Valve timing control device

A valve timing control device includes a rotor fixed on a cam shaft rotatably supported on a cylinder head of an engine so as to be accommodated in the cylinder head, a housing member rotatably mounted on the cam shaft so as to surround the rotor, plural chambers defined between the housing member and the rotor each of which having a pair of circumferentially opposed walls, plural vanes mounted on the rotor and extended outwardly therefrom in the radial direction into the chambers so as to divide each of chamber into a first pressure chamber and a second pressure chamber and a fluid supplying device for supplying fluid under pressure to at least a selected one of the first pressure chamber and the second pressure chamber.

BACKGROUND OF THE INVENTION 
1. Field of the Invention 
The present invention relates to a valve timing control device and, in 
particular, to a valve timing control device for controlling an angular 
phase difference between a crank shaft and a cam shaft of a combustion 
engine. 
2. Description of the Prior Art 
In general, valve timing of a combustion engine is determined by valve 
mechanisms driven by a cam shaft according to a characteristic of the 
combustion engine or the use of the combustion engine. Since conditions of 
combustion are changed in response to the rotational speed of the 
combustion engine, it is difficult to obtain optimum valve timing through 
the whole rotational range. Therefore, a valve timing control device which 
is able to change valve timing in response to the condition of the 
combustion engine has, in recent years, been proposed as an auxiliary 
mechanism of the valve mechanism. 
A conventional device of this kind is disclosed, for example, in U.S. Pat. 
No. 4,858,572. This device includes a rotor which is fixed on an outer 
projecting end of a cam shaft rotatably supported on a cylinder, a drive 
member which is driven by the rotational torque from a crank shaft and 
which is rotatably mounted on the outer projecting end of the cam shaft so 
as to surround the rotor, a plurality of chambers which are defined 
between the drive member and the rotor and each of which has a pair of 
circumferentially opposed walls and a plurality of vanes which are mounted 
to the rotor and which are extended outwardly therefrom in the radial 
direction into the chambers so as to divide each of chambers into a first 
pressure chamber and a second pressure chamber. In this device, a fluid 
under pressure is supplied to a predetermined one of either the first 
pressure chamber or the second pressure chamber in response to the running 
condition of the combustion engine and an angular phase difference between 
the crank shaft and the cam shaft is controlled so as to advance or retard 
the valve timing relative to the crank shaft. The valve timing control 
device is in the position of the maximum advanced condition when each of 
the vanes contacts with one of the opposed walls of each of the chambers. 
On the other hand, the valve timing control device is in the position of 
the maximum retarded condition when each of the vanes contacts with the 
other of the opposed walls of each of the chambers. 
In the event that the valve timing control device is disposed at the 
outside of the cylinder head as in the above prior device, if the fluid, 
which is the same as a fluid for lubricating the engine, leaks from the 
chambers to outside, the amount of the fluid for operating the valve 
timing control device is decreased and other devices, which are located in 
the vicinity of the valve timing control device, become dirty. Therefore, 
strict fluid-tightness is required for the chambers, and additional seal 
members are always required for fluid-tight sealing of the chambers. 
Thereby, the structure of the valve timing control device is complicated. 
SUMMARY OF THE INVENTION 
It is, therefore, an object of the present invention to provide an improved 
valve timing control device which overcomes the aforementioned drawbacks. 
It is another object of the present invention to provide an improved valve 
timing control device which has a simplified structure. 
In order to achieve these objectives, there is provided an improved valve 
timing control device which includes a rotor fixed on a cam shaft 
rotatably supported on a cylinder head of an engine so as to be 
accommodated in the cylinder head, a housing member rotatably mounted on 
the cam shaft so as to surround the rotor, plural chambers defined between 
the housing member and the rotor, each of which having a pair of 
circumferentially opposed walls, plural vanes mounted on the rotor and 
extended outwardly therefrom in the radial direction into the chambers so 
as to divide each chamber into a first pressure chamber and a second 
pressure chamber and a fluid supplying means for supplying fluid under 
pressure to at least a selected one of the first pressure chamber and the 
second pressure chamber.

DESCRIPTION OF THE PREFERRED EMBODIMENTS 
A valve timing control device in accordance with a preferred embodiment of 
the present invention will be described with reference to attached 
drawings. 
In an embodiment shown in FIGS. 1 to 3, a valve timing control device 
according to the present invention is applied to an engine E of the DOHC 
(Double Over Head Cam Shaft) type. 
Referring to FIG. 1, an exhaust cam shaft 2 (a cam shaft) and an intake cam 
shaft 3 (another cam shaft) are rotatably mounted on a cylinder head 1 of 
an engine and are connected to each other by a rotational torque 
transmitting means 6. The rotational torque transmitting means 6 is 
comprised of a gear 4 which is rotatably mounted on the exhaust cam shaft 
2 and a gear 5 which is fixedly mounted on the intake cam shaft 3. 
An end of the exhaust cam shaft 2 is projected out of the cylinder head 1 
and a timing pulley 7 is fixed to this projecting end of the exhaust cam 
shaft 2 by a bolt 8. A stopper pin 9 is fixed to the projecting end of the 
exhaust cam shaft 2 and is fitted into a notch formed on the timing pulley 
7 so that the relative rotation between the timing pulley 7 and the 
exhaust cam shaft 2 is prevented. Rotational torque is transmitted to the 
timing pulley 7 via a belt 49 from a crank shaft 48 which is rotated by 
the engine. 
A cylindrical portion 10 of the exhaust cam shaft 2, which is extended into 
the cylinder head 1, is provided with a male screw portion 11 on which a 
male screw is formed and a passage portion on which two circular grooves 
12, 13 are formed in order from a front side (left side) in FIG. 1. The 
circular grooves 12, 13 are formed so as to maintain a predetermined 
distance between each other in the axial direction. At the adjacent 
portion of the passage portion (at the right side of the passage portion 
in FIG. 1), a journal portion 14 having a larger diameter than that of the 
passage portion is formed and a plurality of cam portions 15 are 
continuously formed at the right side of the journal portion 14. On the 
journal portion 14, the gear 4 having three female screw holes which are 
penetrated in the axial direction and are separated in the circumferential 
direction at regular intervals is rotatably mounted thereon. 
On the passage portion of the exhaust cam shaft 2, a valve timing control 
mechanism 16 is mounted thereon. As shown in FIG. 1 and FIG. 3, the valve 
timing control mechanism 16 includes a rotor 17, six vanes 18, a housing 
member 19, a circular front plate 21 and a circular rear plate 22. The 
rotor 17 has a cylindrical shape and is fixedly mounted on the passage 
portion of the exhaust cam shaft 2 by a pin 32. The pin 32 is pressed into 
the passage portion of the exhaust cam shaft 2 in the radial direction and 
is fitted into notch portion 33 formed on the inner circumferential 
portion of the rotor 17 so that the relative rotation between the rotor 17 
and the exhaust cam shaft 2 is prevented. The housing member 19 has a 
cylindrical shape having an inner bore 19b and is rotatably mounted on the 
outer circumferential surface of the rotor 17 so as to surround the rotor 
17. The housing member 19 has the same axial length as the rotor 17 and is 
provided with six grooves 19a which are outwardly extended from the inner 
bore 19b in the radial direction and which are separated in the 
circumferential direction at regular intervals. The housing member 19 is 
also provided with three holes which are penetrated in the axial direction 
and which are separated in the circumferential direction at regular 
intervals. The rear plate 22 is rotatably mounted on the journal portion 
14 so as to be located between the gear 4 and one side face of the housing 
19 and the rotor 17, and is provided with three holes which are penetrated 
in the axial direction and which are separated in the circumferential 
direction at regular intervals. The front plate 21 is located so as to be 
opposite to the other side face of the housing member 19 and the rotor 17 
and is provided with three holes which are penetrated in the axial 
direction and which are separated in the circumferential direction at 
regular intervals. Three bolts 23 are fitted into the holes of the front 
plate 21, the housing member 19 and the rear plate 22, and are screwed 
into the female screw holes of the gear 4. Thereby, the front plate 21 is 
pressed fluid-tight to the other side face of the housing 19 and the rotor 
17 and the rear plate 23 is fluid-tightly pressed to one side faces of the 
housing 19 and the rotor 17. Namely, the contacting portions among the 
front plate 21, the rotor 17 and the housing member 19 and among the rear 
plate 22, the rotor 17 and the housing member 19 are sealed by a metal 
contact, respectively. 
One side face of the rotor 17 is contacted with a stepped portion 14a of 
the journal portion 14, and under this condition a nut 25 is screwed onto 
the male screw portion 11 of the exhaust cam shaft 2 so as to press the 
rotor 17 toward the journal portion 14. The valve timing control mechanism 
16 is fixedly nipped between the journal portion 14 and the nut 25, such 
that rotor 17 is rotated with the exhaust cam shaft 2 as a unit. 
Thereby, six chambers 20 which are separated in the circumferential 
direction at regular intervals and each of which has a pair of 
circumferentially opposed walls 19a1, 19a2 are defined among the rotor 17, 
the housing member 19, the front plate 21 and the rear plate 22. On the 
outer circumferential portion of the rotor 17, six grooves 17a which are 
extended inwardly therefrom in the radial direction and which are 
separated in the circumferential direction at regular intervals are formed 
thereon. Six vanes 18 which are extended outwardly in the radial direction 
into the chambers 20 are mounted in the grooves 17a, respectively. 
Thereby, each of chambers 20 is divided into a first pressure chamber 30 
and a second pressure chamber 31, both of which are separated in a 
fluid-tight manner from each other. 
The rotor 17 is provided with six first passages 28 and six second passages 
29. One end of each of the first passages 28 is communicated with the 
circular groove 13 and the other end of each of the first passages 28 is 
communicated with each of the first pressure chambers 30. On the other 
hand, one end of each of the second passages 29 is communicated with the 
circular groove 12 and the other end of each of the second passages 29 is 
communicated with each of the second pressure chambers 31. The circular 
groove 13 is in communication with a passage 27 which is formed in the 
exhaust cam shaft 2 at its axial center and which is extended in the axial 
direction via a passage 46. The circular groove 12 is in communication 
with a pair of passages 26 which are formed in the exhaust cam shaft 2 so 
as to locate on the coaxial circle about the axial center of the shaft 2 
and which are extended in parallel in the axial direction via passages 45. 
Now, in this embodiment, the passage 27 is formed at the same time as the 
lubrication passage for the journal portions (not shown) which are located 
at the right side of the exhaust cam shaft 2 in FIG. 1. The passage 27 is 
separated from the lubrication passage by a ball 35 which is pressed into 
the lubrication passage and is separated from outside by a ball 34 which 
is pressed into the passage 27. On the other hand, the passages 26 are 
symmetrical about the passage 27 and have the same flow resistance as that 
of the passage 27. Therefore, the passages 26, 27 which have a 
predetermined flow resistance can be obtained by machining without 
increasing the diameter of the cam shaft 2. 
A portion of the exhaust cam shaft which is located between the cylindrical 
portion 10 and the projecting end portion of the exhaust cam shaft 2 is 
rotatably supported on the cylinder head 1 and a cover (not shown) and is 
provided with a circular groove 43. The circular groove 43 is in 
communication with the passages 26. The supporting surfaces of the 
cylinder head 1 and the cover (not shown) for supporting the exhaust cam 
shaft 2 is provided with a circular groove 44. The circular groove 44 is 
in communication with the passage 27 via a passage 47. 
A fluid supplying device 38 is comprised of a changeover valve 39, a fluid 
pump 40 and a controller 41. In this embodiment, the changeover valve 39 
is an electromagnetic valve which is of the four port--three position 
type. The fluid pump 40 is driven by the engine and discharges the fluid 
(oil) for lubricating the engine. The pump 40 may be a pump for 
lubricating the engine. The circular groove 44 is in communication with a 
port A of the changeover valve 39 and the circular groove 43 is in 
communication with a port B of the changeover valve 39. A port P of the 
changeover valve 39 is in communication to a discharge portion the fluid 
pump 40 and a port R of the changeover valve 39 is in communication to a 
reservoir 42. The position of the changeover valve 39 is controlled by the 
controller 41 so that a first condition in which the discharged fluid from 
the pump 40 is supplied to the circular groove 44, and in which the 
circular groove 43 is in communication with the reservoir 42, a second 
condition in which the communication between the circular grooves 43, 44 
and the pump 40 and the reservoir 42 are interrupted, respectively and in 
which the discharged fluid from the pump 40 is supplied to the reservoir 
42 and a third condition in which the discharged fluid from the pump 40 is 
supplied to the circular groove 43 and in which the circular groove 44 is 
in communication with the reservoir 42 are selectively obtained. The 
controller 41 controls the above conditions of the changeover valve 39 
based on parameter signals which are engine speed, the amount of opening 
of a throttle valve (not shown) and so on. 
As shown in FIG. 2 and FIG. 3, a fluid receiving portion la, which is a 
concave portion for reserving the fluid, is formed on the cylinder head 1. 
The fluid receiving portion 1aallows the fluid for lubricating the journal 
portions of the exhaust cam shaft 2 and the intake cam shaft 3 to flow 
therein. In the fluid receiving portion la, a part of the valve timing 
control mechanism 16 is accommodated therein and is always immersed in the 
fluid. Now, in this embodiment, the level of the fluid in the fluid 
receiving portion la is determined to be positioned near the lowest 
portion of the rotor 17 as shown in FIG. 3. 
The operation of the valve timing control device having the above structure 
will now be described. 
With the starting of the engine, the exhaust cam shaft 2 is rotated 
clockwise by the timing pulley 7 as shown in FIG. 2. Thereby, the exhaust 
valves (not shown) are opened and closed. Simultaneously, the rotor 17 is 
rotated and gear 4 is then rotated via the vanes 18, the housing member 19 
and the bolts 23. The rotation of the gear 4 is transmitted to the gear 5 
and the intake cam shaft 3 is then rotated so that the intake valves (not 
shown) are opened and closed. 
The gear 4 is rotatably mounted on the journal portion 14 of the exhaust 
cam shaft 2. Therefore, when the pressurized fluid is supplied from the 
pump 40 to the second pressure chambers 31 by the changeover valve 39 
changed to the third condition via the circular groove 43, the passages 26 
and 45, the circular groove 12 and the second passages 29, the housing 
member 19, the front plate 21 and the second plate 22 are rotated 
clockwise with the gear 4 relative to the exhaust cam shaft 2 as shown in 
FIG. 3 and the intake cam shaft 3 therefore is rotated. Thereby, the valve 
timing control mechanism 16 is in the position of the maximum advanced 
condition in which the vanes 18 are contacted with the walls 19a1 of the 
chambers 20 and in which the angular phase of the intake cam shaft 3 is 
advanced relative to that of the exhaust cam shaft 2 (crank shaft 48) by a 
maximum value .theta. as shown in FIG. 3. In this condition, when the 
pressurized fluid is supplied from the pump 40 to the first pressure 
chambers 30 by the changeover valve 39 changed to the first condition via 
the circular groove 44, the passages 47, 27 and 46, the circular groove 13 
and the first passages 28, the housing member 19, the front plate 21 and 
the second plate 22 are rotated counterclockwise with the gear 4 relative 
to the exhaust cam shaft 2 as shown in FIG. 3. Thereby, the valve timing 
control mechanism 16 is in the position of the maximum retarded condition 
in which the vanes 18 are contacted with the walls 19a2 of the chambers 20 
and in which the angular phase of the intake cam shaft 3 is retarded 
relative to that of the exhaust cam shaft 2 (crank shaft 48) by a maximum 
value .theta. from the above mentioned maximum advanced condition. Now, 
depending on the manner in which the control of the changeover valve 39 is 
executed, the vanes 18 can be stopped in any position (intermediate 
advanced position) between the maximum advanced position and the maximum 
retarded position. This requires that balance be achieved between the 
fluid pressure of the first pressure chambers 30 and the fluid pressure of 
the second pressure chambers 31 when the vanes 18 have achieved an 
arbitrary position. In this intermediate advanced position, the fluid is 
supplied to both of the first and second chambers 30, 31. The amount of 
the advance can therefore be set to any value between a zero level and a 
maximum level. 
As mentioned above, the opening and closing timing of the intake valves 
(not shown) driven by the intake cam shaft 3 is adjusted, and the angular 
phase difference between the crank shaft 48 and the intake cam shaft 3 is 
adjusted. 
Further, in this embodiment, since the only member which requires an axial 
length is the nut 25 except for the valve timing control mechanism 16, and 
therefore the valve timing control mechanism 16 is accommodated in the 
cylinder head 1 without increasing the size of the engine. The valve 
timing control mechanism is not projected outside of the engine (cylinder 
head) enabling the engine to be miniaturized. Thereby, the degree of 
freedom for disposing other devices is increased. Further, since the fluid 
which is leaked to outside of the chambers 20 is collected in the cylinder 
head 1, it is not necessary to strictly determine the fluid-tightness of 
the chambers and therefore additional seal members are not always required 
for sealing the chambers. Accordingly, the valve timing control device can 
be simplified. 
In this embodiment, during the running of the engine, the fluid in the 
fluid receiving portion la is mixed by rotation of the valve timing 
control mechanism 16 and is used to lubricate the gears 4, 5 and so on. 
When the engine is stopped and supplying the fluid to the chambers 20 is 
stopped, even if the fluid in the chambers 20 leaks gradually via the 
contacting portions among the front plate 21, the rotor 17 and the housing 
member 19 and among the rear plate 22, the rotor 17 and the housing member 
19, this leaked fluid is received in the fluid receiving portion la and 
the fluid remains in the chambers 20 which are located in the fluid 
received in the fluid receiving portion la. All of the fluid is not leaked 
from the chambers 20. Therefore, when the engine is started again under 
this condition or after the engine was stopped for a long time, it is 
prevented by the remained fluid that the vanes 18 impact on the walls 19a2 
(19a1) in the chambers 20. Accordingly, noise generated by this impact is 
prevented. 
Further, in this embodiment, the valve timing control mechanism 16 is 
fixedly nipped between the nut 25 and the journal portion 14 of the 
exhaust cam shaft 2. Therefore, the direction for mounting the valve 
timing control mechanism 16 onto the exhaust cam shaft 2 and the direction 
for screwing the nut 25 onto the exhaust cam shaft 2 are the same, and 
therefore the valve timing control mechanism 16 is easily fixed on the 
exhaust cam shaft 2. Accordingly, in the case that maintenance work on the 
valve timing control mechanism 16 is performed, it is easy to detach the 
valve timing control mechanism 16 from the exhaust cam shaft 2. Further, 
it is easy to mount the valve timing control mechanism 16 on the exhaust 
cam shaft 2 so as to be coaxial and the exact phase adjusting operation is 
secured. 
As mentioned above, according to the present invention, since the valve 
timing control device is accommodated in the cylinder head, the valve 
timing control device is not projected outside of the engine (cylinder 
head), the engine is therefore miniaturized. Thereby, the degree of 
freedom for disposing other devices is increased. Further, since the fluid 
which is leaked to outside of the chambers is collected in the cylinder 
head, it is not necessary to strictly determine the fluid-tightness of the 
chambers and therefore additional seal members are not always required for 
sealing the chambers. Accordingly, the structure of the valve timing 
control device is simplified. 
The principles, a preferred embodiment and modes of operation of the 
present invention have been described in the foregoing description. The 
invention which is intended to be protected herein should not, however, be 
construed as limited to the particular forms disclosed, as these are to be 
regarded as illustrative rather than restrictive. Variations and changes 
may be made by those skilled in the art without departing from the spirit 
of the present invention. Accordingly, the foregoing detailed description 
should be considered exemplary in nature and not limited to the scope and 
spirit of the invention as set forth in the appended claims.