WO2006067896A1 - Dispositif de reglage de distribution - Google Patents

Dispositif de reglage de distribution Download PDF

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Publication number
WO2006067896A1
WO2006067896A1 PCT/JP2005/016259 JP2005016259W WO2006067896A1 WO 2006067896 A1 WO2006067896 A1 WO 2006067896A1 JP 2005016259 W JP2005016259 W JP 2005016259W WO 2006067896 A1 WO2006067896 A1 WO 2006067896A1
Authority
WO
WIPO (PCT)
Prior art keywords
lock pin
lock
storage groove
valve timing
rotating body
Prior art date
Application number
PCT/JP2005/016259
Other languages
English (en)
Japanese (ja)
Inventor
Koji Yudate
Akira Sakata
Hiroyuki Kinugawa
Original Assignee
Mitsubishi Denki Kabushiki Kaisha
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Denki Kabushiki Kaisha filed Critical Mitsubishi Denki Kabushiki Kaisha
Publication of WO2006067896A1 publication Critical patent/WO2006067896A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34463—Locking position intermediate between most retarded and most advanced positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34473—Lock movement perpendicular to camshaft axis

Definitions

  • the present invention relates to a valve timing adjusting device that controls the opening / closing timing of an intake / exhaust valve of an internal combustion engine, and more particularly to a valve timing adjusting device having an improved locking mechanism.
  • a conventional valve timing adjusting device includes a first rotating body that rotates synchronously with a crankshaft of an internal combustion engine, and an end portion of a camshaft that is coaxially integrated with the first rotating body.
  • a second rotator that is movably incorporated, and a lock mechanism that locks the first rotator and the second rotator when the internal combustion engine is stopped or started.
  • a sliding hole for inserting a lock pin which is a radial through hole, is provided in the housing of the housing serving as the first rotating body, and the axial direction of the lock pin is set in the sliding hole.
  • the rotor (second rotating body) inserted so as to be in the radial direction of the housing and provided with a lock hole for engaging the lock pin is provided in the lock hole.
  • a plug body (spring holding member) for connecting the release oil passage and holding the spring for urging the lock pin in the direction of engagement with the lock hole in a compressed state was fitted into the sliding hole.
  • the thing of a structure is already known (for example, refer patent document 1).
  • a flat lock plate is applied as a lock member for restraining the relative rotation of the first rotating body and the second rotating body, and this lock plate is used.
  • the lock plate is inserted into the radial groove (retracted groove) provided in the first rotating body (referred to as the external rotor), and the lock plate is provided in the second rotating body (referred to as the internal rotor).
  • the coiled torsion spring is urged in the direction of engagement with the lock groove (receiving groove) to which the lock release oil passage is connected, and the edge of the lock plate is fitted into the lock groove by the urging force.
  • Patent Document 1 Japanese Patent Laid-Open No. 2003-3809 ([0027] and [0028], FIG. 1)
  • Patent Document 2 Japanese Patent Laid-Open No. 2001-317314 ([0021] and [0022], FIG. 5) [0005]
  • the conventional valve timing adjusting device is configured as described above.
  • the axial direction of the lock pin is inserted into a sliding hole that radially passes through the housing of the housing, and the lock pin Since the end face in the axial direction is a pressure receiving surface on which the unlocking hydraulic pressure acts, there is a problem that the initial operation of the lock pin by the unlocking hydraulic pressure is delayed because the pressure receiving area is narrow.
  • the lock pin inserted into the sliding hole which also serves as the radial through hole of the housing, only moves linearly in the axial direction.
  • the corner portion of the axial end surface of the lock pin is Is likely to squeeze into the inner walls of the sliding hole and the lock hole, and the lock pin may squeeze foreign matter such as in unlocking oil.
  • a wedge phenomenon occurs between the inner wall surface of the moving hole or the lock hole and the lock pin, thereby causing a great hindrance to the operation of the lock pin.
  • the sliding hole for inserting the lock pin that penetrates the housing in the radial direction is drilled in the housing after molding because the housing is made of metal.
  • a drilling force has a problem that it is easy to cause a problem in processing accuracy, increases the number of processing steps, and increases the cost, resulting in poor productivity.
  • a sprocket for inputting the rotational output of the internal combustion engine is provided outside the housing, so that the sliding hole for inserting the lock pin is formed from the outside of the nosing. There was a problem that it was not possible to drill holes in the direction.
  • Patent Document 2 a flat lock plate is applied as a lock member that restrains relative rotation between the first rotating body and the second rotating body, and the lock plate is used as the first rotating body. Since the end portion of the lock plate is inserted into and engaged with the lock groove of the second rotating body by the urging force of the torsion spring after being inserted into the retraction groove (radial groove) of the Since the edge of the lock plate serves as a pressure receiving surface for the unlocking hydraulic pressure and the pressure receiving area is small, there is a problem that the initial operation of the lock plate by the unlocking hydraulic pressure is delayed as in the case of the lock pin of Patent Document 1. It was. In addition, the lock plate is interviewed in the escape groove.
  • the lock plate of Patent Document 2 is a hexahedron
  • the hexahedron must be finished with high accuracy in order to ensure its dimensional accuracy.
  • force is likely to cause a problem in processing accuracy.
  • the lock plate and the external rotor (first rotating body) to which the torsion spring is attached are attached to the lock plate.
  • the retraction groove into which the plate is inserted and the spring housing hole having a unique space shape must be continuously formed, and there is a problem that the continuous shape becomes complicated and design problems are likely to occur.
  • the present invention has been made to solve the above-described problems, and can secure a wide pressure-receiving surface of the lock pin to which the unlocking hydraulic pressure is applied.
  • the purpose is to obtain a highly reliable valve timing adjusting device that can quickly and stably respond and that can prevent the pinching phenomenon of the lock pin.
  • a valve timing adjusting apparatus is arranged in a system that opens and closes at least one of intake and exhaust valves of an internal combustion engine, and a first rotating body that is rotationally driven by the output of the internal combustion engine, A second rotating body that is incorporated in the first rotating body so as to be relatively rotatable and is driven in a retarded or advanced direction by a control hydraulic pressure, and one of the first rotating body and the second rotating body.
  • a lock pin provided on one of the rotating bodies, a lock hole provided on the other rotating body to which a lock release oil passage is connected, and the lock pin is detachably fitted, and the lock pin is connected to the lock hole.
  • a valve timing adjusting device comprising an urging member for urging in the insertion direction, wherein the lock pin housing groove formed in the one rotating body has a circular shaft-shaped lock pin, and the radial direction of the lock pin is the lock direction.
  • the fitting direction to the pin storage groove Slidably fitted housed so that, in which the outer peripheral surface of the lock pin and configured to abut the biasing force of the biasing member in the interior rear wall of the locking hole.
  • the circular pin-shaped lock pin is formed in the lock pin housing groove formed in one of the two rotatable bodies, and the radial direction thereof is the lock pin housing groove.
  • the outer peripheral surface portion of the lock pin is attached to the inner inner wall surface of the lock hole formed on the other rotating body and connected to the unlocking oil passage.
  • the lock pin when unlocking hydraulic pressure is applied is the semi-circumferential circumference of the outer peripheral surface over the entire length in the axial direction becomes the pressure receiving surface of the unlocking hydraulic pressure, and the pressure receiving area is reduced to the conventional lock pin Since the lock pin can be secured more widely than in the case of the lock plate, the lock pin can be quickly and stably responded when the unlocking hydraulic pressure is applied, and the response operability is improved.
  • the lock pin that receives the unlocking hydraulic pressure at the outer peripheral surface can be rotated by the unlocking hydraulic pressure, so that the lock pin may trap foreign matter such as in the unlocking oil. Even in this case, it is possible to discharge the squeezed foreign matter out of the system together with the unlocking oil by the rotation of the lock pin, thus preventing the wedge phenomenon due to the foreign matter stagnation of the lock pin. This has the effect of becoming possible.
  • FIG. 1 is a cross-sectional view showing a valve timing adjusting device according to Embodiment 1 of the present invention.
  • FIG. 2 is a sectional view taken along the line A—A in FIG. 1 at the rotor most retarded angle position.
  • FIG. 3 is a sectional view taken along the line BB in FIG. 1 at the rotor most retarded angle position.
  • FIG. 4 is a cross-sectional arrow view of the rotor at the most advanced angle position along line BB in FIG.
  • FIG. 5 is an explanatory view showing the main part of the valve timing adjusting apparatus according to the second embodiment of the present invention as seen from the direction of arrows CC in FIG.
  • FIG. 6 is an explanatory view showing the main part of a valve timing adjusting apparatus according to Embodiment 3 of the present invention, corresponding to FIG.
  • FIG. 7 is a cross-sectional view showing a lock pin housing portion of a valve timing adjusting apparatus according to Embodiment 4 of the present invention.
  • FIG. 8 is a cross-sectional view showing a lock pin housing portion of a valve timing adjusting device according to Embodiment 5 of the present invention.
  • FIG. 9 shows a lock pin housing portion of a valve timing adjusting device according to Embodiment 6 of the present invention. It is sectional drawing shown.
  • FIG. 10 is a cross-sectional view showing a main part of a valve timing adjusting apparatus according to Embodiment 7 of the present invention.
  • FIG. 11 is a radial sectional view showing a valve timing adjusting device according to an eighth embodiment of the present invention with the front cover removed.
  • FIG. 12 is an axial sectional view showing the valve timing adjusting device of FIG. 11 in a state where a front cover is attached.
  • FIG. 1 is a cross-sectional view showing a valve timing adjusting apparatus according to Embodiment 1 of the present invention
  • FIG. 2 is a cross-sectional view taken along the line A—A in FIG.
  • Fig. 4 is a cross-sectional view of the rotor at the most retarded angle position along line B-B
  • Fig. 4 is a cross-sectional view of the rotor at the most advanced position along line B-B in Fig. 1.
  • the valve timing adjusting device shown in FIG. 1 includes a camshaft 1 that opens and closes an intake / exhaust valve of an internal combustion engine, and a crankshaft (not shown) of the internal combustion engine that is rotatably provided on the camshaft 1.
  • a first rotating body 2 that rotates in synchronization with the first rotating body 2 and a second rotating body 3 that is rotatably incorporated in the first rotating body 2 and rotates together with the camshaft 1. Detailed configurations thereof will be described below.
  • the first rotating body 2 integrally has a timing sprocket 5 on the outer periphery and a plurality of shrouds 6 (see FIGS. 2 and 3) extending in the direction of the center of rotation on the inner peripheral surface.
  • a cylindrical case 4 that is rotatably fitted and held on the camshaft 1, and a front cover 7 and a rear cover 8 that are fastened together by fastening bolts (first fastening members) 9 on both ends of the case 4 in the axial direction.
  • the housing structure consists of
  • the second rotating body 3 is a rotor force for rotating integrally with the camshaft 1.
  • the rotor 3 is rotatably fitted and housed in the case 4 and is fitted to the axial end portion of the camshaft 1 by a shaft bolt (second fastening member not shown).
  • the camshaft 1 is fastened and fixed.
  • the rotor 3 integrally includes a plurality of vanes 10 that extend in the radial direction due to the outer peripheral force between the shears 6. These vanes 10 partition and form an advance hydraulic chamber 11 and a retard hydraulic chamber 12 between the case 6 and the shoe 6, and the advance hydraulic chamber 11 and the retard hydraulic chamber 12 are provided in the advance hydraulic chamber 11 and the retard hydraulic chamber 12. Hydraulic oil is supplied.
  • a radial lock pin housing groove 13 is provided on the axial end surface of the case 6 of the case 4.
  • the lock pin housing groove 13 is formed in a concave shape that is opened in the axial end surface of the case 4 on the rear cover 8 side and the inner diameter surface of the case 4.
  • a circular shaft-shaped lock pin 14 is inserted into the lock pin storage groove 13 formed in this way, and the radial direction of the lock pin 14 is the fitting direction to the lock pin storage groove 13 and extends in the radial direction of the case 4. It is fitted so that it can slide.
  • the lock pin housing groove 13 houses a spring (biasing member) 15 that biases the lock pin 14 in the inner diameter direction of the case 4.
  • the rear cover 8 When the lock pin 14 and the spring 15 are housed in the lock pin housing groove 13 in this way, the side opening end of the lock pin housing groove 13 is fastened and fixed to the rear axial end surface of the case 4.
  • the rear cover 8 is sealed.
  • the rear cover 8 has a drain hole 17 connected to the storage portion of the spring 15 in the lock pin storage groove 13.
  • the outer peripheral surface of the rotor 3 is provided with a lock hole 16 for fitting and engaging the outer peripheral surface portion of the lock pin 14 at the most retarded position of the rotor 3.
  • the lock hole 16 is formed in a concave shape that is open to the axial end surface on the rear side of the rotor 3 and the outer peripheral surface of the rotor 3.
  • the rear opening end of the lock hole 16 is sealed with the rear cover 8, and the outer peripheral surface portion of the lock pin 14 is fitted and engaged with the lock hole 16 in this state by the urging force of the spring 15. It is summer.
  • the rotor 3 is provided with an unlocking oil passage 20 communicating with the lock hole 16.
  • the camshaft 1 has a first oil passage (advance oil passage) 18 that supplies hydraulic oil into each advance hydraulic chamber 11 and a first oil passage that supplies hydraulic oil to each retard hydraulic chamber 12.
  • Two oil passages (retarding oil passages) 19 are provided, and hydraulic oil is supplied to these oil passages 18 and 19 from a hydraulic oil supply means via a hydraulic control valve. Then, the unlocking oil passage 2 is connected to the first oil passage 18. 0 is connected.
  • the unlocking hydraulic pressure for the lock pin 14 is zero or less than the specified pressure value, such as when the internal combustion engine is stopped or idling, the outer peripheral surface of the lock pin 14 biased in the inner diameter direction of the case 4 by the biasing force of the spring 15
  • the substantially half circumferential surface portion is fitted and engaged in the lock hole 16 on the rotor 3 side, and the relative rotation between the case 4 and the rotor 3 is restricted. If an unlocking hydraulic pressure higher than a predetermined pressure is supplied from the unlocking oil passage 20 to the lock pin 14 by starting the internal combustion engine or increasing the output from this restrained state, the unlocking hydraulic pressure is applied to the outer periphery of the lock pin 14. Acts almost half a plane.
  • the outer peripheral surface of the lock pin 14 becomes a pressure receiving surface for almost half the circumferential force release oil, so that the lock pin 14 quickly retracts into the lock pin housing groove 13 against the biasing force of the spring 15.
  • the restraint between the case 4 and the rotor 3 is released.
  • the working oil is supplied from the first oil passage 18 to the advance hydraulic chamber 11 and the working oil in the retard hydraulic chamber 12 is discharged from the second oil passage 19, so that the rotor 3 Is rotated counterclockwise on the paper surface of FIG. 3 with respect to the case 4, and the mouth 3 is held at the most advanced position shown in FIG.
  • the circular shaft-shaped lock pin 14 is placed in the radial lock pin housing groove 13 provided in the shoe 6 of the case 4 that is the first rotating body 2.
  • the lock pin 14 is fitted so that the radial direction of the lock pin 14 is fitted in the lock pin housing groove 13 (the radial direction of the lock pin 14 faces the radial direction of the case 4).
  • a substantially half of the outer peripheral surface of the rotor is configured to be fitted and engaged by a biasing force of a spring 15 in a lock hole 16 formed in the rotor 3 as the second rotating body and connected to the unlocking oil passage 20.
  • the lock pin 14 when unlocking oil pressure is applied from the unlocking oil passage 20 is the pressure receiving surface of the unlocking oil pressure almost half of the outer circumferential surface over the entire length in the axial direction.
  • the pressure receiving surface of the unlocking hydraulic pressure can be secured widely, and the lock pin 14 can be quickly and stably responded when the unlocking hydraulic pressure is applied, and the response operability is improved.
  • the lock pin 14 that receives the unlocking hydraulic pressure almost half of its outer peripheral surface can be rotated by the unlocking hydraulic pressure. Even when a foreign object is trapped, it is possible to naturally discharge the trapped foreign object to the outside of the system together with the unlocking oil by the rotation of the lock pin 14. If the wedge phenomenon can be prevented, there will be an effect.
  • the lock pin 14 that can be rotated by the unlocking hydraulic pressure does not always have a constant contact surface with the inner wall surface of the lock hole 16, so that the durability of the lock pin 14 is improved. There is also an effect.
  • the lock pin storage groove 13 is formed in a concave shape on the axial end surface of the case 6 of the case 4, the lock pin storage groove 13 is formed in the case. 4 Both can be easily molded, and unlike the conventional example, it is no longer necessary to drill the sliding hole into which the lock pin is slidable in the axial direction. It is easy, productivity is improved, and cost can be reduced.
  • the concave lock pin housing groove 13 is formed on the axial end surface of the case 4 so that the lock pin insertion hole (in the radial direction) has the sprocket 5 outside the case 4. Even if it is a thin noble timing adjustment device that cannot drill through holes, it can be manufactured.
  • valve timing adjusting device can be easily assembled, and the assembling workability can be improved.
  • the lock pin can be processed into a cylindrical shape to reduce the weight, which has the effect of reducing the influence of centrifugal force.
  • FIG. 5 is an explanatory view showing the main part of the noble timing adjusting apparatus according to the second embodiment of the present invention as seen in the direction of arrows CC in FIG. The second embodiment will be described with reference to FIGS. 1 to 4.
  • the lock pin housing groove 13 and the lock hole 16 described in the first embodiment are further characterized in configuration. That is, in the second embodiment, as shown in FIGS. 2 to 4, the lock pin storage groove 13 has a back force spring storage groove (biasing member storage groove) in the lock pin storage groove 13.
  • a lock pin storage groove portion (hereinafter referred to as pin storage groove) formed as 13a and having a groove width (groove width in the axial direction of the lock pin 14) formed continuously from the spring storage groove portion 13a. It is a stepped structure consisting of 13b).
  • a recess 13c for preventing pinching is formed at the connecting portion between the spring housing groove 13a and the pin housing groove 13b to correspond to the corners on the spring 15 side at both axial end surfaces of the lock pin 14.
  • the drain hole 17 of the rear cover 8 shown in FIG. 1 is connected to the pin receiving groove 13b!
  • the connection position of the drain hole 17 with respect to the pin housing groove 13b is in the vicinity of the contact portion between the lock pin 14 and the spring 15 that have retracted into the pin housing groove 13b from the lock hole 16 and the lock pin 14 It is set outside the sliding stroke range.
  • the lock hole 16 is formed with a recess 16a (see FIG. 5) for preventing the lock pin 16 from squeezing into a position where both axial end surfaces of the lock pin 14 are fitted.
  • An unlocking oil passage 20 is opened at the center of the back wall in the lock hole 16.
  • the sliding range of the lock pin 14 in the direction in which the spring 15 is compressed is formed at the connection portion of the spring storage groove portion 13a with the pin storage groove portion 13b. Therefore, the spring 15 can be prevented from being excessively compressed by the lock pin 14, and the spring 15 is not stuck in the compressed state, so that the durability of the spring 15 is improved.
  • the lock pin 14 can be operated stably and smoothly at all times.
  • the recesses 13c and 16a for preventing the stagnation of the lock pin receiving groove 13 and the lock hole 16 serve as reliefs at the corners of both end surfaces of the lock pin 14 in the axial direction.
  • the drain hole 17 connected to the spring housing groove portion 13a is configured so that the connection position with the spring housing groove portion 13a is set outside the sliding stroke range of the lock pin 14. Therefore, there is no blockage with the lock pin 14, and therefore, there is an effect that it is possible to always ensure a good hydraulic oil discharge performance.
  • FIG. 6 is an explanatory view showing the main part of the valve timing adjusting apparatus according to the third embodiment of the present invention in correspondence with FIG.
  • the unlocking oil passage 20 is opened and connected to the center of the back wall in the lock hole 16.
  • the stagnation in the lock hole 16 in the second embodiment is used.
  • the unlocking oil passage 20 is openly connected along the wall surface of the recess 16a for preventing entrapment.
  • the recess 16a that prevents the lock pin 14 from being caught in the lock hole 16 and the unlocking oil passage 20 can be formed continuously, and the lock If it is possible to prevent the lock pin 14 from being squeezed by both the release oil passage 20 and the recess 16a, there is an effect!
  • FIG. 7 is a cross-sectional view showing the lock pin housing portion of the valve timing adjusting apparatus according to Embodiment 4 of the present invention.
  • the diameter of the lock pin 14 and the outer diameter of the spring 15 are set to substantially the same diameter, and the contact point (action point) P of the spring 15 with respect to the outer peripheral surface of the lock pin 14 is set to the lock pin 14 described above. This is set at the center of the outer peripheral surface of the lock pin 14 near the center of gravity.
  • the symmetrical portion of the end ring portion of the coiled spring 15 is brought into contact with the two-point contact state at positions on both sides in the axial direction across the center of gravity of the lock pin 14.
  • the urging force of the spring 15 can be concentratedly applied to the vicinity of the center of gravity of the outer peripheral surface of the lock pin 14, and therefore the lock pin 14 is There is an effect that it can slide smoothly and stably. Also, as mentioned above, Since the vicinity of the center of gravity of the outer peripheral surface of the lock pin 14 is the contact point of the spring 15 and the outer peripheral surface of the lock pin 14 is supported on the spring 15 in a two-point contact state, the lock pin 14 rotates. Even if the lock pin 14 squeezes foreign matter between the lock pin receiving groove 13 or the inner wall surface of the lock hole 16, the foreign matter is naturally removed by the rotation of the lock pin 14. If you can!
  • FIG. 8 is a cross-sectional view showing the lock pin housing portion of the valve timing adjusting apparatus according to Embodiment 5 of the present invention.
  • the spring 15 having the same diameter as the lock pin 14 and the outer diameter is applied, but in the fifth embodiment, the spring whose outer diameter is smaller than the diameter of the lock pin 14 is used. 15 is applied, and the spring 15 does not bend in the radial direction. That is, in the fifth embodiment, the lock pin storage groove 13 having a stepped structure is configured such that the radial groove width of the lock pin 14 in the spring storage groove portion 13a is narrower than the groove width of the pin storage groove portion 13b. The spring 15 is housed in the spring housing groove 13a.
  • the groove width of the spring housing groove portion 13a is adjustable according to the outer diameter of the spring 15, and the spring housing groove portion 13a is provided on the inner surface of the rear cover 8 as the means.
  • a convex portion 8a is formed in the direction of narrowing the groove width. Therefore, the groove width of the spring accommodating groove 13a can be adjusted by changing the thickness of the convex portion 8a.
  • the outer periphery of the lock pin 14 is the same as in the fifth embodiment.
  • the contact point (action point) P of the spring 15 with respect to the surface can be set at the center near the center of gravity of the lock pin 14 on the outer peripheral surface of the lock pin 14, and therefore, Similar effects can be obtained.
  • FIG. 9 is a sectional view showing a lock pin housing portion of the valve timing adjusting apparatus according to Embodiment 6 of the present invention.
  • a flat surface 14a that is parallel to the entire length in the axial direction is formed at a position symmetrical to the outer peripheral surface of the circular shaft-shaped lock pin 14, and this flat surface 14a is formed on the inner wall surface of the lock pin housing groove 13 and the rear cover. It is configured to be in sliding contact with the inner side surface of 8. According to the sixth embodiment having such a configuration, there is an effect that the sealing performance between the inner wall surface of the lock pin housing groove 13 and the rear cover 8 and the lock pin 14 is improved.
  • FIG. 10 is a cross-sectional view showing the main part of the valve timing adjusting apparatus according to Embodiment 7 of the present invention.
  • the inner surface of the rotor 3 is depressed in the inner diameter direction of the rotor 3 on the inner wall surface in the lock hole 16 of the rotor 3 so as to correspond to the corners of both ends of the lock pin 14 fitted in the lock hole 16 in the axial direction.
  • the concave groove portion 16b is formed.
  • Other configurations in the tenth embodiment are the same as those in the first embodiment and the second embodiment.
  • the effects similar to those of the first embodiment are considered, and the corners at both axial ends of the lock pin 14 fitted into the lock hole 16 by the urging force of the spring 15 are used. If the concave groove portion 16b in the lock hole 16 can prevent the portion from squeezing into the inner wall surface of the lock hole 16, there is an effect!
  • FIG. 11 is a radial sectional view showing the valve timing adjusting device according to Embodiment 8 of the present invention with the front cover removed
  • FIG. 12 is an axial sectional view showing the valve timing adjusting device of FIG. 11 with the front cover attached. .
  • the rotor 3 as the second rotating body is provided with a lock pin housing groove 21. That is, in the eighth embodiment, the vane 10 of the rotor 3 is provided with the lock pin receiving groove 21 having a concave cross section opened in the axial end surface on the front cover 7 mounting side of the rotor 3 in the axial direction.
  • a lock hole 22 having a concave cross section facing the opening end of the lock pin housing groove 21 at the most retarded position of the rotor 3 is formed on the inner side surface of the front cover 7.
  • the lock pin storage groove 21 is formed as a spring storage groove portion 21a (see FIG. 11) in which the inner portion of the lock pin storage groove 21 has a circular hole portion force, and is continuously formed in the mouth.
  • the pin housing groove portion 21b formed by a square hole opening on the axial end surface of the motor 3 is formed.
  • the front cover 7 is provided with an unlocking oil passage 23 that communicates with the lock hole 22, and this unlocking oil passage 23 passes through the advance hydraulic chamber 11 and the first shaft of the camshaft 1. It is connected to the oil passage (advanced oil passage) 18. Since the other configuration of the eighth embodiment is the same as that of the first embodiment, the same parts are denoted by the same reference numerals and the description of the configuration is omitted.
  • the spring 15 is fitted and housed in the spring housing groove 21a of the lock pin housing groove 21, and the lock pin 14 is housed in the pin housing groove 21b.
  • the lock pin 14 is slidably fitted into the pin housing groove 21b with the radial direction of the lock pin 14 being the fitting direction with respect to the pin housing groove 21b.
  • the case pin 4 the front cover 7, and the rear force bar 8 are fastened and fixed together with the fastening bolt 9, so that the mouth pin 14 in the pin housing groove 21b is connected to the front cover.
  • the valve timing adjustment device is assembled with the inner surface of 7 in sliding contact or in the lock hole 22.
  • the operation of the nove timing adjustment device assembled in this way is the same as that of the first embodiment except that the lock pin 14 moves in the axial direction of the rotor 3 and engages and disengages with the lock hole 22 of the front cover 7. It is done in the same way.
  • the lock pin housing groove 21 having a concave cross-section opening in the axial end surface of the rotor 3 is formed in the vane 10 of the rotor 3 along the axial direction thereof. Since it is configured as described above, it is possible to easily mold the lock pin housing groove 21 together with the rotor 3, and the same effect as in the first embodiment can be obtained. Further, the same effect as that of the first embodiment can be obtained by fitting the outer peripheral surface portion of the lock pin 14 into the lock hole 22.
  • the lock pin 14 described in the first embodiment to the seventh embodiment may have substantially the same diameter and axial length, but the axial length is longer than the diameter. But preferable. In this case, it is possible to prevent the lock pin 14 from being assembled in the wrong direction in the lock pin housing groove 13, and this has the effect of improving the assembling workability.
  • This lock pin storage groove 13 is the axial direction of the case 4 on the front cover 7 side. Even in this case, the same effect can be obtained.
  • the lock pin housing groove 21 opened in the axial end surface on the front cover 7 side of the rotor 3 is provided with the axial end surface on the rear cover 8 side of the rotor 3.
  • the lock hole 22 of the front cover 7 may be provided in the rear cover 8.
  • the drain hole 17 of the rear cover 8 in the first embodiment may be provided in the front cover 7 case 4 or the shape may be a groove other than the hole. If the drain hole 17 is connected to the spring housing groove 13a, 21a at a position outside the sliding stroke range of the lock pin 14 in the spring housing groove 13a, 21a, the hydraulic oil discharge performance may be impaired. Nah ...
  • valve timing adjusting device can secure a wide pressure receiving surface of the lock pin to which the unlocking hydraulic pressure is applied, and can make the lock pin respond quickly and stably. Suitable for preventing pin stagnation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

La présente invention décrit un dispositif de réglage de distribution, comprenant deux corps rotatifs (2, 3) pouvant tourner l’un par rapport à l’autre, une goupille de verrouillage (14) installée dans le premier corps rotatif (2), et un trou de verrouillage (16) formé dans l’autre corps rotatif (3). La goupille de verrouillage en forme de tige circulaire (14) est installée dans une rainure de stockage de goupille de verrouillage (13) formée dans le premier corps rotatif (2) de sorte que la direction radiale de la goupille de verrouillage (14) soit alignée avec la direction d’installation de la goupille de verrouillage dans la rainure de stockage de goupille de verrouillage (13). Ainsi, la partie de surface périphérique extérieure de la goupille de verrouillage (14) est mise en contact avec la surface de paroi intérieure du trou de verrouillage (16) par la force de mise en fonctionnement de la goupille de verrouillage (14).
PCT/JP2005/016259 2004-12-21 2005-09-05 Dispositif de reglage de distribution WO2006067896A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004-369647 2004-12-21
JP2004369647A JP2006177212A (ja) 2004-12-21 2004-12-21 バルブタイミング調整装置

Publications (1)

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WO2006067896A1 true WO2006067896A1 (fr) 2006-06-29

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WO (1) WO2006067896A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010196674A (ja) * 2009-02-27 2010-09-09 Hitachi Automotive Systems Ltd 内燃機関のバルブタイミング制御装置
US8499732B2 (en) 2009-02-27 2013-08-06 Hitachi Automotive Systems, Ltd. Valve timing control apparatus for internal combustion engine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105745403B (zh) * 2013-10-01 2018-11-16 日立汽车系统株式会社 内燃机的气门正时控制装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20010022165A1 (en) * 2000-03-18 2001-09-20 Eduard Golovatai-Schmidt Valve timing control apparatus of an internal combustion engine
DE10031974A1 (de) * 2000-06-30 2002-01-10 Bayerische Motoren Werke Ag Hydraulische Drehwinkel-Verstellvorrichtung für eine Steuerwelle einer Brennkraftmaschine
US20020011226A1 (en) * 2000-07-27 2002-01-31 Martin Scheidt Device for varying valve timing of gas exchange valves of internal combustion engines, particularly a hydraulic camshaft adjusting device of a rotary piston type
JP2004257356A (ja) * 2003-02-27 2004-09-16 Aisin Seiki Co Ltd 弁開閉時期制御装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20010022165A1 (en) * 2000-03-18 2001-09-20 Eduard Golovatai-Schmidt Valve timing control apparatus of an internal combustion engine
DE10031974A1 (de) * 2000-06-30 2002-01-10 Bayerische Motoren Werke Ag Hydraulische Drehwinkel-Verstellvorrichtung für eine Steuerwelle einer Brennkraftmaschine
US20020011226A1 (en) * 2000-07-27 2002-01-31 Martin Scheidt Device for varying valve timing of gas exchange valves of internal combustion engines, particularly a hydraulic camshaft adjusting device of a rotary piston type
JP2004257356A (ja) * 2003-02-27 2004-09-16 Aisin Seiki Co Ltd 弁開閉時期制御装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010196674A (ja) * 2009-02-27 2010-09-09 Hitachi Automotive Systems Ltd 内燃機関のバルブタイミング制御装置
US8499732B2 (en) 2009-02-27 2013-08-06 Hitachi Automotive Systems, Ltd. Valve timing control apparatus for internal combustion engine

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