JP3371735B2 - Valve timing control device for internal combustion engine - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an internal combustion engine (engine).
Tie) to open or close the intake or exhaust valve
Valve timing control device that continuously changes the timing
More specifically, the so-called vane-type valve timing
To a switching control device. 2. Description of the Related Art Conventionally, in automobile engines,
Achieves optimal valve timing depending on operating conditions
For this purpose, various variable mechanisms of a valve train have been put to practical use. Or
The most widely used variable mechanism is the two-stage
It is a switching type, that is, an ON / OFF control type.
In recent years, the need for higher performance engines has been increasing.
Variable valve timing mechanism
(Hereinafter also referred to as VVT mechanism),
Instead of the two-stage switching type, always use the optimal
Continuously variable type with adjustable timing
Is being developed. Has a variable valve timing mechanism
Internal combustion engines, the suction efficiency of the engine
Viewpoint, and NO _x Emissions purification performance (Emi
Fuel consumption by improving pumping loss and reducing pumping loss
Internal exhaust gas recirculation (internal EGR)
From a viewpoint, the valve timing is controlled according to the engine operating condition.
Is controlled. For example, Japanese Patent Application Laid-Open No. 8-121122 discloses
A vane-type VVT mechanism is disclosed. This vane type V
In a VT mechanism, when it is drivingly connected to a crankshaft,
A housing having a recess on the inner peripheral surface and
With vanes partitioning into two hydraulic chambers and relative rotation
A camshaft that can be combined with the housing
By controlling the hydraulic pressure supplied to the hydraulic chamber,
Rotate the camshaft relative to the housing,
Valve timing is continuously changed by shifting the rotation phase of
It has a structure to make it. And two hydraulic chambers
Of the housing and the vane
A seal member is provided between them. As the sealing member
In general, an apex seal is used. [0004] However, such a sheet
Pressure increases due to linear contact with the housing
In this state, the contact part slides with the housing,
There is a problem that it is easy. Thus, the vane type VVT
In the mechanism, the sealing performance is high due to severe wear of the sealing member.
Easy to fall, resulting in poor controllability,
There is a problem that. In view of such circumstances, an object of the present invention is to
Vane valve that can prevent wear of
An object of the present invention is to provide an imaging control device. [0006] Generally, wear is "pressure"
The higher the value of “× sliding speed” (PV value), the more easily this occurs.
In the case of the VVT mechanism, the “sliding speed of the seal member” = “V
VT mechanism response speed (displacement speed).
Considering the response speed of the VT mechanism,
Due to the magnitude of the friction
Speed. ”Therefore, in the vane type VVT mechanism, the retard angle
It can be said that wear has occurred during driving. Toko
In addition, the retardation speed has a sufficient margin for the required value.
The present invention, as described below based on the above findings
The above objectives can be achieved by adopting the technology configuration.
It is. That is, according to the first aspect of the present invention,
The valve timing control device of the fuel engine
A first rotating body having both a concave portion and a concave portion;
At least one partitioned into a first hydraulic chamber and a second hydraulic chamber
And the first rotation of the first rotation
A second rotating body coaxially combined with the rolling body;
Rotate one of the first rotator or the second rotator
A crankshaft, the first rotating body or the second
A camshaft that rotates in conjunction with the other rotating body and drives the valve
And a first hydraulic chamber or a hydraulic chamber through a hydraulic fluid supply passage.
Means for supplying hydraulic fluid to the second hydraulic chamber
And at least the first rotating body or the second rotating body.
The first hydraulic chamber and the second hydraulic
Internal combustion engine comprising: a sealing member for partitioning a chamber in a liquid-tight manner.
In the valve timing control device according to
Is retarded relative to the crankshaft
In order to prevent wear of the seal member, the first
The speed of the relative rotation between the rotating body and the second rotating body is reduced.
And a retarding speed reducing means for reducing the retarding speed. According to a second aspect of the present invention, the above
In the apparatus according to the first aspect of the present invention, the retardation velocity
The reducing means is provided in the working fluid supply passage,
The shaft is advanced with respect to the crankshaft.
Pressure loss in the direction of hydraulic fluid flow when
The shaft is retarded with respect to the crankshaft.
Pressure loss that increases the pressure loss in the working fluid flow direction when
It is constituted by providing the adjusting means. Further, according to a third aspect of the present invention,
The apparatus according to the second aspect of the present invention, wherein the pressure loss
The loss adjusting means includes a passage surface provided in the hydraulic fluid supply passage.
A product changing unit, wherein the camshaft is connected to the crankshaft.
Hydraulic fluid flow direction when retarded to shaft
To increase the area at a ratio of 1 / 0.7 or more
You. [0010] The first aspect of the present invention configured as described above.
In the valve timing control device for an internal combustion engine according to
Of the relative rotation between the first rotating body and the second rotating body.
And the sliding speed of the seal member increases,
When the camshaft is retarded, which tends to increase wear,
And its relative rotational speed can be kept low,
The defect is eliminated. Further, according to the second aspect of the present invention,
In the device, the reduction of the retarding speed requires special control.
Without the need for advance in the hydraulic fluid supply passage.
Hydraulic fluid flow when retarded compared to pressure loss in the hydraulic fluid flow direction
Easily achieved by increasing the pressure loss in the direction
Is done. Further, in the device according to the third aspect of the present invention,
Indicates that the increase in pressure loss in the working fluid flow direction at the time of retard
Area in the working fluid flow direction at a ratio of 1 / 0.7 or more
With a very simple configuration of providing an expanding part
Is achieved. The present invention will be described below with reference to the accompanying drawings.
An embodiment will be described. FIGS. 1 to 5 show an embodiment of the present invention.
Of the internal combustion engine valve timing control device 10 according to
FIG. Here, FIG.
FIG. 1 is a perspective view showing a schematic configuration of a lubrication timing control device 10.
Yes, Figure 2 shows valve timing control with cover 13 removed
It is a front view of the apparatus 10. FIG. 3 is a view taken from 3-3 in FIG.
Side when the valve timing control device 10 is cut off with a line
FIG. 4 is a sectional view taken along line 3-3 in FIG.
FIG. 7 is a partially enlarged cross-sectional view when the mining control device 10 is cut.
is there. Further, FIG. 5 shows the valve timing by line 5-5 in FIG.
FIG. 2 is a side cross-sectional view when the tuning control device 10 is cut. The valve timing control device 10 is a
Ket 11, rotor 12, cover 13, rear housing
14 and an intake-side camshaft 15. The sprocket 11 has the same rotation axis as its own.
It is made of a thick cylindrical member having a hollow portion 111 of a shaft.
The outer peripheral surface on the end side (left side in FIG. 1) has a timing chain
A plurality of teeth 112 for mounting (not shown) are formed.
Have been. That is, the engine (not shown)
The driving force output from the link shaft (not shown)
Crank sprocket fixed to the crankshaft
(Not shown) and the timing chain
This is transmitted to the ket 11. Also sprocket
A cover 13 is provided on the outer peripheral surface on the distal end side (right side in FIG.
Cover attaching portion 113 for attaching
You. Further, the sprocket 11 is moved outward from the tip.
A hollow portion is formed on the inner peripheral surface corresponding to the formation position of the teeth 112 on the peripheral surface.
Four substantially fan-shaped concave portions 114 extending from 111 to the outer peripheral surface are formed.
And four relatively trapezoidal protrusions between each recess 114.
A part 115 is formed. In addition, the teeth 112 on the outer peripheral surface
From the inner peripheral surface corresponding to the forming position to the base end,
Rear housing mounting for mounting the housing 14
A part 116 is formed. As will be described later, the sprocket 11
Is supplied with engine oil (oil pressure).
And a sprocket 11, a rotor 12, a cover 13, and
When the rear housing 14 is combined, the hydraulic chamber and
Function. Further, one of the projections 115 of the sprocket 11
First, as shown in FIG.
When the relative rotation of 1 is not restricted, the lock pin 20 is reset.
Lock pin so that it does not contact the
20 has a lock pin hole 117 for completely containing
You. The lock pin 20 has a large diameter portion 21 and a small diameter portion 2.
2 is a cylindrical pin having a large diameter
A spring hole 23 for accommodating the ring 24.
You. Connection between large diameter portion 21 and small diameter portion 22 of lock pin 20
A ring-shaped end face appearing in the portion is provided with an advanced hydraulic chamber 10 described later.
1 as the first pressure receiving surface 25 to which the hydraulic pressure supplied to
Function, the end surface of the small diameter portion 22 on the rear housing 14 side is
The hydraulic pressure supplied to the retard hydraulic chamber 102 described above is applied.
It functions as the second pressure receiving surface 26. Further, the first pressure receiving surface area and the second pressure receiving surface area
What is the advance chamber oil pressure x first pressure receiving surface area / retard chamber oil pressure x second pressure receiving surface
It is determined so that the area relationship is established. And lock
The cupin 20 is moved to the rear housing by a spring 24.
It is constantly receiving urging force in 14 directions. The lock pin hole 117 is
End face generated by a difference in diameter between large diameter portion 21 and small diameter portion 22
(First pressure receiving surface 25), applied to advance hydraulic chamber 101
As shown in FIG.
In this way, two cylindrical holes of different diameters having the same axis
ing. The lock pin hole 117 is shown in FIG.
Communication between the advanced hydraulic chamber 101 and the first pressure receiving surface 25
The lock pin advance hydraulic pressure supply passage 118 is provided. The rotor 12 has a bore coaxial with its own rotation axis.
Having a through hole 121 and inside the sprocket 11
It is made of a thick cylindrical body that fits the space 111, and its outer periphery
On the surface, four vanes 122 are arranged at 90 ° intervals in the radial direction.
It is stretch formed. The vane 122 has a sealing member (a
Pex seal) 123 and rotor 12 are sprockets
When the seal member 123 is attached to the sprocket 11
A leaf spring 124 that presses against the inner peripheral surface of the concave portion 114 of the slot 11
It has. The vane 122 is connected to the sprocket 1
1, rotor 12, cover 13, and rear housing 14
Sprockets function as hydraulic chambers when
The concave portion 114 of the gate 11 is divided into an advance hydraulic chamber and a retard hydraulic chamber.
I do. Here, a partition is provided on the left side of the vane 122 in FIG.
The formed hydraulic chamber functions as an advance hydraulic chamber, and the vane 1
The hydraulic chamber defined on the right side of 22 is a retard hydraulic chamber
Shall function. Further, in the present embodiment,
Rocket 11, rotor 12, cover 13, and rear how
Vane 122 in a state where jing 14 is combined
The recess 114 on the left side is connected to the advance hydraulic chamber 101 and the vane 122.
The right recess 114 is referred to as the retard hydraulic chamber 102.
You. The vicinity of the tip of the rotor 12 (right in FIG. 1)
Side) and the side of the advance hydraulic chamber 101 of each vane 122
Is the advance hydraulic chamber 10 of the bolt hole 121 and each vane 122.
Rotor advance hydraulic pressure supply passage 125 communicating with the base end on the first side
Are formed near the base end of the rotor 12 (left in FIG. 1).
Side) and the side of the vane 122 on the side of the retard hydraulic chamber 102,
The bolt hole 121 and the retarded hydraulic chamber 102 side of each vane 122
The rotor retard hydraulic pressure supply passage 126 communicating with the base end of the rotor is shaped.
Has been established. Further, one vane 122 has its proximal end
Side, rotor 12 and rear housing 14 are securely synchronized
An engagement pin 30 for engaging the two to rotate is inserted.
It has an engaging pin hole 127 to be inserted. The cover 13 extends along the outer peripheral surface of the disk-shaped member.
To fit the cover mounting portion 113 of the sprocket 11
It has a flange 131 and is coaxial with its rotation axis.
And a bolt hole 132 through which the coupling bolt 32 passes
I have. The rear housing 14 includes the sprocket 11
Of the flange inscribed in the rear housing mounting portion 116
A thick disk portion 141 on the outer periphery thereof;
And a shaft portion 142 formed on the distal end surface of the shaft. The disk portion 141 is a rear housing advance hydraulic pressure.
Supply path 143, rear housing retard hydraulic pressure supply path 144,
Lock pin engagement hole 14 for engaging lock pin 20
5. Engagement for engaging the rear housing 14 with the rotor 12
An engagement pin hole 146 into which the pin 30 is inserted is provided.
Also, the rear end of the rear housing 14
And the intake side camshaft 15 are reliably rotated synchronously.
Engagement where the engagement pin 31 that securely engages both is inserted
It has a pin hole 147. Further, the disk portion 141 and the shaft portion 142
A bolt coaxial with the rotation axis and through which the coupling bolt 32 passes
A hole 148 is provided on the outer peripheral surface of the shaft portion 142.
Seal groove 149 for mounting the
I have. The intake side camshaft 15 is located near the tip (see FIG.
1 (right side), each journal including the journal part 151
Cylinder head (not shown) via internal portion 151
Supported by a journal receiver (not shown)
You. And, the journal part 151 has the connecting bolt 32
Bolt connection hole 152 to be screwed, tip of camshaft 15
Advance hydraulic supply port between the disc-shaped end face of the
153, a cam communicating with the retard hydraulic pressure supply port 154
Shaft advance hydraulic pressure supply path 155, camshaft retard hydraulic pressure
Two supply paths 156 are provided. On the outer peripheral surface of the journal part 151,
Oil control even when the intake camshaft 15 rotates
From the valve (OCV) via the journal receiver
The engine oil is supplied to the advance hydraulic pressure supply port 153,
The oil can be smoothly supplied to the angular hydraulic supply port 154
A connection hydraulic supply path 157 is formed. Further, a disc-shaped portion at the tip of the cam shaft 15
The end face connects the camshaft 15 and the rear housing 14.
Engagement pin hole 158 for inserting mating engagement pin 31
It has. The above-mentioned components are mutually connected in the relationship shown in FIG.
And finally bolt holes 121, 1 of each member
After inserting the connecting bolt 32 into the connecting bolt 32,148,
Bolt 32 of the intake side camshaft 15
And the valve timing control device 10 is assembled.
It is. In this assembly, the lock pin 20
Is engaged with the lock pin engagement hole 145, the vane 122
Is separated from the protrusion 115 of the sprocket 11 by α degrees
Assembled to be locked in position. That is, an engine in which no hydraulic pressure is generated
At the time of starting, the relative position between the rotor 12 and the sprocket 11
The vane 122 is positioned at the position where the rotation is mechanically regulated.
At a position separated by α degrees from the convex portion 115 of the
Because As a result, the valve timing control device 10
Is the valve required when starting the engine after starting the engine.
Valve ties, independent of timing
It is possible to delay the mining. Here, the cover 13, the rotor 12, and the
The housing 14 is connected to the intake side housing by a connecting bolt 32.
The camshaft is connected to the intake shaft
It rotates in synchronism with the shaft 15. In addition, the rotor 12 and
Housing 14, the rear housing 14, and the intake side housing.
The shaft 15 is engaged by engagement pins 30 and 31, respectively.
, The relative rotation is reliably restricted,
These three members 12, 13, 14 rotate synchronously. to this
On the other hand, the sprocket 11 is
Not bound to Therefore, the sprocket 11 is mounted on the intake side power.
Relative to the shaft 15, and as a result
The rotor 12 and the sprocket 11 rotate relative to each other,
Intake side camshaft 1 for rotation phase of link shaft
The rotation phase 5 is advanced or retarded. Next, referring to FIGS.
Oil passage configuration and valve timing of the imaging control device 10
The operation of the control device 10 is controlled by the OCV 40
It will be explained while following the flow of engine oil. The OCV 40 includes an electromagnetic actuator 41
And a plunge driven by the coil spring 42
The spooler 43 reciprocates the spool 44 in the axial direction.
4 ports to switch engine oil flow direction
It is a directional control valve. And the electromagnetic actuator 41
Is controlled by duty to adjust its opening.
And the hydraulic pressure supplied to each of the hydraulic chambers 101 and 102 is adjusted.
Is done. The casing 45 of the OCV 40 is
Port 45t, A port 45a, B port 45b, and 2
It has two reservoir ports 45r. And tongue
The port 45t is connected to the hydraulic pump 46 and the oil filter 4
7 is connected to the oil pan 48 via
Port 45a is connected to the advance hydraulic pressure supply port 153,
The port 45b is connected to the retard hydraulic pressure supply port 154.
ing. Also, the two reservoir ports 45r are provided with oil.
It is in communication with the pan 48. The spool 44 is a cylindrical valve body,
Seals the flow of engine oil between two ports
Communication between the four lands 44a and the two ports
Passage 44b and two allowing engine oil flow
Has a passage 44c. When the engine is stopped, the hydraulic pump 46, O
CV40 is not working together, and when cranking
In this case, since sufficient hydraulic pressure is not generated, the advanced hydraulic chamber 101
No hydraulic pressure is applied to the retard hydraulic chamber 102 and both hydraulic chambers
A lock pin to which the hydraulic pressure supplied to 101 and 102 is applied
No oil pressure is applied to the motor 20. As a result, the lock pin
20 is a rear housing by the elastic force of a spring 24.
14 when the engine is stopped.
When the lock pin engagement hole 14
Locked when engaged with 5 or when engine stopped
If the pin engaging hole 145 is not engaged,
The rotation of the rotor 12 at the time of
It engages with the hole 145. Therefore, when starting the engine, the rotor
12 and the sprocket 11 rotate synchronously, and the sprocket
11 (crankshaft not shown)
The rotation phase of the shaft 15 is not changed. In addition,
In the embodiment, the lock pin engagement hole 145 is
Position to achieve the optimal valve timing for starting
In other words, rather than the position that realizes the valve timing of the most retarded angle
(positions separated by α degrees). As a result,
When starting the engine, always optimize the intake camshaft 1
5, the valve timing of the intake valve
Engine is determined mechanically, and
There is no loss. After starting the engine, the hydraulic pump 46
When sufficient oil pressure is generated, the OCV 40 is driven and controlled,
When the ruler 44 is moved to the left of the drawing, the passage 4
4b communicates between tank port 45t and A port 45a
And the engine oil is supplied to the advance hydraulic pressure supply port 153.
Is done. Then, it is supplied to the advance hydraulic pressure supply port 153.
The engine oil that has been removed is the first hydraulic pressure in the journal 151.
The supply path 155 is connected to the inner peripheral surface of the bolt hole 121 of the rotor 12.
Clearance between outer surface of mating bolt 32 and advance hydraulic pressure of rotor 12
The oil is supplied to the advance hydraulic chamber 101 through the supply path 125,
The hydraulic pressure in the square hydraulic chamber 101 increases. At the same time, the passage 44c is
Port 45b and the reservoir port 45r.
The engine oil in the chamber 102 is the retard hydraulic pressure of the rotor 12.
Supply passage 126, retard hydraulic supply passage in journal 151
156, the second hydraulic supply port 154, and the OCV 40
Through the B port 45b and the reservoir port 45r of
The oil is discharged to the oil pan 48 and the hydraulic pressure of the retard hydraulic chamber 102 is reduced.
Decrease. The first pressure receiving surface 25 of the lock pin 20
Is the lock pin advance hydraulic pressure from the adjacent advance hydraulic chamber 101.
The hydraulic pressure is supplied via the supply path 118. And the advance angle
The hydraulic pressure in the hydraulic chamber 101 rises, and the elastic force of the spring 24
Is exceeded, the lock pin 20 engages with the lock pin.
Separates from the hole 145 and contacts the surface of the rear housing 14
It is stored in the lock pin hole 117 so that it does not occur.
Therefore, the smooth connection between the rotor 12 and the sprocket 11
Relative rotation is allowed. Alternatively, the hydraulic pressure is already
Is applied, the lock pin 20 is in the second pressure receiving state.
In the lock pin hole 117 by the hydraulic pressure applied to the surface 26
Is stored in Then, it acts on the second pressure receiving surface 26.
The pressure decreases as the pressure in the retard hydraulic chamber 102 decreases.
However, the pressure acting on the first pressure receiving surface 25 increases.
The lock pin 20 is still in the lock pin hole 117.
Remains stored in Therefore, the vane 122 is provided in the advance hydraulic chamber.
The rotation direction from 101 to the retard hydraulic chamber 102 (see FIG. 2)
(In the clockwise direction) and receive the hydraulic pressure to rotate the rear housing.
Torsion is applied to the intake side camshaft 15 through the
It is. As a result, the sprocket 11 (clamp not shown)
Rotation of the intake-side camshaft 15 with respect to the
The phase is changed, and the intake camshaft 15 moves from the retarded position.
Rotate to advanced position. And the intake side camshaft
Opening timing of the intake valve driven by
Is advanced. Thus, the valve opening timing is advanced.
The intake valve opened while the exhaust valve was open.
And the intake and exhaust valves open simultaneously.
The valve overlap period is extended
You. Then, the vane 122 is connected to the projection 1 of the sprocket 11.
The opening timing of the intake valve at the phase where it comes into contact with 15
Is the fastest. On the other hand, the drive of the OCV 40 is controlled.
When the spool 44 is moved rightward in the drawing,
Sage 44b is connected to tank port 45t and B port 45b.
And the engine oil is supplied to the second hydraulic supply port 154.
Is supplied. Then, the power is supplied to the second hydraulic pressure supply port 154.
The supplied engine oil is delayed in the journal section 151.
Angular hydraulic supply path 156, retard hydraulic supply path 12 for rotor 12
6 to the retard hydraulic chamber 102 and the retard hydraulic chamber 1
02 oil pressure increases. At the same time, the passage 44c
Port 45a and the reservoir port 45r.
The engine oil in the chamber 101 is the advance hydraulic pressure of the rotor 12.
Supply passage 125, bolt hole 121 of rotor 12 and coupling bolt
, And the advance hydraulic pressure supply passage of the journal 151
155, the first hydraulic pressure supply port 153, and the OCV 40
Through the A port 45a and the reservoir port 45r of
The oil is discharged to the oil pan 48. Therefore, the advance hydraulic chamber
The oil pressure at 101 decreases. Also, the second pressure receiving surface 26 of the lock pin 20
From the retard hydraulic pressure supply passage 156 in the journal 151
Directly via the lock pin retard hydraulic pressure supply path 261 (retard oil
Oil pressure is supplied (without passing through the pressure chamber 102). Soshi
Therefore, after the engine starts, first the hydraulic pressure is
When the voltage is applied, the lock pin 20 is connected to the first pressure receiving surface 2.
5 operates in the same manner as when hydraulic pressure acts. on the other hand,
If the hydraulic pressure has already acted on the first pressure receiving surface 25,
Although the hydraulic pressure acting on the first pressure receiving surface 25 decreases,
Since the hydraulic pressure acting on the pressure surface 26 increases, the lock pin 2
0 is continuously locked in the lock pin hole 117. Accordingly, the vane 122 is provided in the retard hydraulic chamber.
The rotation direction from 102 to the advance hydraulic chamber 101 (see FIG. 2)
Counter-clockwise) and rotate in response to hydraulic pressure,
Torsion is applied to the intake side camshaft 15 via the ring 14
Is done. As a result, the sprocket 11 (class
Rotation of the intake side camshaft 15 with respect to the
The phase is changed and the intake camshaft 15 is in the advanced position.
To the retard position. And the intake side camshaft
Opening timing of the intake valve driven by the shaft 15
Is delayed. Thus, the valve overlap period is reduced.
Or removed. In addition, the vane 122 is connected to the sprocket 1
Opening of the intake valve at the phase of contact with the first convex portion 115
The timing is the slowest. Eventually, when the engine stops, the hydraulic pump
The pump 46 stops, and the oil pressure in the engine system becomes zero. Ma
In addition, the spool 44 of the OCV 40 is
Stop at the position where the hydraulic pressure is supplied, and
The engine oil is discharged to an oil pan 48. Therefore, the first pressure receiving surface of the lock pin 20
25, the hydraulic pressure applied to the second pressure receiving surface 26 also decreases,
The lock pin 20 is reset by the elastic force of the spring 24.
The housing 14 is pressed. In addition, the intake valve
With the rotation of the intake side camshaft 15 receiving the force, the rotor
12 (vane 122) rotates toward the advance hydraulic chamber 101 side.
You. Then, when the lock pin engagement hole 145 arrives
The lock pin 20 is engaged with the lock pin engagement hole 145.
The relative rotation between the rotor 12 and the sprocket 11 is restricted.
It is. Now, the intake side power for the sprocket 11 will be described.
Retard the relative rotation angle (rotation phase) of the shaft 15
Displacement speed (retarding speed) when tightening and when advancing
And the displacement speed (advance angle speed) of the friction
Due to the difference, the advance angle speed 進 the retard angle speed. Therefore,
A sealing member (appet
Seal 123 is in the recess 114 of the sprocket 11.
The speed when sliding on the peripheral surface increases at the time of retarding. So
Then, the value of "pressure x sliding speed" (PV value) is high
The wear of the seal member 123 is retarded
It will go to. By the way, the retardation speed is
I can afford it. Therefore, in this embodiment,
Reduces the retardation speed so that the sealing member 123
To prevent wear. The reduction of the retardation speed is caused by the hydraulic supply passage.
And retards compared to the pressure loss in the oil flow direction during advance.
Adopts a configuration that increases the pressure loss in the oil flow direction at the time of
This can be achieved. In particular,
In the present embodiment, as shown in FIG.
Passage area change to retard hydraulic pressure supply passage 156 in null part 151
And a camshaft 15 with respect to the sprocket 11
1 / 0.7 or less in the oil flow direction when retarding
The pipe cross-sectional area is enlarged at the above ratio. That is, as shown in FIG.
At the time of retarding, the retard hydraulic pressure supply passage 156 is shifted from right to left in the drawing.
Oil flows into the pipe, and on the way, the area of the pipeline is A2
To A1. On the other hand, at the time of advance, retarded oil
Oil flows through the pressure supply passage 156 from left to right in the drawing.
On the way, the area of the pipeline is rapidly reduced from A1 to A2.
It will be. Pressure loss in the direction of rapid line expansion
The coefficient is ζ1 and the pressure loss coefficient in the direction of rapid line contraction is ζ
Assuming that 2, the cross-sectional area ratio A2 / A1 of ζ1, ζ2 and
Is as shown in the graph of FIG. FIG. 6B shows the enlarged loss coefficient.
Ζ1 / ζ2 and the cross-sectional area ratio A2 of the pipeline
/ A1 is also shown. As you can see from this figure
In contrast, if A2 / A1 is 0.7 or less, the direction of the pipeline rapid expansion
That is, the pressure loss in the oil flow direction at the time of retard
Is the direction of the oil flow at the time of the rapid contraction of the pipeline, that is, the advance angle.
Is greater than the pressure loss at Therefore, this implementation
In the embodiment, 1/0.
Retard the passage area change part that enlarges the area at a ratio of 7 or more
This is provided in the hydraulic supply path 156. Thus, before
As described above, the retarding speed, that is, the seal at the time of retarding
The sliding speed of the member 123 is suppressed,
Wear is prevented. As described above, in the present embodiment, the delay
Although a passage area changing portion is provided in the angular hydraulic pressure supply passage 156,
The same applies to the case where a passage area changing portion is provided in the hydraulic pressure supply passage 155.
Action can be obtained. In addition, controlling the displacement speed requires the OCV
It is also possible by the control of 40. Control OCV40
Drive duty ratio for the electromagnetic actuator 4
Of ON time in energizing pulse to 1 solenoid
In other words, it indicates the current value supplied to the solenoid,
Therefore, it is proportional to the stroke of the spool 44. Spool 4
4 is arranged at an arbitrary position within the movable range.
The oil flow area changes, and the advance and retard speeds
Changes slightly. Therefore, the drive duty ratio
It is possible to control the displacement speed based on the value of.
That is, by changing the value of the drive duty ratio,
The valve timing determines the displacement speed.
However, the displacement angle is not determined. Paraphrase
Then, the OCV 40 is controlled based on the drive duty ratio.
When the spool 44 is moved by
Valve timing after moving the spool 44
The angle of displacement. Thus, OCV40
The retard speed can also be suppressed by the control. As described above, according to the present invention,
It is possible to prevent the wear of the seal member.
A vane type valve timing control device is provided. sand
That is, according to the first aspect of the present invention, sliding of the seal member is performed.
Suitable for retarding when the speed is high and its wear tends to increase
The speed is kept low,
You. According to the second aspect of the present invention, the retardation velocity
Reduced hydraulic fluid supply without the need for special controls.
In the supply passage, the pressure loss is
To increase the pressure loss in the hydraulic fluid flow direction at the time of retard
This is easily achieved by the configuration. Further, the third aspect of the present invention
According to the aspect, the pressure loss in the flow direction of the hydraulic fluid at the time of the retard is increased.
The ratio is 1 / 0.7 or more in the working fluid flow direction at the time of retarding
Very simple to provide a part to increase the area with
It is realized by the configuration.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an exploded perspective view showing a schematic configuration of a valve timing control device according to an embodiment of the present invention. FIG. 2 is a front view of the valve timing control device with a cover removed. FIG. 3 is a side sectional view taken along line 3-3 in FIG. 2; FIG. 4 is a partially enlarged cross-sectional view when cut along line 3-3 in FIG. 2; FIG. 5 is a side sectional view taken along line 5-5 in FIG. 2; 6A is a diagram illustrating a passage area changing portion provided in a retard hydraulic pressure supply passage 156, and FIG. 6B is a diagram illustrating a pressure in a pipeline rapid expansion direction (at the time of retard, A1 ← A2); Loss factor ζ
1. Shows the pressure loss coefficient ζ2 in the direction of abrupt contraction of the pipeline (at the time of advance, A1 → A2) and how the ratio ζ1 / ζ2 changes according to the cross-sectional area ratio A2 / A1 of the pipeline. It is a characteristic diagram. DESCRIPTION OF SYMBOLS 10 ... Valve timing control device 11 ... Sprocket (first rotating body) 111 ... Hollow portion 112 ... Teeth 113 ... Cover mounting portion 114 ... Recessed portion 115 ... Convex portion 116 ... Rear housing mounting portion 117 ... Lock pin Hole 118 Lock pin advance hydraulic pressure supply path 12 Rotor (second rotating body) 121 Bolt hole 122 Vane 123 Seal member (apex seal) 124 Plate spring 125 Rotor advance hydraulic pressure supply path 126 Rotor Retard hydraulic pressure supply path 127 engaging pin hole 13 cover 131 flange 132 bolt hole 14 rear housing 141 thick disc 142 shaft 143 rear housing advance hydraulic pressure supply path 144 rear housing retard Hydraulic supply path 145 Lock pin engagement hole 146 Engagement pin hole 147 Engagement pin hole 148 Bolt hole 149 Sea Groove 15 ... intake side camshaft 151 ... journal portion 152 ... bolt connection hole 153 ... advance hydraulic pressure supply port 154 ... retard hydraulic pressure supply port 155 ... camshaft advance hydraulic supply path 156 ... camshaft retard hydraulic supply path 157 ... Connection hydraulic pressure supply path 158... Engagement pin hole 20. Lock pin 21. Large diameter portion 22. Small diameter portion 23. Spring hole 24. Spring 25. First pressure receiving surface 26. Supply path 30 Engagement pin 31 Engagement pin 32 Coupling bolt 40 Oil control valve (OCV) (hydraulic fluid supply means) 41 Electromagnetic actuator 42 Coil spring 43 Plunger 44 Spool 44a Land 44b Passage 44c Passage 45 Casing 45t Tank port 45a A port 45b B port 45r ... reservoir port 46 ... hydraulic pump (hydraulic fluid supply means) 47 ... oil filter 48 ... oil pan (hydraulic fluid supply means) 101 ... advance hydraulic chamber 102 ... retard hydraulic chamber

Continuation of front page (56) References JP-A-8-121122 (JP, A) JP-A-8-170507 (JP, A) JP-A-7-139317 (JP, A) JP-A-7-229408 (JP) , A) Hydraulic Mechanical Engineering Handbook Editing Committee, Hydraulic Mechanical Engineering Handbook, Japan, Corona Co., Ltd., December 15, 1957, first edition, p. 51-52 Editorial Committee of the Japan Hydraulic Manufacturers Association, Practical Hydraulic Pocketbook Revised Edition, Japan, Japan Hydraulic Manufacturers Association, August 25, 1967, p. 327 (58) Fields surveyed (Int. Cl. ⁷ , DB name) F01L 1/34

Claims (1)

(57) [Claim 1] A first rotating body having at least one concave portion on an inner peripheral surface, and the concave portion is divided into a first hydraulic chamber and a second hydraulic chamber. A second rotating body having at least one vane and being coaxially combined with the first rotating body so as to be relatively rotatable; and a crankshaft for rotating one of the first rotating body and the second rotating body. A camshaft that rotates in conjunction with the other of the first rotator or the second rotator and drives a valve; and a first hydraulic chamber or the second hydrator via a hydraulic fluid supply passage.
Hydraulic fluid supply means for supplying hydraulic fluid to the hydraulic chamber of the first and second hydraulic bodies, the first hydraulic chamber and the second hydraulic chamber provided in at least one of the first rotating body or the second rotating body. And a seal member for partitioning the camshaft in a liquid-tight manner, wherein the camshaft is retarded with respect to the crankshaft.
To prevent wear of the sealing member when
Relative rotation between the first rotator and the second rotator
As a retarding speed reducing means for reducing the speed of the camshaft, as compared with the pressure loss in the working fluid flow direction when the camshaft is advanced with respect to the crankshaft, the camshaft is provided in the working fluid supply passage. Pressure loss adjusting means for increasing the pressure loss in the flow direction of the hydraulic fluid when retarded with respect to the crankshaft; and the pressure loss adjusting means is provided in the hydraulic fluid supply passage.
A passage area changing portion, wherein the camshaft is
Operation when retarded with respect to the crankshaft
Enlarge the area at a ratio of 1 / 0.7 or more in the liquid flow direction
And characterized in that, the valve timing control apparatus for an internal combustion engine.