VALVE TIMING CONTROL APPARATUS OF INTERNAL COMBUSTION ENGINE
In a valve timing control apparatus employing a helical torsion spring attached at one end to a vane rotor and attached at the other end to a housing, for biasing the vane rotor relative to the housing in a specified phase-change direction under a preload, adjacent coils of the torsion spring being brought into contact with each other at a part of the torsion spring in a circumferential direction under a state where the torsion spring is loaded, a back-pressure relief passage is configured to discharge working oil in a back-pressure chamber of a lock mechanism. The back-pressure relief passage is provided at a predetermined circumferential position that goes across a coil-to-coil contact part that the adjacent coils of the torsion spring are brought into contact with each other when the vane rotor rotates relative to the housing by a maximum angular displacement.
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The present invention relates to a valve timing control apparatus of an internal combustion engine configured to variably control valve timing of an engine valve (intake and/or exhaust valves) depending on an operating condition of the engine.
BACKGROUND ARTOne such valve timing control (VTC) apparatus has been disclosed in Japanese Patent Provisional Publication No. 2005-325749 (hereinafter is referred to as “JP2005-325749”). In the VTC apparatus disclosed in JP2005-325749, a helical torsion spring is interleaved between a housing and a vane rotor such that the centerline of the helical torsion spring is arranged to be substantially coaxial with the rotation axis of the rotor, for enabling a biasing force of the torsion spring to act the rotor to oppose the rotating load of the rotor relative to the housing, produced by a valve-spring reaction force (i.e., a force acting to phase-retard an angular phase of a camshaft relative to an engine crankshaft) during operation of the valve operating system of the engine. This contributes to superior operating characteristic and enhanced responsiveness of the VTC apparatus.
SUMMARY OF THE INVENTIONHowever, when the helical torsion spring is loaded in its winding direction, the torsion spring deforms, so that the distance between adjacent coils (adjacent turns of wire) of a certain circumferential part of the coiled spring portion of the torsion spring narrows and the distance between the adjacent coils of the diametrically-opposed part of the coiled spring portion widens. At this time, the deformed helical torsion spring tends to incline with respect to the axis (the centerline) of the torsion spring. As a result of this, in the case of the prior-art VTC apparatus, a coil-to-coil contact tends to occur at the circumferential part of the coiled spring portion having the narrowed coil-to-coil distance. Such a coil-to-coil contact leads to the problem of undesirable wear of the helical torsion spring.
It is, therefore, in view of the previously-described drawbacks of the prior art, an object of the invention to provide a valve timing control (VTC) apparatus of an internal combustion engine configured to suppress a helical torsion spring from being worn owing to a coil-to-coil contact, even in the presence of occurrences of the coil-to-coil contact of the torsion spring, loaded and deformed during operation of the VTC apparatus.
In order to accomplish the aforementioned and other objects of the present invention, a valve timing control apparatus of an internal combustion engine comprises a housing adapted to be driven by a crankshaft of the engine, and configured to define a plurality of working-fluid chambers therein by partitioning an internal space by a plurality of shoes protruding radially inward from an inner peripheral surface of the housing, a vane rotor having a rotor adapted to be fixedly connected to a camshaft and a plurality of radially-extending vanes formed on an outer periphery of the rotor for partitioning each of the working-fluid chambers of the housing by the shoes and the vanes to define phase-advance working chambers and phase-retard working chambers, the vane rotor being configured to phase-advance relative to the housing by supplying hydraulic pressure to each of the phase-advance working chambers and by discharging working oil in each of the phase-retard working chambers and configured to phase-retard relative to the housing by supplying hydraulic pressure to each of the phase-retard working chambers and by discharging working oil in each of the phase-advance working chambers, and also configured to have a cylinder structural bore formed in at least one of the plurality of vanes as a through hole extending in a direction of a rotation axis of the vane rotor, a lock mechanism having a lock member slidably installed in the cylinder structural bore and a biasing member for biasing the lock member in its extended direction from the vane rotor, the lock mechanism being configured to permit the lock member to be displaced in its retracted direction against a biasing force of the biasing member by hydraulic pressure acting on the lock member, an engaging recess formed in the housing so as to oppose the lock member, for restricting rotary motion of the vane rotor relative to the housing by bringing the lock member into engagement with the engaging recess with sliding motion of the lock member in the extended direction, a helical torsion spring attached at one end to the vane rotor and attached at the other end to the housing, for exerting a biasing force on the vane rotor and for biasing the vane rotor relative to the housing in a specified phase-change direction under a preload of the torsion spring, adjacent coils of the torsion spring being brought into contact with each other at a part of the torsion spring in a circumferential direction under a state where the torsion spring is loaded, and a back-pressure relief passage through which a back-pressure chamber, configured to install the biasing member of the lock mechanism, is communicated with an exterior space of the housing, the back-pressure relief passage configured to open toward the torsion spring, wherein the back-pressure relief passage is provided at a predetermined circumferential position that goes across a coil-to-coil contact part that the adjacent coils of the torsion spring are brought into contact with each other when the vane rotor rotates relative to the housing by a maximum angular displacement.
According to another aspect of the invention, a valve timing control apparatus of an internal combustion engine comprises a driving rotary member adapted to be driven by a crankshaft of the engine, a driven rotary member adapted to be fixedly connected to a camshaft and configured to phase-change relative to the driving rotary member by supplying or discharging working oil, and also configured to have a cylinder structural bore formed to extend in a direction of a rotation axis of the driven rotary member, a lock mechanism having a lock member slidably installed in the cylinder structural bore and a biasing member for biasing the lock member in its extended direction from the vane rotor, the lock mechanism being configured to permit the lock member to be displaced in its retracted direction against a biasing force of the biasing member by hydraulic pressure acting on the lock member, an engaging recess formed in the driving rotary member so as to oppose the lock member, for restricting rotary motion of the driven rotary member relative to the driving rotary member by bringing the lock member into engagement with the engaging recess with sliding motion of the lock member in the extended direction, a helical torsion spring attached at one end to the driven rotary member and attached at the other end to the driving rotary member, for exerting a biasing force on the vane rotor and for biasing the vane rotor relative to the housing in a specified phase-change direction under a preload of the torsion spring, adjacent coils of the torsion spring being brought into contact with each other at a part of the torsion spring in a circumferential direction under a state where the torsion spring is loaded, a spring guide provided to surround an outer periphery of the torsion spring, and a back-pressure relief passage through which a back-pressure chamber, configured to install the biasing member of the lock mechanism, is communicated with an inner periphery of the spring guide, wherein the back-pressure relief passage is provided at a predetermined circumferential position that goes across a point of contact between the spring guide and the torsion spring at which the outer periphery of the torsion spring is most strongly brought into contact with the inner periphery of the spring guide when the driven rotary member rotates relative to the driving rotary member by a maximum angular displacement.
According to a further aspect of the invention, a valve timing control apparatus of an internal combustion engine comprises a housing adapted to be driven by a crankshaft of the engine, and configured to define a plurality of working-fluid chambers therein by partitioning an internal space by a plurality of shoes protruding radially inward from an inner peripheral surface of the housing, a vane rotor having a rotor adapted to be fixedly connected to a camshaft and a plurality of radially-extending vanes formed on an outer periphery of the rotor for partitioning each of the working-fluid chambers of the housing by the shoes and the vanes to define phase-advance working chambers and phase-retard working chambers, the vane rotor being configured to phase-advance relative to the housing by supplying hydraulic pressure to each of the phase-advance working chambers and by discharging working oil in each of the phase-retard working chambers and configured to phase-retard relative to the housing by supplying hydraulic pressure to each of the phase-retard working chambers and by discharging working oil in each of the phase-advance working chambers, and also configured to have a cylinder structural bore formed in at least one of the plurality of vanes as a through hole extending in a direction of a rotation axis of the vane rotor, a lock mechanism having a lock member slidably installed in the cylinder structural bore and a biasing member for biasing the lock member in its extended direction from the vane rotor, the lock mechanism being configured to permit the lock member to be displaced in its retracted direction against a biasing force of the biasing member by hydraulic pressure acting on the lock member, an engaging recess formed in the housing so as to oppose the lock member, for restricting rotary motion of the vane rotor relative to the housing by bringing the lock member into engagement with the engaging recess with sliding motion of the lock member in the extended direction, a helical torsion spring attached at one end to the vane rotor and attached at the other end to the housing, for exerting a biasing force on the vane rotor and for biasing the vane rotor relative to the housing in a specified phase-change direction under a preload of the torsion spring, adjacent coils of the torsion spring being brought into contact with each other at a part of the torsion spring in a circumferential direction under a state where the torsion spring is loaded, and a back-pressure relief passage through which a back-pressure chamber, configured to install the biasing member of the lock mechanism, is communicated with an exterior space of the housing, the back-pressure relief passage configured to open toward the torsion spring, wherein the back-pressure relief passage is provided at a predetermined circumferential position that goes across a given angular position displaced from a spring-retainer position at which the other end of the torsion spring is attached to the housing by approximately 90 degrees in a direction opposite to a spring-loaded direction of the torsion spring.
The other objects and features of this invention will become understood from the following description with reference to the accompanying drawings.
Referring now to the drawings, the valve timing control apparatus of the embodiment is exemplified in a hydraulically-operated rotary vane type variable valve timing control (VTC) apparatus installed in an internal combustion engine of an automotive vehicle.
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By the way, regarding the layout of back-pressure relief passage 40, it is more preferable that the back-pressure relief passage 40 is laid out at a predetermined circumferential position going across a press-contact part “P” (described later by reference to the enlarged cross section of
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In a similar manner to the four oil seals S1 fitted into the respective seal grooves of shoes 11-14, as shown in
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Additionally, the second spring retainer 45 is configured as the radially-cutout groove formed or machined by further cutting out partially only the root of the one sidewall 44a of cutout 44. Hence, the circumferential width “W1” of the cutout 44 at the tip of the ring-shaped axially-forward-protruding end 43b is dimensioned to be narrower than the circumferential width “W2” of the cutout 44 at the root of the ring-shaped axially-forward-protruding end 43b. The inside face 45b of the second spring retainer 45, which inside face is configured to face in the axial direction, functions as a fall-out prevention spring short-arm retainer for restricting axial movement of the other end 30b of torsion spring 30 and for retaining the radially-outward bent short arm of the other end 30b in place. By means of the fall-out prevention spring short-arm retainer 45b, it is possible to restrict or suppress the torsion spring 30 from falling out, thus stably retaining the torsion spring in place.
As shown in FIGS. 1 and 3-5, rear plate 27 is formed as a comparatively thick-wall disc. Rear plate 27 is integrally formed at its outer periphery with the sprocket 1. As best seen in
Additionally, as described previously, rear plate 27 has the engaging hole 35 (see
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The operation and effects of the VTC apparatus of the internal combustion engine of the embodiment are hereunder described in detail in reference to
During an engine startup, as shown in
During operation of the engine in a first predetermined load range after the engine has been started up, directional control valve 55 becomes energized (ON) responsively to a control signal from the ECU. Hence, fluid-communication between the phase-retard side oil passage 51 and the oil pump 53 becomes established and simultaneously fluid-communication between the phase-advance side oil passage 52 and the drain passage 54 becomes established. That is, working oil, discharged from the oil pump 53, is flown into each of phase-retard chambers Re through the phase-retard side oil passage 51, and thus hydraulic pressure in each of phase-retard chambers Re becomes high. At this time, working oil in each of phase-advance chambers Ad is directed through the phase-advance side oil passage 52 and the drain passage 54 to the oil pan 56, and thus hydraulic pressure in each of phase-advance chambers Ad becomes low. By the way, part of working oil, flown into the phase-retard chamber Re, defined between the wide vane 11 and the shoe 21, is further flown or supplied into the engaging hole 35. Hence, the lock pin 32 is brought out of engagement with the engaging hole 135, thereby permitting free rotary motion of vane rotor 10 relative to housing 20. As a result, owing to an increase in the volume of each phase-retard chamber Re, arising from hydraulic-pressure supply (working-oil supply) to each phase-retard chamber Re, vane rotor 10 rotates counterclockwise and therefore the angular phase of camshaft 2 relative to the crankshaft is converted to a phase-retard side (see
In contrast, when the engine operating condition has been shifted to a second predetermined load range, directional control valve 55 becomes de-energized (OFF) responsively to a control signal from the ECU. Hence, fluid-communication between the phase-advance side oil passage 52 and the oil pump 53 becomes established and simultaneously fluid-communication between the phase-retard side oil passage 51 and the drain passage 54 becomes established. That is, working oil in each of phase-retard chambers Re is directed through the phase-retard side oil passage 51 and the drain passage 54 to the oil pan 56, and thus hydraulic pressure in each of phase-retard chambers Re becomes low. At this time, working oil, discharged from the oil pump 53, is flown into each of phase-advance chambers Ad through the phase-advance side oil passage 52, and thus hydraulic pressure in each of phase-advance chambers Ad becomes high. Owing to hydraulic-pressure supply to each phase-advance chamber Ad, there is an increased tendency for the hydraulic pressure in the phase-advance chamber Ad, defined between the wide vane 11 and the shoe 24, to be positively supplied via the through hole 39 into the annular space 38. With the hydraulic pressure supplied to the annular space 38 and exceeding the predetermined high-pressure level, the lock-pin disengagement state where the lock pin 32 is out of engagement with the engaging hole 35 can be maintained. As a result, owing to an increase in the volume of each phase-advance chamber Ad, arising from hydraulic-pressure supply (working-oil supply) to each phase-advance chamber Ad, vane rotor 10 rotates clockwise and therefore the angular phase of camshaft 2 relative to the crankshaft is converted to a phase-advance side (see
Immediately before the engine becomes put into a stopped state, hydraulic-pressure supply to each of phase-advance and phase-retard chambers Ad-Re becomes stopped, and hence there is an increased tendency for the angular phase of vane rotor 10 relative to housing 20 to be shifted to the phase-retard side by alternating torque acting on the camshaft 2. However, by virtue of the biasing force (i.e., the opposing torque) of torsion spring 30, interleaved between the vane rotor 10 and the housing 20, as shown in
As discussed above, in the VTC apparatus of the embodiment, free rotary motion of vane rotor 10 relative to housing 20 can be ensured or maintained by introducing or supplying hydraulic pressure to the lock-pin engaging hole 35 or to the annular space 38. At the same time, working oil, supplied to the engaging hole 35 or to the annular space 38, is considerably flown or leaked into the back-pressure chamber 36 through the very small radial clearance space defined between the outer peripheral surface of the large-diameter portion 32a of lock pin 32 and the inner peripheral surface of the large-diameter bore 34a of lock-pin bore 34, and then the working oil, flown or leaked into the back-pressure chamber 36, is discharged through the back-pressure relief passage 40 (i.e., the recessed communication groove 40a) into the spring accommodation bore 42.
By the way, as described previously, the back-pressure relief passage 40 is configured or formed at a predetermined circumferential position that the back-pressure relief passage 40 goes across the coil-to-coil contact part “T” of the coiled spring portion 30c of helical torsion spring 30. Hence, working oil, discharged through the back-pressure relief passage 40, is directed to the coil-to-coil contact part “T”, thereby enabling the coil-to-coil contact part “T” of torsion spring 30 to get a proper amount of lubrication, and consequently suppressing undesirable wear of the coil-to-coil contact part “T”. In particular, in the case of the embodiment using a helical torsion spring having a substantially rectangular longitudinal cross section and made from a flat square wire, when torsion spring 30 is loaded or twisted due to the applied torque and thus a twisted deformation of torsion spring 30 having the substantially rectangular longitudinal cross section takes place, the twisted, deformed torsion spring tends to easily incline in the axial direction. Hence, in the case of the use of such a helical torsion spring having a substantially rectangular longitudinal cross section, there is an increased tendency for an undesirable coil-to-coil contact to occur, during operation of the VTC apparatus. For the reasons discussed above, the proper amount of lubrication of the coil-to-coil contact part “T” is effective in smooth, low-friction torsional motion of torsion spring 30. By the way, in the case of the embodiment using a helical torsion spring made from a flat square wire having a lateral cross section of a long side in the radial direction, when subjected to torque, the twisted, deformed torsion spring tends to more easily incline in the axial direction, and thus there is a further increased tendency for an undesirable coil-to-coil contact to occur, during operation of the VTC apparatus. Hence, the proper amount of lubrication of the coil-to-coil contact part “T” is more effective in smooth, low-friction torsional motion of torsion spring 30 during operation of the VTC apparatus.
In addition to the above, due to the inclination of the coiled spring portion 30c, occurring when subjected to torque, the outer periphery of the coil-to-coil contact part “T” is most strongly brought into press-contact with the inner peripheral surface of the spring guide 41 (i.e., the curved peripheral wall of annularly-grooved torsion-spring seat 18 of vane rotor 10 and the inner peripheral wall of central through hole 43a of front plate 26) with contact pressure. The back-pressure relief passage 40 (i.e., the recessed communication groove 40a) is configured to open through the inner peripheral wall surface of spring guide 41 into the spring accommodation bore 42. Hence, working oil, discharged through the back-pressure relief passage 40, is also directed to the press-contact part “P”, thereby enabling the press-contact part “P” of torsion spring 30 to get a proper amount of lubrication, and consequently suppressing undesirable wear and scoring of the press-contact part “P”. That is to say, the proper amount of lubrication of the press-contact part “P” is effective in smooth, low-friction sliding-motion of torsion spring 30 relative to the inner periphery of spring guide 41 during operation of the VTC apparatus.
As will be appreciated from the above, according to the torsion-spring equipped VTC apparatus of the internal combustion engine of the embodiment, the back-pressure relief passage 40 is provided at a predetermined circumferential position going across a circumferential portion of the coiled spring portion 30c of torsion spring 30 that (i) the previously-discussed coil-to-coil contact between the adjacent coils (the adjacent turns of wire) and/or (ii) the previously-discussed press-contact of the outer periphery of the coiled spring portion 30c with the inner periphery of the spring guide 41 with contact pressure occurs due to an inclination of the coiled spring portion 30c when subjected to torque during rotary motion of vane rotor 10 relative to housing 20. More concretely, the previously-noted predetermined circumferential position, going across the coil-to-coil contact part “T” and/or the press-contact part “P”, corresponds to a circumferential position that goes across a given angular position displaced from the angular position of the second spring retainer 45, at which the radially-outward bent short arm of the other end 30b of torsion spring 30 is retained, by approximately 90 degrees in the direction opposite to the spring-loaded direction of torsion spring 30. By virtue of working oil, introduced into the back-pressure relief passage 40, and then directed to the coil-to-coil contact part “T” and/or the press-contact part “P”, the coil-to-coil contact part “T” and the press-contact part “P” can be properly lubricated. As a result, it is possible to effectively suppress undesirable wear, occurring at the coil-to-coil contact part “T” and/or the press-contact part “P” of the coiled spring portion 30c due to friction.
In the shown embodiment, back-pressure relief passage 40 is constructed by the recessed communication groove 40a formed in the sliding-contact surface of the wide vane 11 of vane rotor 10, in sliding-contact with the inside face of front plate 26. In lieu thereof, back-pressure relief passage 40 may be constructed as a radial through hole formed in the wide vane 11 in a manner so as to communicate the back-pressure chamber 36 with the spring accommodation bore 42. As compared to the back-pressure relief passage 40, constructed as a radial through hole formed in the wide vane 11, the back-pressure relief passage 40, constructed by the recessed communication passage 40a, is superior in easier machining, in other words, good productivity of the torsion-spring equipped VTC apparatus.
By the way, for the purpose of introducing working oil (lubricating oil) into the spring accommodation bore 42 through the use of the back-pressure relief passage 40, the torsion-spring equipped VTC apparatus of the embodiment adopts a specific clearance-space fluid-flow path configuration that, first of all, working oil is introduced into the annular space 38 adjacent to the back-pressure chamber 36, and then the introduced working oil is leaked from the annular space 38 through the very small radial clearance space defined between the lock pin 32 and the lock-pin bore 34 into the back-pressure chamber 36. The annular space 30 adjacent to the back-pressure chamber 36 functions to properly promote working-oil leakage through the very small radial clearance space into the back-pressure chamber 36. This ensures an adequate amount of working oil (lubricating oil) to be supplied through the back-pressure relief passage 40 to the spring accommodation chamber 42, thus enabling the coil-to-coil contact part “T” and/or the press-contact part “P” to get a proper amount of lubrication.
Furthermore, back-pressure relief passage 40 is positioned on the phase-advance side with respect to an circumferential position (an angular position) of the coil-to-coil contact part “T” of the coiled spring portion 30c of torsion spring 30 under a locked state where the lock pin 32 of lock mechanism 31 is kept in locked-engagement with the lock-pin bore 34 for restricting rotary motion of vane rotor 10 relative to housing 20. This ensures more certain lubrication of the coil-to-coil contact part “T”, during operation of the VTC apparatus.
The entire contents of Japanese Patent Application Nos. 2012-179732 (filed Aug. 14, 2012) and 2013-091054 (filed Apr. 24, 2013) are incorporated herein by reference.
While the foregoing is a description of the preferred embodiments carried out the invention, it will be understood that the invention is not limited to the particular embodiments shown and described herein, but that various changes and modifications may be made without departing from the scope or spirit of this invention as defined by the following claims.
Claims
1. A valve timing control apparatus of an internal combustion engine comprising:
- a housing adapted to be driven by a crankshaft of the engine, and configured to define a plurality of working-fluid chambers therein by partitioning an internal space by a plurality of shoes protruding radially inward from an inner peripheral surface of the housing;
- a vane rotor having a rotor adapted to be fixedly connected to a camshaft and a plurality of radially-extending vanes formed on an outer periphery of the rotor for partitioning each of the working-fluid chambers of the housing by the shoes and the vanes to define phase-advance working chambers and phase-retard working chambers, the vane rotor being configured to phase-advance relative to the housing by supplying hydraulic pressure to each of the phase-advance working chambers and by discharging working oil in each of the phase-retard working chambers and configured to phase-retard relative to the housing by supplying hydraulic pressure to each of the phase-retard working chambers and by discharging working oil in each of the phase-advance working chambers, and also configured to have a cylinder structural bore formed in at least one of the plurality of vanes as a through hole extending in a direction of a rotation axis of the vane rotor;
- a lock mechanism having a lock member slidably installed in the cylinder structural bore and a biasing member for biasing the lock member in its extended direction from the vane rotor, the lock mechanism being configured to permit the lock member to be displaced in its retracted direction against a biasing force of the biasing member by hydraulic pressure acting on the lock member;
- an engaging recess formed in the housing so as to oppose the lock member, for restricting rotary motion of the vane rotor relative to the housing by bringing the lock member into engagement with the engaging recess with sliding motion of the lock member in the extended direction;
- a helical torsion spring attached at one end to the vane rotor and attached at the other end to the housing, for exerting a biasing force on the vane rotor and for biasing the vane rotor relative to the housing in a specified phase-change direction under a preload of the torsion spring, adjacent coils of the torsion spring being brought into contact with each other at a part of the torsion spring in a circumferential direction under a state where the torsion spring is loaded; and
- a back-pressure relief passage through which a back-pressure chamber, configured to install the biasing member of the lock mechanism, is communicated with an exterior space of the housing, the back-pressure relief passage configured to open toward the torsion spring,
- wherein the back-pressure relief passage is provided at a predetermined circumferential position that goes across a coil-to-coil contact part that the adjacent coils of the torsion spring are brought into contact with each other when the vane rotor rotates relative to the housing by a maximum angular displacement.
2. The valve timing control apparatus as claimed in claim 1, further comprising:
- a spring guide provided to surround an outer periphery of the torsion spring.
3. The valve timing control apparatus as claimed in claim 2, wherein:
- the housing comprises: a cylindrical housing body formed integral with the plurality of shoes protruding radially inward from the inner peripheral surface of the cylindrical housing body; a front plate configured to close one axial end of the housing body; and a rear plate configured to close the other axial end of the housing body, facing the camshaft;
- the spring guide comprises: an axially-protruding cylindrical portion formed integral with the front plate; and an annular groove recessed in the vane rotor.
4. The valve timing control apparatus as claimed in claim 1, wherein:
- the vane rotor has the back-pressure relief passage, which is a recessed groove formed in a sliding-contact surface of the vane rotor in sliding-contact with the front plate.
5. The valve timing control apparatus as claimed in claim 1, wherein:
- the torsion spring is made from a flat square wire having a substantially rectangular lateral cross section.
6. The valve timing control apparatus as claimed in claim 5, wherein:
- the torsion spring is made from the flat square wire having the lateral cross section of a longer side in a radial direction of the torsion spring.
7. The valve timing control apparatus as claimed in claim 1, wherein:
- the back-pressure relief passage is positioned on a phase-advance side with respect to the coil-to-coil contact part of the torsion spring under a locked state where the lock member of the lock mechanism has been engaged with the engaging recess.
8. The valve timing control apparatus as claimed in claim 1, wherein:
- the lock member is a stepped lock pin having a stepped portion formed between a large-diameter portion and a small-diameter portion; and
- the lock mechanism is configured so that hydraulic pressure acts on at least the stepped portion.
9. The valve timing control apparatus as claimed in claim 8, wherein:
- two hydraulic pressures act on the large-diameter portion and the small-diameter portion separately from each other.
10. A valve timing control apparatus of an internal combustion engine comprising:
- a driving rotary member adapted to be driven by a crankshaft of the engine;
- a driven rotary member adapted to be fixedly connected to a camshaft and configured to phase-change relative to the driving rotary member by supplying or discharging working oil, and also configured to have a cylinder structural bore formed to extend in a direction of a rotation axis of the driven rotary member;
- a lock mechanism having a lock member slidably installed in the cylinder structural bore and a biasing member for biasing the lock member in its extended direction from the vane rotor, the lock mechanism being configured to permit the lock member to be displaced in its retracted direction against a biasing force of the biasing member by hydraulic pressure acting on the lock member;
- an engaging recess formed in the driving rotary member so as to oppose the lock member, for restricting rotary motion of the driven rotary member relative to the driving rotary member by bringing the lock member into engagement with the engaging recess with sliding motion of the lock member in the extended direction;
- a helical torsion spring attached at one end to the driven rotary member and attached at the other end to the driving rotary member, for exerting a biasing force on the vane rotor and for biasing the vane rotor relative to the housing in a specified phase-change direction under a preload of the torsion spring, adjacent coils of the torsion spring being brought into contact with each other at a part of the torsion spring in a circumferential direction under a state where the torsion spring is loaded;
- a spring guide provided to surround an outer periphery of the torsion spring; and
- a back-pressure relief passage through which a back-pressure chamber, configured to install the biasing member of the lock mechanism, is communicated with an inner periphery of the spring guide,
- wherein the back-pressure relief passage is provided at a predetermined circumferential position that goes across a point of contact between the spring guide and the torsion spring at which the outer periphery of the torsion spring is most strongly brought into contact with the inner periphery of the spring guide when the driven rotary member rotates relative to the driving rotary member by a maximum angular displacement.
11. A valve timing control apparatus of an internal combustion engine comprising:
- a housing adapted to be driven by a crankshaft of the engine, and configured to define a plurality of working-fluid chambers therein by partitioning an internal space by a plurality of shoes protruding radially inward from an inner peripheral surface of the housing;
- a vane rotor having a rotor adapted to be fixedly connected to a camshaft and a plurality of radially-extending vanes formed on an outer periphery of the rotor for partitioning each of the working-fluid chambers of the housing by the shoes and the vanes to define phase-advance working chambers and phase-retard working chambers, the vane rotor being configured to phase-advance relative to the housing by supplying hydraulic pressure to each of the phase-advance working chambers and by discharging working oil in each of the phase-retard working chambers and configured to phase-retard relative to the housing by supplying hydraulic pressure to each of the phase-retard working chambers and by discharging working oil in each of the phase-advance working chambers, and also configured to have a cylinder structural bore formed in at least one of the plurality of vanes as a through hole extending in a direction of a rotation axis of the vane rotor;
- a lock mechanism having a lock member slidably installed in the cylinder structural bore and a biasing member for biasing the lock member in its extended direction from the vane rotor, the lock mechanism being configured to permit the lock member to be displaced in its retracted direction against a biasing force of the biasing member by hydraulic pressure acting on the lock member;
- an engaging recess formed in the housing so as to oppose the lock member, for restricting rotary motion of the vane rotor relative to the housing by bringing the lock member into engagement with the engaging recess with sliding motion of the lock member in the extended direction;
- a helical torsion spring attached at one end to the vane rotor and attached at the other end to the housing, for exerting a biasing force on the vane rotor and for biasing the vane rotor relative to the housing in a specified phase-change direction under a preload of the torsion spring, adjacent coils of the torsion spring being brought into contact with each other at a part of the torsion spring in a circumferential direction under a state where the torsion spring is loaded; and
- a back-pressure relief passage through which a back-pressure chamber, configured to install the biasing member of the lock mechanism, is communicated with an exterior space of the housing, the back-pressure relief passage configured to open toward the torsion spring,
- wherein the back-pressure relief passage is provided at a predetermined circumferential position that goes across a given angular position displaced from a spring-retainer position at which the other end of the torsion spring is attached to the housing by approximately 90 degrees in a direction opposite to a spring-loaded direction of the torsion spring.
Type: Application
Filed: Aug 12, 2013
Publication Date: Feb 20, 2014
Applicant: Hitachi Automotive Systems, Ltd. (Hitachinaka-shi)
Inventor: Atsushi WATANABE (Atsugi-shi)
Application Number: 13/964,613
International Classification: F01L 1/34 (20060101);