Abstract:
A cam shaft phase variable device of an engine in which the attachment angle of a crankshaft and a cam shaft is maintained securely without being shifted by disturbance torque. The device has a drive body of revolution having a tubular section and a guide groove of reducing diameter and rotating relatively to the cam shaft and being driven by a crankshaft, a control body of revolution rotating relatively to the drive body through a rotary operating force imparting means and having the outer circumferential surface supported by the inner circumferential surface of the tubular section, an eccentric circular cam rotating synchronously, a movable member for displacing the guide groove, a cam guide intersecting the central axis perpendicularly and displaced by the eccentric circular cam, and an intermediate body of revolution displacing in the direction intersecting the cam guide perpendicularly while being supported on, and rotating integrally with, the camshaft.

Description:
TECHNICAL FIELD 
     This invention relates to a phase varying device for use with an automobile engine equipped with a camshaft and a coaxial torque means for rotating a rotary drum in the forward or backward direction relative to the crankshaft of the engine so as to advance or retard the rotational phase of the camshaft relative to the crankshaft, thereby varying the valve timing of the engine. The relative rotational direction of the camshaft to advance/retard the phase angle thereof will be referred to phase advancing/retarding direction. 
     BACKGROUND ART 
     There has been known a valve timing control device for an automobile engine as disclosed in Patent Document 1 cited below. The device of Patent Document 1 has a drive plate 3 rotatably mounted on a camshaft 1 of the device and driven by the crankshaft of the engine; a driven shaft member 9 integrally mounted on the camshaft 1 and having on the periphery thereof a conversion guide 11 spaced apart at a distance from the front end of the drive plate 3; and an intermediate rotor 5 rotatably mounted on the driven shaft member 9 via a bearing 14 ahead of the conversion guide 11. 
     Each of the drive plate 3, driven shaft member 9, and intermediate rotor 5 is provided with radial guides 10 in the form of radial grooves, guide bores 12 skewed with respect to the circumference, a spiral guide 15, and balls 16 that can roll in the guides (10, 12, 15). The intermediate rotor 5 is rotated relative to the driven shaft member 9 as the yoke 19 integrated with the intermediate rotor 5 is driven by magnetic forces exerted by electromagnetic coils 22 a  and 22 b.    
     In the device of Patent Document 1, as the intermediate rotor 5 is rotated relative to the driven shaft member 9 by magnetic forces in the phase retarding direction, the balls 16 roll in the spiral guide 15 and is displaced radially inwardly in the respective radial guides 10, thereby performing a cam action on the conversion guide 11, which in turn causes the driven shaft member 9 integral with the camshaft 1 to be advanced in phase relative to the drive plate 3. On the other hand, as the intermediate rotor 5 is rotated in the phase advancing direction relative to the driven shaft member 9 under the magnetic forces, the balls 16 roll in the respective guides 15, 10, and 11 in the opposite direction, performing a cam action on the conversion guide 11 in the opposite direction to retard the phase of the driven shaft member 9 relative to the drive plate 3. 
     DISCLOSURE OF THE INVENTION 
     Problems to be Solved by the Invention 
     In the Patent Document 1, the camshaft in operation is subjected to external disturbing torques arising from valve spring reactions. In the device of Patent Document 1, the balls 16 tend to roll in the guide bores 12 under a disturbing torque, and hence the disturbing torque is likely to invite an erroneous phase variation between the drive plate and camshaft and hence incorrect intake/exhaust valve timing. 
     In view of such problem as mentioned above, the inventors of the present invention were directed to provide a phase variable device for automobile engine equipped with a self-locking structure for immovably locking the members that correspond to the camshaft and drive plate of Patent Document 1 even under disturbing torques. The device has been filed as an International Patent Application, PCT/JP2008/51763, which will be referred to as Prior Application 1. 
     The phase variable device of Prior Application 1 is provided with an intermediate rotor 33 integral with the camshaft 30 (connected to center shaft 32), a first rotor 31 (corresponding to the drive plate 3 of Patent Document 1), and a second rotor 35, both rotated by the crankshaft. In the phase variable device of Prior Application 1, when the second rotor 35 is acted upon by a torque exerted by an electromagnetic clutch 34 (coil spring 59), the first circular eccentric cam 53 of a circular eccentric cam 36 slides in an elongate bore 56. As a consequence, a cam guide plate 37 is moved together with slide pins 40 along the guide pins (48-51) provided at the opposite ends of the elongate bore 56 in the direction perpendicular to the rotational axis L1 of the camshaft. As the slide pins 40 are displaced in the radially decreasing oblique guides 39 formed in the first rotor 31, the camshaft 30 and intermediate rotor 33 rotate relative to the first rotor 31 (coupled to the crankshaft), which causes the phase of the camshaft relative to the crankshaft to change. 
     On the other hand, the self-locking structure of Prior Application 1 is configured as follows: Firstly, when the camshaft 30 is acted upon by an external disturbing torque exerted by a valve spring, the intermediate rotor 33 is rotated by the torque relative to the first rotor 31. Since in this instance the slide pins 40 are acted upon by forces exerted by the respective oblique guides 39, the cam guide plate 37 is subjected to a force acting in the direction perpendicular to the rotational axis L1. As the first circular eccentric cam 53 is subjected to a force exerted by the elongate bore 56, and as a second circular eccentric bore 52 is subjected to a force exerted by a second circular eccentric cam 54 integral with the first circular eccentric cam 53, the second rotor 35 is acted upon by a force acting in the direction perpendicular to the rotational axis L1. 
     As a consequence of the external disturbing torque applied to the camshaft 30, the circumference 35 a  of the second rotor 35 comes into touch with the inner circumference 33 d  of the cylindrical section of the intermediate rotor 33, and gives rise to a frictional force between them. This frictional force automatically brings the second rotor 35 and intermediate rotor 33 in a mutually unrotatable locked condition (such locking hereinafter referred to as self-locking). 
     Thus, the self-locking structure of Prior Application 1 maintains the second rotor 35 and intermediate rotor 33 mutually unrotatable under an external disturbing torque, thereby prohibiting any phase error between the camshaft and the crankshaft. 
     However, in the phase variable device of Prior Application 1, the second rotor 35 is in contact with the interior of the intermediate rotor 33 and the circular eccentric cam 36 is rotatably mounted, via a circular bore 55, on the cylindrical section 32 d  formed at the leading end of the center shaft 32 (which is integral with the camshaft 30). 
     As a consequence, in the phase variable device of Prior Application 1 under an external disturbing torque, the cam guide plate 37 is subjected to a force in the direction perpendicular to the rotational axis L1. The force is transmitted to the first circular eccentric cam 53, which may cause the circular hole 55 of the first circular eccentric cam 53 to come into contact with the cylindrical section 32 d  and generate a torque that acts on the first circular eccentric cam 53 as well as on the second circular eccentric cam 54 integral with the first circular eccentric cam 53 before a local friction is generated between the outer circumference of the second rotor 35 a  and the inner circumference 33 d  of the intermediate rotor 33. If such a torque acts on the second circular eccentric cam 54, the second rotor 35 is subjected to a force exerted by the second circular cam 54 in the rotational direction. 
     In other words, in the device of Prior Application 1, if an external disturbing torque is applied to the second rotor 35, a local friction is not promptly generated, or only a negligible local friction takes place, between the second rotor 35 and intermediate rotor 33. As a consequence, in the device of the Prior Application, the self-locking function does not properly take place, thereby resulting in a possible phase error between the camshaft 30 and first rotor 31. 
     On the other hand, the force exerted to the second rotor 35 has a component in the direction perpendicular to the rotational axis L1. This component is transmitted to the first contact point where the elongate bore 56 comes into contact with the first circular eccentric cam 53, and further to the center axis L3 of the first circular eccentric cam 53. The force is further transmitted to the center axis L2 of the second circular eccentric cam 54 and results in a friction at the point where intermediate rotor 33 is in contact with the inner circumference 33 d . (Such contact point where friction takes place will be referred to as point of action). This frictional force furnishes self-locking function. 
     The magnitude of the torque of the above-mentioned frictional force is given by μ*Fcosq, where F is the component of the force acting on the above-mentioned first contact point in the direction towards the point of action (where the frictional force takes place), q is the angle (referred to as friction angle) between the force F and the line connecting the rotational axis L1 and the point of action, and μ is the coefficient of friction. This frictional force increases with decreasing friction angle q. Thus, in the device of Prior Application 1, in order to furnish a large frictional force for the self-locking function, the eccentric radius d1 of the second circular eccentric cam 54 be set smaller than the eccentric radius d2 of the first circular eccentric cam 53. 
     However, since the circular eccentric cam 36 consists of the first and second circular eccentric cams (53 and 54) integrated together, it has a rather complex configuration. Further, the second rotor 35 and circular eccentric cam 36 are supposedly separate members that the second circular eccentric cam 54 and circular eccentric bore 52 must be manufactured at a high precision. Thus, the device of the Prior Application disadvantageously requires many costly parts. 
     In view of the problems pertinent to Prior Application 1, it is an object of the present invention to provide an improvement in a phase variable device for an automobile engine: the improvement lying in enhancement of the self-locking structure such that an inadvertent phase error between the crankshaft and the camshaft will be prevented if an external disturbing torque is transmitted to the camshaft. 
     Means for Solving the Problem 
     To achieve the object above, the present invention provides a phase variable device for an automobile engine, comprising: 
     a cylindrical section; 
     a drive rotor having curved guide slits each extending in the circumferential direction of the cylindrical section with the radii thereof continuously decreasing, the drive rotor being rotatable relative to the camshaft and driven by the crankshaft of the engine; 
     a control rotor having an outer circumference in contact with, and supported by, the inner circumference of the cylindrical section, the control rotor driven by a torque means for rotation relative to the drive rotor; 
     a circular eccentric cam rotatable about the center axis of the camshaft in synchronism with the control rotor; 
     movable members in engagement with, and movable in, the respective guide slits; and 
     an intermediate rotor having a cam guide in the form of a groove that extends in the direction perpendicular to the center axis of the camshaft to allow the circular eccentric cam to slide therein, the intermediate rotor being mounted on the camshaft such that the intermediate rotor is rotatable together with the camshaft but movable in the direction perpendicular to the camshaft. 
     Under a given initial condition, the control rotor rotates together with the intermediate rotor which is integral with the camshaft and with the drive rotor driven by the crankshaft. The control rotor is rotated by the torque means relative to the camshaft. The phase angle of the camshaft (or intermediate rotor) relative to the crankshaft (or drive rotor) may be varied in the phase advancing direction (which is the rotational direction of the drive rotor) or in the phase retarding direction (which is the direction opposite to the rotational direction of the drive rotor) in accordance with the direction of the relative rotation of the control rotor. 
     In other words, as the control rotor is put in a relative rotation, the circular eccentric cam slides in the cam guide. At the same time, the intermediate rotor and the movable member are moved in the direction perpendicular to the longitudinal direction of the cam guide. The phase angle of the camshaft relative to the crankshaft is varied by the displacement of the movable member in the curved guide slits and the resultant relative rotation of the intermediate rotor relative to the drive rotor. On the other hand, if an external disturbing torque is transmitted from a valve spring to the camshaft, the movable member and the intermediate rotor are acted upon by a force, via the curved guide slits, in the direction perpendicular to the longitudinal direction of cam guide. This force is transmitted from the cam guide to the circular eccentric cam and further therefrom to the control rotor, so that the control rotor is slightly displaced in the direction perpendicular to the longitudinal direction of the cam guide. As a consequence, the circumference of the control rotor is pushed against the inner circumference of the cylindrical section of the drive rotor, thereby giving rise to a local frictional force. That is, the phase variable device of the present invention automatically sets up the drive rotor and the control rotor in mutually immovable condition, thereby rendering the crankshaft (drive rotor) and camshaft (intermediate rotor) locked together without causing any phasic error between them. 
     On the other hand, since the circumference of the control rotor is supported by the inner circumference of the cylindrical section of the drive rotor, it is not necessary to mount the control rotor on the camshaft. Thus, the camshaft and the control rotor can be spaced apart and not in contact with each other, so that the control rotor is not subjected to a rotational force that arises from an external disturbing torque. As a result, a local frictional force takes place promptly between the control rotor and the drive rotor. 
     In achieving the object mentioned above, the circular eccentric cam of the phase variable device may be integrated with the control rotor. 
     By integrating the circular eccentric cam with the control rotor, the force exerted by the cam guide to the circular eccentric cam at their contact point (point of effort) has a component that lies in the direction perpendicular to the common rotational axis (which is the common to the drive rotor, intermediate rotor, and control rotor) and acts on the point of contact (point of action) between the cam guide and the circular eccentric cam. The direction does not pass through the center axis of the circular eccentric cam. Thus, this force gives rise to a local frictional force at the point of contact between the circumference of the control rotor and the inner circumference of the cylindrical section of the drive rotor. In this case, the distance from the point of effort (contact point between the cam guide and the circular eccentric cam) to the point of action is longer as compared with the corresponding distance in the case where the direction of the component passes through the center axis of the circular eccentric cam. This implies that the friction angle is smaller in the former case. Accordingly, the phase variable device can operate with a smaller friction angle and gives rise to a larger local frictional force for self-locking function without using coaxial circular eccentric cams in combination as in Prior Application 1. 
     It is noted that, through integration of the control rotor and the circular eccentric cam, the phase variable device can have a simpler structure and less elements as compared with a multi-element device. 
     In the phase variable device of the present invention, a local frictional force caused by an external disturbing torque is promptly transmitted to the intermediate rotor  33  without being damped. As a result, the self-locking function can effectively prevent a phase error from occurring between the camshaft and crankshaft. 
     The phase variable device can have a still smaller friction angle and hence an enhanced local frictional force due to an external disturbing torque. As a result, the self-locking function of the device can effectively prevent a phase error from occurring between the camshaft and crankshaft. Further, the inventive device has a less number of simplified elements, and hence can be manufactured at a lower cost. 
     The invention will now be described in detail by way of example with reference to the accompanying drawings. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is an exploded perspective view as seen from the front of a camshaft phase variable device for an automobile engine in accordance with an embodiment of the invention. 
         FIG. 2  is a front view of the device. 
         FIG. 3  shows the axial cross section of the device taken along line A-A of  FIG. 2 . 
         FIG. 4  shows radial cross sections taken at different axial positions of the device having no phase change. More particularly,  FIG. 4(   a ) shows the cross section taken along line B-B,  FIG. 4(   b ) the cross section taken along line C-C, and  FIG. 4(   c ) the cross section taken along line D-D of  FIG. 3 . 
         FIG. 5  shows cross sections of the device after a phase change has occurred, the cross section taken along the same lines as in  FIG. 4 . 
         FIG. 6(   a ) illustrates a self-locking structure comprising a first control rotor and a drive rotor, and  FIG. 6(   b ) shows another self-locking structure in which a first control rotor and another member constitute a circular eccentric cam. 
         FIG. 7  shows radial cross sections of the device having no phase change. More particularly,  FIG. 7(   a ) shows the cross section taken along line E-E of  FIG. 3 ,  FIG. 7(   b ) the cross section taken along line F-F of  FIG. 3 , and  FIG. 7(   c ) the cross section taken along line G-G. 
         FIG. 8  shows cross sections taken along the same lines as in  FIG. 6  of the device after a phase change has occurred. 
     
    
    
     DETAILED DESCRIPTION  
     In use the camshaft phase variable device of the invention is installed integral with an internal combustion engine. The device is adapted to transmit the rotational motion of the crankshaft to a camshaft so as to open/close an intake valve/exhaust valve while varying the valve timing of the intake valve/exhaust valve in accordance with such operating conditions as the load and rpm of the engine. 
     Referring to  FIGS. 1 through 8 , there is shown a phase variable device in accordance with the first embodiment of the invention. For convenience, the term “front” section refers to the section of the device having a second electromagnetic clutch  90  (described in detail below), while the section having a sprocket  71   a  will be referred to as the “rear” section. The device is provided with: a drive rotor  71  driven by the crankshaft (not shown) of the engine; a center shaft  72  fixedly mounted on a coaxial camshaft (not shown) for rotatably supporting the drive rotor  71 ; an intermediate rotor  73  mounted on the center shaft  72  ahead of the drive rotor  71  such that the intermediate rotor  73  is unrotatable relative to the center shaft  72  but rotatable relative to the drive rotor  71 ; a first control rotor  74  (which is equivalent to the control rotor defined in claim  1 ) with its circumference supported by the drive rotor  71  such that the first control rotor  74  is rotatable relative to the center shaft  72  without touching the center shaft  72 ; and a first electromagnetic clutch  75  securely fixed to an engine casing (not shown), for braking the first control rotor  74 , all aligned to the same rotational axis L 1 . 
     The first control rotor  74  has on the backside thereof a circular eccentric cam  76  ( FIGS. 3 and 4(   a )) that rotates together with the control rotor  74  about the rotational axis L 1 . The intermediate rotor  73  is provided on the front end thereof with a cam guide  77  that receives thereon the circular eccentric cam  76 . As the circular eccentric cam  76  rotates, the intermediate rotor  73  reciprocates in the direction perpendicular to both the rotational axis L 1  and the wall of the cam guide  77 . 
     The center shaft  72  unrotationaly coupled to the camshaft (not shown) by securely fixing the leading end of the camshaft in the bore  72   a  formed in the center shaft  72 . The drive rotor  71  consists of a sprocket  71   a  and a drive cylinder  71   b  coupled together with a multiplicity of coupling pins  78 . The drive rotor  71  is rotatably mounted on the cylindrical section  72   c  formed on the rear end of a flange  72   b  of the center shaft  72  by rotatably fitting the cylindrical section  72   c  in the hole  71   c  formed in the sprocket  71   a . The drive cylinder  71   b  has a bottom having a guide slit system  79  consisting of a pair of curved guide slits  79   a  and  79   b  extending in substantially the circumferential direction about the rotational axis L 1 . As shown in  FIG. 4 , the guide slits  79   a  and  79   b  are formed in the opposite sides of the rotational axis, with their radii continuously decreasing towards the rotational direction D 1  of the drive rotor  71  (clockwise direction D 1  as viewed from front). It should be understood that the radially inwardly decreasing guide slit  79   a  can decrease its radius in the counterclockwise direction D 2 , as described later. 
     The first intermediate rotor  73  is generally a disk having a pair of faces perpendicular to the rotational axis L 1 . The first intermediate rotor  73  is provided on the front face thereof with a cam guide  77  adapted to receive thereon the circular eccentric cam  76 . The cam guide  77  has a bottom face perpendicular to the rotational axis L 1  and the sidewall thereof. The bottom face has a generally square elongate hole  80 . The first intermediate rotor  73  is mounted on the flat engaging face  72   d  of the center shaft  72  unrotatably relative to the center shaft  72 , but is supported by the center shaft  72  slidable in the longitudinal direction of the elongate hole  80 . 
     The first intermediate rotor  73 , first control rotor  74 , and circular eccentric cam  76  are arranged inside the drive cylinder  71   b . The first control rotor  74  is provided at the center thereof with a through-hole  74   a  for allowing the cylindrical section  72   e  of the center shaft  72  to pass through it without touching it. 
     The inner diameter of the through-hole  74   a  is larger than the outer diameter of the cylindrical section  72   e  of the center shaft  72 . Between the cylindrical section  72   e  so as to provide an annular space  96  between the center shaft  72  and the cylindrical section  72   e . The first control rotor  74  is slightly moved in the direction perpendicular to the rotational axis L 1  by the self-locking structure, as described later. Thus, in order to prevent the cylindrical section  72   e  from touching the inner circumference of the through-hole  74   a  while moving, the space  96  is formed larger than the movable distance of the first control rotor  74 . Then, under the self-locking condition, the first control rotor  74  touches the cylindrical section  72   e  without being subjected to a torque that causes rotation. As a consequence, the outer circumference  74   b  and the inner circumference  71   d  are securely self-locked. 
     The circular eccentric cam  76  integrally formed on the rear face of the first control rotor  74  has a center axis L 2  offset from the rotational axis L 1  by a distance d 0 . The first control rotor  74  is also a disk having an outer circumference  74   b , which is set to be in substantial contact with, and supported by, the stepped inner circumference  71   d  formed inside the drive cylinder  71   b.    
     The self-locking function that takes place between the first control rotor  74  and drive rotor  71  will now be described. The outer circumference  74   b  of the first control rotor  74  is in contact with, and supported by, the inner circumference  71   d  of the drive cylinder  71 . The self-locking function arises from the local friction between the outer circumference  74   b  of the first control rotor  74  and the inner circumference  71   d  of the drive rotor  71   d  of the drive rotor  71 . As shown in  FIG. 6(   a ), when the camshaft (not shown) is subjected to a torque caused by an external disturbance, the circular eccentric cam  76  is subjected to a force acting on the point of effort P 1  in the direction perpendicular to the extension line of the cam guide  77  and to the rotational axis L 1  (the point of effort being the point where the circular eccentric cam  76  is in contact with the cam guide  77 ). 
     The first control rotor  74 , which is integral with the circular eccentric cam  76 , is moved by the force F 0  until the outer circumference  74   b  comes into contact with the inner circumference  71   d  of the drive rotor  71   b  at the point of action P 2 . A force F acts on this point of action P 2  in the direction from the point P 1  to the point P 2 . Denoting by q the angle (referred to as friction angle) between the force F and the line L 4  passing through the rotational axis L 1  and the point of action P 2 , the component of F that causes the drive rotor  71  and the first control rotor  74  to rotate relative to each other and gives rise to a phase variation between the camshaft and the crankshaft equals Fsinq, as shown in  FIG. 6(   a ). On the other hand, the reaction exerted by the drive cylinder  71   b  and acting on the first control rotor  74  equals Fcosq. Thus, assuming that the frictional coefficient between the outer circumference  74   b  and the inner circumference  71   d  is m, a local frictional force of mFcosq acts on the point of action P 2 . This frictional force furnishes the self-locking function. It is noted that the self-locking function does not take place unless the frictional force is larger than the force that causes the phase variation. In other words, the self-locking function becomes effective in the respective embodiments when the following condition is satisfied.
 
Fsinq&lt;mFcosq
 
or if the friction angle q satisfies the condition
 
 q &lt;tan −1   m.  
 
       FIG. 6(   b ) illustrates a case where the circular eccentric cam  76  and the first control rotor  74  are separate members. When the circular eccentric cam  76  is slidably supported by the circular hole  74   e  formed in the first control rotor  74 , the force F 0  due to an external disturbing torque acts on the center axis L 0  of the circular eccentric cam  76 . In this case, the distance from the force of effect L 0  to the point of action P 2  is shorter than the distance from the point of effort P 1  to the point of action P 2 , and the friction angle q is larger than that of the case where the circular eccentric cam  76  and first control rotor  74  are formed integral. Then the local frictional force is disadvantageously reduced in the former case (mFcosq 1 &lt;mFcosq), which is not preferable for self-locking function. Therefore, it is preferred from the point of self-locking function to integrate the circular eccentric cam  76  and first control rotor  74  to reduce the friction angle q. 
     Thus, in the phase variable device of the first embodiment, the circular eccentric cam  76  and first control rotor  74  are integrated together, so that the point of effort P 1  is located at the contact point between the cam guide  77  and the circular eccentric cam  76 , instead of the center axis L 0  of the circular eccentric cam  76 . Accordingly, the self-locking function is enhanced as compared with Prior Application 1. It is noted that the profile of the circular eccentric cam  76  is not limited to a circle as in the present embodiment, but it may be of any cam configuration. 
     The first intermediate rotor  73  has a pair of movable members  81  extending rearward from a pair of engagement bores  73   a . Each of the movable members  81  is formed of a thinner shaft  81   a  inserted in a thicker hollow cylindrical shaft  81   b . The thinner shafts  81   a  engages the engagement bores  73   a , while the thicker hollow cylindrical shaft  81   b  are movably fitted in a pair of substantially circumferential guide slits  79   a  and  79   b  formed in the drive cylinder  71   b.    
     The first control rotor  74  is provided on the front end thereof with a torque means  100 . The torque means  100  has a first electromagnetic clutch  75  for rotating the first control rotor  74  relative to the intermediate rotor  73  and drive rotor  71 , and a reverse mechanism for rotating the first control rotor  74  in the reverse direction. The first electromagnetic clutch  75  is provided on the rear end thereof with a friction member  82 , which is arranged to face the front end of the first control rotor  74 . When the coil  75   a  of the electromagnetic clutch  75  is energized, the contact face  74   c  of the first control rotor  74  is brought into sliding contact with the friction member  82 , thereby braking the rotational motion of the first control rotor  74 . 
     The reverse mechanism includes a first ring member  83  disposed ahead of the first control rotor  74 , second intermediate rotor  84 , movable member  85 , second ring member  86 , second control rotor  87 , shim  88 , holder  89 , and second electromagnetic clutch  90 . Together with the first electromagnetic clutch  75 , the reverse mechanism constitutes the torque means  100  of claim  1 . 
     The first control rotor  74  is a generally hollow cylinder having a bottom, wherein the bottom has a stepped first circular eccentric bore  74   d  whose center axis L 2  is offset from the rotational axis L 1  by a distance d 1 . The first ring member  83  is slidably fitted in the circular eccentric bore  74   d . The first ring member  83  has a first engagement hole  83   a.    
     The second intermediate rotor  84  is provided at the center thereof with a square hole  84   a  and a substantially radial guide slit (hereinafter simply referred to as radial guide slit)  84   b  outside the square hole  84   a . The second intermediate rotor  84  is securely fixed to the center shaft  72  by fitting the second flat engagement faces  72   f  and  72   g  of the center shaft  72  in the square hole  84   a.    
     The second control rotor  87  is rotatably mounted on the center shaft  72  by fitting the small cylindrical section  72   h  formed at the leading end of the center shaft  72  in the circular hole  87   a  formed at the center of the second control rotor  87 . The second control rotor  87  is provided in the rear end thereof with a stepped circular eccentric bore  87   b , whose center axis L 3  is offset from the rotational axis L 1  by a distance d 1  in a manner similar to the first circular eccentric bore  74   d . Slidably fitted in the second circular eccentric bore  87   b  is the second ring member  86 . The second ring member  86  is provided on the rear end thereof with a second engagement hole  86   a.    
     The movable member  85  comprises a thin shaft  85   a  coaxially fitted in a thick hollow shaft  85   b . The opposite ends of the thin shaft  85   a  are slidably fitted in the first and second engagement holes  83   a  and  86   a , respectively. The thick hollow shaft  85   b  is movably fitted in the radial guide slit  84   b  of the second intermediate rotor  84 . 
     The first and second ring members  83  and  86  are rotatably fitted in the first and second circular eccentric holes  74   d  and  87   b , respectively, such that the center axes L 2  and L 3  of the first and second ring members  83  and  86 , respectively, are located symmetrically across the phantom extension line L 4  of the radial guide slit  84   b.    
     The shim  88  is fitted in the stepped circular bore  87   c  formed in the front end thereof. A holder  89  is mounted on the small cylindrical section  72   h  of the center shaft  72  that protrudes forward from the circular hole  87   a . Those elements arranged between the holder  89  and the drive cylinder  71   b  inclusive are securely fixed on the camshaft (not shown) by a screw inserted from front into the camshaft (not shown) through the central holes formed in these elements. The second electromagnetic clutch  90  is securely fixed to the engine casing (not shown) in front of the front end of the second control rotor  87 . When the coil  90   a  of the second electromagnetic clutch  90  is energized, the contact face  87   d  of the front end of the second control rotor  87  is attracted onto the friction member  91  so as to brake the second control rotor  87  in rotation. 
     It is preferable to make the contact face  87   d  of the second control rotor  87  flush with the contact face  74   c  of the first control rotor  74  as shown in  FIG. 3 , since if the second control rotor  87  is disposed inside the coil  75   a , the second control rotor  87  can be also magnetized and become instabilized by the first electromagnetic clutch  75  in braking operation. 
     The movable members  81  and  85  may be configured to have bearings or may be replaced by balls so that they can roll in the guide slit system  79  and in the radial guide slit  84   b  as they move. Then, the movable members  81  and  85  can move much easier with reduced friction, thereby saving electric energy consumed by the electromagnetic clutches. 
     The second intermediate rotor  84  is preferably made of a non-magnetic material. If the second intermediate rotor  84  is made of a non-magnetic material, it prevents the magnetic field attracting one of the control rotors  74  and  87  from being transmitted to the other control rotor via the second intermediate rotor  84 , thereby preventing both of the control rotors from being attracted together. 
     Referring to  FIG. 1  and  FIGS. 4 through 8 , operation of the camshaft phase variable device will be described for a case where the relative phase angle between the drive rotor  71  and the camshaft (not shown) is varied. When the drive rotor  71  is in phase with the camshaft (not shown) under the initial condition and rotates in the clockwise direction D 1  as viewed from the front end of the device, the first intermediate rotor  73 , control rotor  74  (circular eccentric cam  76 ), intermediate rotor  84 , and control rotor  87  rotate together with the drive rotor  71  in the same clockwise direction D 1 . 
     To advance the phase angle of the camshaft (in the clockwise direction D 1 ) relative to the drive rotor  71  the second control rotor  87  is braked by the second electromagnetic clutch  90 . If the second electromagnetic clutch  90  is enabled, the first and second ring members  83  and  86 , respectively, move from the positions shown in  FIG. 7  to the positions shown in  FIG. 8 . Thus, the second control rotor  87  is retarded in phase, that is, rotated in the counterclockwise direction D 2  (as viewed from the front end of the device), relative to the second intermediate rotor  84  and first control rotor  74 . In that event, as the second ring member  86  slides in the circular eccentric bore  87   b  in D 1  direction, the movable member  85  moves in the radial guide slit  84   b  radially inwardly (that is, in D 3  direction as shown in  FIG. 6(   b )). As the movable member  85  moves radially inwardly in the radial guide slit  84   b , the first ring member  83  exerts a torque on the first control rotor  74  in D 1  direction while sliding in the first circular eccentric bore  74   d  in D 2  direction. The first control rotor  74  rotates in the phase advancing direction (D 1  direction) relative to the second intermediate rotor  84  and second control rotor  87 . 
     At the same time, the first control rotor  74  rotates in D 1  direction relative to the first intermediate rotor  73  and drive rotor  71 , while the circular eccentric cam  76  integral with the first control rotor  74  eccentrically rotates in the clockwise direction D 1  about the center axis L 1  as shown in  FIG. 4 . As the circular eccentric cam  76  undergoes an eccentric rotation while sliding on the inner circumference of the cam guide  77 , the first intermediate rotor  73  and movable members  81  move downward in the longitudinal direction D 3  of the elongate square hole  80  as shown in  FIG. 4 . 
     As the movable members  81  go down, the first intermediate rotor  73  is displaced in the guide slits  79   a  and  79   b  in the D 1  direction, so that the first intermediate rotor  73  is rotated in D 1  direction relative to the drive rotor  71 , thereby displaced from the position shown in  FIG. 4  to the position shown in  FIG. 5 . As a consequence, the phase angle of the camshaft (not shown) in phase with the intermediate rotor  73  in rotation is advanced in D 1  direction relative to the drive rotor  71 . 
     On the other hand, to return the phase angle of the camshaft in the phase retarding direction D 2  relative to the drive rotor  71 , the first electromagnetic clutch  75  is activated to put the brake on the first control rotor  74 . Then the circular eccentric cam  76  integral with the braked first control rotor  74  is rotated in the counterclockwise direction D 2  relative to the drive rotor  71  and first intermediate rotor  73  as shown in  FIG. 5 , thereby moving the first intermediate rotor  73  and movable members  81  in the upward direction D 4  as shown in  FIG. 5 . As the movable members  81  are moved upward, the first intermediate rotor  73  is displaced in the guide slit system  79  in D 2  direction and hence rotated in D 2  direction relative to the drive rotor  71 , thereby returning from the position shown in  FIG. 5  to the position shown in  FIG. 4 . As a consequence, the phase of the camshaft rotating in synchronism with the first intermediate rotor  73  is retarded in D 2  direction relative to the drive rotor  71  driven by the crankshaft.