 becomes low. Is introduced into the advance-side hydraulic chamber 27 through the first hydraulic passage 29, and the blade portion 23 of the vane body 4 is moved toward the retard-side hydraulic chamber 28 (advance angle) due to a difference between these pressures. Direction).

Therefore, the timing sprocket 1 and the camshaft 3 relatively rotate to the other side, and the opening / closing timing of the intake valve is controlled to the advanced side. The engine output is thereby improved.

When the regulating mechanism 6 switches from the retard side to the advance side, as described above, the first hydraulic passage 29
The high-pressure oil is introduced into the advance-side hydraulic chamber 27 through the oil passage, and the high-pressure of the first hydraulic passage 29 acts on the end face of the pressure control spool 51 from the annular oil chamber 40 through the pressure introduction passage 59, so that the advance-side hydraulic The high-pressure oil in the chamber 27 is introduced into the pressure chamber 47 by opening the check valve 48 through the introduction path 65 of the plunger 14, and at this time, the pressure control spool 51 receives the oil pressure in the annular oil chamber 40 and changes the connection path 50. Close. For this reason, the plunger 14 advances by an amount corresponding to the amount of the rotation stroke as shown in FIGS. 8 and 9 sequentially with the clockwise rotation of the vane body 4 from the position shown in FIG. The shoe 67 at the tip of 14 is kept in contact with the partition wall 13.

When the vane body 4 rotates relative to the housing 2 in this manner, the angle formed between the partition wall 13 and the plunger 14 gradually changes in accordance with the rotation. 13 planes 1
The oscillating swing is performed with respect to the plunger 14 while being in sliding contact with 3a. Therefore, the front end surface 67a of the shoe 67 is
The plane contact with the third plane 13a is maintained.

When the rotation of the vane body 4 is controlled, a positive fluctuation torque of the camshaft 3 is transmitted to the vane body 4. The fluctuation torque causes the blade section 23 to temporarily rotate in the counterclockwise direction. Then, at this time, the pressure in the pressure chamber 47 increases and the check valve 48 closes the introduction path 62, so that the plunger 14 is restricted from retreating by the hydraulic pressure of the pressure chamber 47 closed by the check valve 48. Accordingly, the regulating mechanism 6 applies a so-called projecting force to the counterclockwise rotation of the vane body 4 due to the positive fluctuation torque, and regulates the counterclockwise rotation of the vane body 4 by the projecting force. Therefore, as shown by the solid line (b) in FIG. 10, the vane body 4 is reliably restricted from rotating counterclockwise during rotation from the most retarded side to the most advanced side.
With the urging force of No. 6, the motor rotates quickly in the clockwise direction (advance angle side).

Accordingly, the relative rotation speed of the timing sprocket 1 and the camshaft 3 to the advance side is increased, and the control response of the valve timing is improved.

On the other hand, the negative rotation fluctuation torque acting on the camshaft 3 at this time acts as an assisting force for rotating the vane body 4 to the advance side, thereby further improving the control response of the valve timing.

Here, when the assisting force due to the negative rotation fluctuation torque is large, the advance of the vane body 4 is sharp and the follow-up of the plunger 14 by the urging force of the spring 66 is almost delayed. In the timing control device, the following delay is avoided by bringing the shoe 67 at the tip of the plunger 14 into contact with the partition wall 13 on the surface. In other words, in the case of this device, when the vane body 4 and the housing 2 rotate relative to each other, the shoe 67 swings and swings accordingly, and the planar contact between the shoe 67 and the partition 13 is maintained. The hydraulic oil that has entered between the parts and the hydraulic oil in the peripheral area causes a pressure drop when the shoe 67 is about to separate from the partition wall 13, and this pressure drop, together with the viscosity of the hydraulic oil, causes the shoe 67 to drop.
And the partition 13 are prevented from being separated from each other.

Accordingly, the shoe 67 is maintained in a constant contact state with the partition 13, thereby deteriorating the valve timing control responsiveness due to a delay in following the plunger 14 and noise due to the collision between the shoe 67 and the partition 13. The problem such as occurrence of the problem does not occur.

Further, when the engine operation shifts from this state to the high-speed high-load region, the electromagnetic switching valve 33 operates to supply the supply passage 31, the second hydraulic passage 30, and the drain passage 32 in the same manner as in the idling operation. And the first hydraulic passage 29 communicate with each other, so that the advance hydraulic chamber 27 is set to the low pressure and the retard hydraulic chamber 2.
1 and 3, the vane body 4 rotates counterclockwise as shown in FIG. 1 and FIG. 3 to relatively rotate the timing sprocket 1 and the camshaft 3 to one side. Change the opening / closing timing to the retard side. As a result, the closing timing of the intake valve is delayed, and the intake charging efficiency is improved.

At this time, since the pressure introducing passage 59 becomes low pressure and the pressure control spool 51 opens the connecting passage 50 at this time, the operating oil in the pressure chamber 47 is discharged to the low-pressure passage 49 through the connecting passage 50. You. As a result, the projecting tension of the plunger 14 is released, the vane body 4 immediately rotates counterclockwise, and the opening / closing timing of the intake valve is immediately changed to the retard side. Also at this time, the shoe 67 at the tip of the plunger 14 swings with the rotation of the vane body 4, thereby maintaining the flat contact with the partition 13.

In this valve timing control device, since the tip of the plunger 14 and the partition 13 are in flat contact with each other via the shoe 67, a large load is applied from the plunger 14 when a torque reaction force is input from the engine valve. Can be greatly reduced. Therefore, according to this device, wear of the partition 13 is less likely to occur, and the housing 2 including the partition 13 is hardly worn.
It is possible to form the entire body from a lightweight material such as an aluminum material or a resin material.

Further, in this device, since the tip of the plunger 14 is brought into planar contact with the partition 13 via the shoe 67, the partition 13 is swung due to rotation of the vane body 4 or engine vibration. Can be stably and reliably suppressed by the plunger 14. Further, since the contact surface between the partition wall portion 13 and the shoe 67 is made flat, the surface can be processed easily and with high accuracy, and the manufacturing cost can be reduced.

Next, a second embodiment of the present invention shown in FIG. 11 will be described. In the following description of the embodiment, the same portions as those of the first embodiment shown in FIGS. 1 to 10 are denoted by the same reference numerals, and the description of the overlapping portions will be omitted.

The device of this embodiment is similar to the first embodiment, except that a shoe 67 having a flat tip surface is attached to the tip of the plunger 14 so as to be swingable.
A spring 70 as an elastic member is interposed between a caulking flange 68a formed on the periphery of the concave portion 68 of the shoe 67 and the back surface of the head 64 of the plunger 14, and the spring 70 allows the shoe 67 to take an initial posture with respect to the plunger 14. Is being urged to maintain.

Accordingly, in the case of this embodiment, the same effect as that of the first embodiment can be obtained, and in addition, since the shoe 67 always receives the urging force by the spring 70 to return to the initial position, the vane When the angular change between the plunger 14 and the partition 13 due to the relative rotation of the body 4 occurs, the swing is swung to imitate the flat surface 13a of the partition 13 immediately and flexibly in response to this change. . When the shoe 67 is tilted from the initial position, the reaction force of the spring 70 acts and the flat surface 13a of the
, The contact stability between the shoe 67 and the partition 13 is enhanced, and rattling noise between the two is less likely to occur.

In the second embodiment, the shoes 67
Was attached to the plunger 14 via the spring 70, but as in the third embodiment shown in FIG.
Through the elastic material 80 such as rubber or resin.
4 may be connected to the tip. In the case of this embodiment, the elastic material 80 is directly adhered to the tip of the plunger 114 and the back of the shoe 167, and is engaged with the plunger 114 by a projection 81 provided at the center of the tip of the plunger 114. ing. Therefore, when the vane 4 is relatively rotated, the elastic material 80 is deformed to allow the swing of the shoe 167 to swing. This swing is mainly centered on the projection 81 at the tip of the plunger 114, and Plane contact between the tip end surface of the partition 167 and the partition wall 13 is thereby stably maintained.

In the case of this embodiment, the reaction force of the elastic material 80 acts not only in the direction of restoring the posture of the shoe 167 but also in the direction of directly pressing the shoe 167 against the partition wall 13. Is the partition wall 1
In addition, when the load is suddenly transmitted between the plunger 114 and the partition 13, the impact can be reliably cushioned by the elastic material 80.

In each of the first and second embodiments, a spherical head 64 is provided at the tip of the plunger 14.
The concave portion 68 on the rear surface of the shoe 67 is fitted to the head portion 64. However, as in the fourth embodiment shown in FIG. On the side, a bulging portion 91 slidably engaged with the concave portion 90 may be formed. In the case of this embodiment, a caulking flange 92 is provided on the periphery of the concave portion 90 of the plunger 214, and the caulking flange 92 is provided.
The shoe 267 is prevented from coming off from the plunger 214 by making the tip of the shoe face the constriction 93 of the bulging portion 91.

The device of this embodiment can basically obtain the same operation and effects as those of the first embodiment. However, in order to avoid interference between the shoe 67 and the plunger 14 as in the first embodiment, There is no need to provide the taper portion 62 on the tapered portion 14, and there is an advantage that processing is facilitated. Further, since the bulging portion 91 of the shoe 267 is housed in the recess 90 of the plunger 214,
There is also an advantage that the outer diameter of 7 can be easily reduced.

[0066]

As described above, the invention according to claim 1 is
An operation that acts on the contact portion and its peripheral region by bringing the pressing contact portion at the tip of the plunger into surface contact with the other member (the member on the side where the plunger is not attached) of the vane body and the cylindrical member. Since the separation between the pressing portion at the tip of the plunger and the other member can be prevented by the suction action of the oil, the plunger reliably follows the rapid advance of the vane body due to the torque reaction force from the engine valve. As a result, control responsiveness of the valve timing is improved, and collision noise between the pressing portion at the tip of the plunger and the member on the other side is eliminated, thereby improving quietness.

Further, according to the present invention, since the contact pressure between the pressing portion at the tip of the plunger and the member on the other side is reduced,
Wear and scratches between these two contact parts are less likely to occur,
It is possible to use a lightweight material having low hardness such as an aluminum material or a resin material.

Further, in the present invention, since the member on the other side is stably supported by the plunger via the surface contact portion, the member between the vane body and the cylindrical member due to vibration or the like input from the outside is provided. There is also an advantage that the fluctuation of the data can be surely suppressed.

According to the second aspect of the present invention, since the contact surface between the pressing portion at the tip of the plunger and the pressing portion of the other side member is formed to be flat, the other side of the plunger is used. Since the support of the member is more stable and the processing of the contact surface is facilitated, there is an advantage that the manufacturing can be performed at low cost.

According to the third aspect of the present invention, a pressing member is swingably attached to the tip of the plunger, and the pressing member and the other member are brought into planar contact.
The planar contact between the pressing member and the member on the other side can always be stably maintained by flexibly following the change in the relative angle between the plunger and the member on the other side.

According to a fourth aspect of the present invention, since the pressing member which comes into contact with the member on the other side is swingably attached to the tip of the plunger via an elastic member, the plunger and the member on the other side are mounted. Since it is possible to more flexibly follow the change in the relative angle with the elastic member, the urging force of the elastic member acts along with the inclination of the pressing member,
It is also possible to increase the contact stability between the pressing member and the other member.

[Brief description of the drawings]

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

FIG. 2 is a longitudinal sectional view showing the same embodiment.

FIG. 3 is an exemplary sectional view taken along the line BB of FIG. 2 showing the embodiment;

FIG. 4 is an exploded perspective view showing the same embodiment.

FIG. 5 is a sectional view of a part showing the embodiment.

FIG. 6 is a hydraulic circuit diagram showing the same embodiment.

FIG. 7 is a hydraulic circuit diagram showing the same embodiment.

FIG. 8 is a sectional view taken along the line AA of FIG. 2 showing the operation of the embodiment.

FIG. 9 is an exemplary cross-sectional view of the operation of the embodiment, taken along line AA of FIG. 2;

FIG. 10 is a graph showing rotation characteristics of a vane body and torque fluctuation characteristics of a camshaft of the apparatus of the embodiment and a conventional apparatus.

FIG. 11 is a sectional view showing a second embodiment of the present invention.

FIG. 12 is a sectional view showing a third embodiment of the present invention.

FIG. 13 is a sectional view showing a fourth embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Timing sprocket (drive rotary body) 2 ... Housing (tubular member) 3 ... Camshaft 4 ... Vane body 5 ... Hydraulic circuit 6 ... Restriction mechanism 13 ... Partition wall part 14 ... Plunger 23 ... Blade part 27 ... Advanced hydraulic pressure Chamber 28: Hydraulic chamber on the retard side 67: Shoe (pressing member)

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3G016 AA06 AA19 BA23 BA38 CA04 CA13 CA15 CA17 CA24 CA27 CA33 CA36 CA46 CA48 CA52 CA59 DA06 DA22 GA00 GA01 GA04

Claims (4)

[Claims] 1. A drive rotating body which is driven to rotate by a crankshaft of an engine, and a drive cam for operating an engine valve is provided on an outer periphery, and the drive rotary body is assembled so as to be able to relatively rotate as required. A camshaft that is driven and rotated by receiving power from the driving rotator, fixed to one of the camshaft and the driving rotator, and radially extends radially outward from the center of rotation. A vane body having at least one vane portion, and a plurality of partition portions fixed to the other member of the camshaft and the driving rotating body and extending on the inner peripheral surface in the direction of the rotation center of the vane body. A tubular member having a plurality of partition walls forming an advance hydraulic pressure chamber and a retard hydraulic pressure chamber on both sides in the rotation direction of each blade of the vane body; and the advance hydraulic chamber and the retard angle. Side oil pressure A hydraulic circuit for rotating the vane body forward and reverse with respect to the tubular member by sucking and discharging hydraulic pressure relative to the tubular member; and a torque countermeasure from the engine valve when rotating the vane body in one direction with respect to the tubular member. A regulating mechanism that regulates return of the vane body by force, wherein the regulating mechanism defines a vane body as a tip end side of a plunger slidably attached to one of the vane body and the cylindrical member. A valve timing control device for an internal combustion engine configured to press against a member on the other side of a cylindrical member, wherein a pressing portion at a tip of the plunger is brought into surface contact with the member on the other side. A valve timing control device for an internal combustion engine. 2. The valve timing of an internal combustion engine according to claim 1, wherein a contact surface between the contact portion at the tip of the plunger and the contact portion of the other member is formed flat. Control device. 3. A valve for an internal combustion engine according to claim 2, wherein a pressing member is swingably attached to a tip of said plunger, and said pressing member and said member on the other side are brought into planar contact. Timing control device. 4. The plunger according to claim 1, wherein a pressing member that contacts the member on the other side is swingably attached to an end of the plunger via an elastic member. Valve timing control device.