DE102015113615A1 - Valve timing adjustment system and manufacturing method thereof - Google Patents

Valve timing adjustment system and manufacturing method thereof Download PDF

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Publication number
DE102015113615A1
DE102015113615A1 DE102015113615.5A DE102015113615A DE102015113615A1 DE 102015113615 A1 DE102015113615 A1 DE 102015113615A1 DE 102015113615 A DE102015113615 A DE 102015113615A DE 102015113615 A1 DE102015113615 A1 DE 102015113615A1
Authority
DE
Germany
Prior art keywords
valve timing
solenoid
timing adjusting
oil
radially
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
DE102015113615.5A
Other languages
German (de)
Inventor
Kazuaki NEMOTO
Isao Hattori
Eiji Isobe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
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
Priority to JP2014-171720 priority Critical
Priority to JP2014171720A priority patent/JP6417788B2/en
Application filed by Denso Corp filed Critical Denso Corp
Publication of DE102015113615A1 publication Critical patent/DE102015113615A1/en
Granted legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • F01L2001/34423Details relating to the hydraulic feeding circuit
    • F01L2001/34426Oil control valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • F01L2001/34423Details relating to the hydraulic feeding circuit
    • F01L2001/34426Oil control valves
    • F01L2001/3443Solenoid driven oil control valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • F01L2001/34423Details relating to the hydraulic feeding circuit
    • F01L2001/34426Oil control valves
    • F01L2001/34433Location oil control valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • F01L2001/3445Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453Locking means between driving and driven members

Abstract

A valve timing adjusting system (1) includes a solenoid (90) located on an axial side of a valve timing adjusting device (20). A solenoid cover (91) surrounding a radially outer side of the solenoid (90) extends toward the valve timing adjusting means (20) and is coupled to a radially inner side surface (271) of a valve timing adjusting means housing (21) (20) slidably fitted. Misalignment between the solenoid cover (91) and the valve timing adjusting means (20) in a radial direction is thereby limited.

Description

  • TECHNICAL AREA
  • The present disclosure relates to a valve timing adjusting system and a method of manufacturing the valve timing adjusting system.
  • BACKGROUND
  • A known valve timing adjusting system changes a relative rotational phase between a drive shaft of an internal combustion engine and a driven shaft to be driven by the drive shaft by an opening and closing timing of valves driven by the driven shaft will adapt.
  • A valve timing adjusting system of DE 10 2004 062 037 A1 For example, a valve timing adjusting device attached to a driven shaft of an internal combustion engine and an electric matching unit located at a position opposite to a valve timing adjusting device side in an axial direction of an axis of rotation of the valve timing adjusting device include , A shaft extending from the electrical matching unit is inserted in a hole formed in a housing of the valve timing adjusting device. An oil seal, which is built on an inner wall of the hole of the housing, limits leakage of oil, which is present in an interior of the housing, from a gap between the shaft and the housing to an exterior of the housing.
  • The valve timing adjusting system of DE 10 2004 062 037 A1 however, has no means for coaxially aligning the valve timing adjusting means and the electrical matching unit relative to one another. Therefore, when the rotational axis of the valve timing adjusting means and the rotational axis of the electrical matching unit are misaligned relative to each other, that is, deviate relatively, a gap may form between the shaft and the oil seal to allow the oil to leak to the exterior of the housing To allow gap.
  • SHORT VERSION
  • The present disclosure is made in view of the foregoing drawbacks, and an object of the present disclosure is to provide a valve timing adjusting system and a manufacturing method thereof, which has misalignment between an axis of a solenoid cap configured in a tubular shape, and a rotation axis of a valve timing adjusting device can limit.
  • According to the present disclosure, there is further provided a valve timing adjusting system comprising a valve timing adjusting means, a solenoid and a solenoid cap. The valve timing adjusting device is integrally rotatable with a drive shaft of an internal combustion engine or a driven shaft to be driven by the drive shaft. The valve timing adjusting means transmits torque from the drive shaft to the driven shaft and changes a relative rotational phase between the drive shaft and the driven shaft by an opening and closing timing of a valve which is driven to be opened and closed by the driven shaft to adapt. The solenoid is placed in an axial direction of an axis of rotation of the valve timing adjusting device on one side of the valve timing adjusting device and facing the valve timing adjusting device. The solenoid controls an operation of driving the valve timing adjusting means. The solenoid cap is configured in a tubular shape and surrounds a radially outer side of the solenoid. The solenoid cover extends toward the valve timing adjusting device and is slidably fitted to a radially inner side surface or a radially outer side surface of the valve timing adjusting device.
  • According to the present disclosure, there is further provided a valve timing adjusting system comprising a valve timing adjusting means, a solenoid and a solenoid cap. The valve timing adjusting device is integrally rotatable with a drive shaft of an internal combustion engine or a driven shaft to be driven by the drive shaft. The valve timing adjusting means transmits torque from the drive shaft to the driven shaft and changes a relative rotational phase between the drive shaft and the driven shaft by an opening and closing timing of a valve which is driven to be opened and closed by the driven shaft to adapt. The solenoid is placed in an axial direction of an axis of rotation of the valve timing adjusting device on one side of the valve timing adjusting device and facing the valve timing adjusting device. The solenoid controls an operation of driving the valve timing adjusting means. The solenoid cap is configured in a tubular shape and surrounds a radially outer side of the solenoid. The solenoid cover extends toward the valve timing adjusting device. and an inner diameter of the solenoid cover is equal to or greater than an inner diameter of a tubular portion of the valve timing adjusting means located on a side where the solenoid is placed.
  • According to the present disclosure, there is provided a manufacturing method of the valve timing adjusting system described above, comprising a connecting step of connecting the valve timing adjusting means to the driven shaft, a centering step of coaxially adjusting the solenoid cap, and the valve timing adjusting means relative to each other, by inserting a tensioner operable with an inner wall of the solenoid cover and an inner wall of the tubular portion of the valve timing adjusting means, from an interior of the solenoid cover into an interior of the tubular portion of the valve timing adjusting means, a solenoid Cover installing step of the solenoid cover to a belt cover, which protects a belt that transmits a torque of the drive shaft to the valve timing adjusting device, after the centering Schr and a solenoid-mounting step of building the solenoid into the interior of the solenoid cover after removing the tensioner from the tubular portion of the valve timing adjuster and the solenoid cover.
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way.
  • 1 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to a first embodiment of the present disclosure; FIG.
  • 2 is a cross-sectional view taken along a line II-II in FIG 1 ;
  • 3 Fig. 12 is a schematic view showing a structure of a driving force transmission system to which the valve timing adjusting system of the first embodiment is applied;
  • 4 is a partially enlarged view of a region IV in FIG 1 ;
  • 5 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to a second embodiment of the present disclosure; FIG.
  • 6 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to a third embodiment of the present disclosure; FIG.
  • 7 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to a fourth embodiment of the present disclosure; FIG.
  • 8th FIG. 10 is a cross-sectional view of a valve timing adjusting system according to a fifth embodiment of the present disclosure; FIG.
  • 9 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to a sixth embodiment of the present disclosure; FIG.
  • 10 FIG. 10 is a cross-sectional view showing a manufacturing method of the valve timing adjusting system according to the sixth embodiment; FIG.
  • 11 FIG. 10 is a flowchart showing a manufacturing method of the valve timing adjustment system according to the sixth embodiment; FIG.
  • 12 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to a seventh embodiment of the present disclosure; FIG.
  • 13 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to the seventh embodiment of the present disclosure; FIG.
  • 14 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to an eighth embodiment of the present disclosure; FIG.
  • 15 FIG. 10 is a cross-sectional view showing a manufacturing method of the valve timing adjusting system according to the eighth embodiment; FIG.
  • 16 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to a ninth embodiment of the present disclosure; FIG.
  • 17 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to FIG 10th embodiment of the present disclosure;
  • 18 is a cross-sectional view taken along a line XVIII-XVIII in 17 showing a key characteristic of the valve timing adjusting system of the tenth embodiment;
  • 19 FIG. 10 is a cross-sectional view showing a key characteristic of a valve timing adjusting system according to an eleventh embodiment of the present disclosure; FIG.
  • 20 FIG. 12 is a cross-sectional view of a valve timing adjusting system according to a twelfth embodiment of the present disclosure; FIG.
  • 21 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to a thirteenth embodiment of the present disclosure; FIG.
  • 22 FIG. 10 is a cross-sectional view of a valve timing adjusting system according to a fourteenth embodiment of the present disclosure; FIG. and
  • 23 FIG. 12 is a cross-sectional view of a valve timing adjusting system according to a fifteenth embodiment of the present disclosure. FIG.
  • DETAILED DESCRIPTION
  • Various embodiments of the present disclosure will be described with reference to the accompanying drawings. In the following embodiments, similar components are indicated by the same reference numerals and are not redundantly described for simplicity.
  • (First embodiment)
  • 1 to 4 show a first embodiment of the present disclosure. A valve timing adjustment system 1 The present embodiment is applied to a driving force transmission system of an internal combustion engine 2 , this in 3 shown is used. In the driving force transmission system is a belt 9 around a pulley 4 attached to a crankshaft 3 (which as a drive shaft of the machine 2 serves), and two pulleys 7 . 8th , each on two camshafts 5 . 6 (which serve as driven shafts) are fixed, wound. A torque is transmitted through the belt 9 from the crankshaft 3 to the camshafts 5 . 6 transfer.
  • The camshaft 5 drives intake valves 10 on, and the camshaft 6 drives exhaust valves 11 at. A valve timing adjusting device 20 the valve timing adjustment system 1 connects the pulley 7 with the belt and also connects a vane rotor 40 with the camshaft 5 , In this way, the valve timing adjusting means rotates 20 the camshaft 5 along with the crankshaft 3 during a predetermined phase difference between the crankshaft 3 and the camshaft 5 is implemented. The valve timing adjusting device 20 changes a relative rotational phase between the crankshaft 3 and the camshaft 5 to an opening and closing timing of the intake valves 10 adapt.
  • As in 1 and 3 is shown has a belt cover 12 a front lid 13 and a rear lid 14 on. The belt cover 12 covers the valve timing adjusting means 20 and the belt 9 , around the pulley 7 the valve timing adjusting device 20 is wound. The belt cover 12 limits the adhesion of, for example, oil to the belt 9 , which is the driving force of the crankshaft 3 to the valve timing adjusting means 20 transfers.
  • An arrow R, in 3 is shown, gives a sense of rotation of the belt 9 at.
  • As in 1 and 2 is shown, the valve timing adjusting system 1 the valve timing adjusting means 20 , a solenoid 90 and a solenoid lid 91 on. The structure of these constituent components of the valve timing adjustment system 1 is described.
  • The valve timing adjusting device 20 has a housing 21 , the wing rotor 40 and an oil pressure control valve 60 on.
  • The housing 21 has a housing wing 22 , a back cover 23 and the pulley 7 on.
  • The housing wing 22 is configured in a tubular shape having a bottom. The housing wing 22 has a front wall 24 , a peripheral wall 25 and a plurality of protrusions 26 on.
  • A center hole 27 is through the front wall 24 of the housing wing 22 educated. The peripheral wall 25 is configured in a tubular shape and extends from an outer peripheral edge portion of the front wall 24 , The projections 26 jump from the peripheral wall 25 radially inward. In an interior of the housing wing 22 is between each adjacent two of the projections 26 which are adjacent to each other in the rotational direction, an oil pressure chamber 30 educated.
  • The back cover 23 has an annular portion 31 and a tubular section 32 on. The annular section 31 is at an opening end of the housing wing 22 placed opposite the front wall. The tubular section 32 extends axially from an inner peripheral edge portion of the annular portion 31 to one side, from the front wall 24 turned away. The back cover 23 has a through hole 33 in an interior of the tubular portion 32 on, and the camshaft 5 is through the through hole 33 added.
  • An O-ring 34 is between the annular section 31 the rear lid 23 and the housing wing 22 placed. The O-ring 34 limits leakage of the oil from inside the housing 21 ,
  • A closure member 35 is between the tubular section 32 the rear lid 23 and the rear lid 14 of the belt cover 12 placed. The closure member 35 limits penetration of oil from an oil spill area 15 which is open to the atmosphere and located in an exterior of the camshaft 5 is in a room 16 that is inside the belt cover 12 located and the belt 9 receives.
  • The pulley 7 has a flange portion 36 and a toothed section 37 on. The flange section 36 is configured in a circular disc shape and on the housing wing 22 together with the rear lid 23 with bolts 38 attached.
  • The toothed section 37 is configured in a tubular shape and extends from an outer peripheral edge portion of the flange portion 36 in the axial direction of the rotation axis and is on a radially outer side of the peripheral wall 25 of the housing wing 22 placed. The belt 9 is around teeth of the toothed section 37 the pulley 7 wound. The housing 21 is therefore rotated by the driving force coming from the crankshaft 3 through the belt 9 is transmitted.
  • The wing rotor 40 is relative to the housing 21 rotatable and at one end portion of the camshaft 5 attached in a manner that is a rotation of the vane rotor 40 relative to the camshaft 40 limited. The wing rotor 40 has a rotor 41 configured in a cylindrical tubular shape, a plurality of vanes 42 and a socket 43 on.
  • The rotor 41 points in a center of the rotor 41 a recording hole 44 on to the oil pressure control valve 60 in the axial direction. The socket 43 is on the rotor 41 on one side, that of the back cover 23 turned away, attached.
  • Each of the wings 42 jumps from the rotor 41 radially outward and divides a corresponding one of the oil pressure chambers 30 in a forwarding chamber 45 and a delay chamber 46 , The advance chambers 45 be through pre-routing oil channels 47 supplied with an oil pressure or the same is drained from it. The delay chambers 46 be through delay oil channels 48 also supplied with the oil pressure or the same is drained from it.
  • Connecting links 49 are at a radially outer wall of the rotor 41 and a radially outer wall of each of the wings 42 built. The closure members 49 limit a flow of oil between a corresponding feed chamber 45 and a corresponding delay chamber 46 , The wing rotor 40 is responsive to the oil pressure with which the Vorverlegungskammern 45 be supplied, and the oil pressure with which the delay chambers 46 be supplied, relative to the housing 21 turned.
  • An arrow showing an advance page in 2 indicates gives a Vorverlegungsrichtung of the wing rotor 40 relative to the housing 21 at. An arrow that has a delay side in 2 indicates, further, a direction of delay of the vane rotor 40 relative to the housing 21 at.
  • A stopper piston 50 is in a hole of the wing rotor 40 received in a manner that causes axial reciprocation of the stopper piston 50 allows. A ring 51 is in a depression of the front wall 24 recorded, and the stopper piston 50 is in the ring 51 insertable. The stopper piston 50 can in the ring 51 by a driving force of a spring 52 be fitted when the vane rotor 40 in a most retarded position relative to the housing 21 is placed.
  • A first pressure chamber 53 and a second pressure chamber 54 are around the stopper piston 50 educated. Either the first pressure chamber 53 or the second pressure chamber 54 stands with the appropriate delay chamber 46 in communication, and the other from the first pressure chamber 53 and the second pressure chamber 54 stands with the corresponding forwarding chamber 54 in connection.
  • If a sum of the oil pressure of the first pressure chamber 53 that is attached to the stopper piston 50 is applied, and the oil pressure of the second pressure chamber 54 that is attached to the stopper piston 50 is created, greater than the driving force of the spring 52 becomes, becomes the stopper piston 50 from the ring 51 away.
  • The oil pressure control valve 60 has a sleeve 61 and a coil 62 on. The sleeve 61 is configured in a tubular bolt shape. The sink 62 is in the sleeve 61 added.
  • The sleeve 61 is through the recording hole 44 of the wing rotor 40 taken up and with a female or internal thread 17 the camshaft 5 screwed in engagement, and a head 63 the sleeve 61 touches the socket 43 of the wing rotor 40 , In this way, the camshaft 5 , the wing rotor 40 and the sleeve 61 attached to each other.
  • As in 1 and 4 is shown, the sleeve has 61 a forwarding gate 64 , a supply gate 65 and a delay gate 66 on, extending through a peripheral wall of the sleeve 61 extend radially and successively in this order from the side of the head 63 are arranged. The sleeve 61 also has a sliding chamber 67 and an axial channel 69 , The sliding chamber 67 axially takes the coil 62 on. The axial channel 69 stands with the sliding chamber 67 and a discharge oil channel 68 the camshaft 5 in connection.
  • The forwarding gate 64 stands with the advance oil channels 47 of the wing rotor 40 in connection.
  • The delay gate 66 stands with the delay oil channels 48 of the wing rotor 40 in connection.
  • The supply gate 65 stands with a supply channel 55 of the wing rotor 40 in connection. The supply channel 55 of the wing rotor 40 stands with an oil pressure supply channel 18 the camshaft 5 in connection. This will be the supply gate 65 through the supply channel 55 of the wing rotor 40 and the oil pressure supply channel 18 the camshaft 5 with oil passing through an oil pump 191 from an oil pan 19 the vehicle is being pumped.
  • The sink 62 is in the sliding chamber 67 the sleeve 61 recorded in a way that a reciprocating motion of the coil 62 in the axial direction.
  • The sink 62 has a front groove and hole section 71 , a middle groove section 72 and a rear groove and hole portion 73 located in an outer peripheral surface of a peripheral wall of the coil 62 are formed and arranged in this order from the front side to the rear side in the axial direction. A first jetty 74 is between the front groove and hole section 71 and the middle groove portion 72 in the outer peripheral surface of the peripheral wall of the coil 62 educated. A second jetty 75 is between the middle groove portion 72 and the rear groove and hole portion 73 in the outer peripheral surface of the peripheral wall of the coil 62 educated.
  • The sink 62 has an inner oil channel 76 in an interior of the coil 62 on. The inner oil channel 76 stands with the sliding chamber 67 the sleeve 61 in connection. The inner oil channel 76 stands with the sliding chamber 67 , the axial channel 69 and the outlet oil channel 68 the camshaft 5 in connection. The inner oil channel 76 stands with an oil reservoir 77 in connection.
  • The oil reservoir 77 stores the oil from a gap between the housing 21 and the wing rotor 40 is unloaded, and / or the oil from the feed oil channels 47 or the delay oil channels 48 unloaded. The oil reservoir 77 stands with the inner oil channel 76 , the sliding chamber 67 , the axial channel 69 and the outlet oil channel 68 the camshaft 5 in connection.
  • A stopper ring 78 that's upside down 63 the sleeve 61 is built, limits a distance of the coil 62 from the sliding chamber 67 the sleeve 61 ,
  • A feather 79 is between the coil 62 and an inner wall of the sliding chamber 67 the sleeve 61 placed. The feather 79 drives the coil 62 towards the stopper ring 78 , An axial position of the coil 62 is determined by an axial position of a press pin 92 of the solenoid 90 that is on one side of the coil 62 located by the spring 79 turned away, determined. The sink 62 can be between corresponding of the ports of the sleeve 61 depending on an axial position of the coil 62 selectively connect.
  • In a case where the vane rotor 40 to the forward side relative to the housing wing 22 phase-controlled, more specifically, the supply port 65 and the advance gate 64 through the middle groove section 72 at the coil 62 in contact with each other, and the delay gate 66 and the inner oil channel 76 stand together through the rear groove and hole section 73 at the coil 62 in connection.
  • In a case where the vane rotor 40 towards the deceleration side relative to the housing wing 22 is phased, are also the supply port 65 and the delay gate 66 each other through the middle groove portion 72 at the coil 62 in conjunction, and the forwarding port 64 and the inner oil channel 76 stand together through the front groove and hole section 71 at the coil 62 in connection.
  • As in 1 is shown is the solenoid lid 91 configured in a tubular shape and attached to the belt cover 12 with bolts 93 built. Every bolt 93 is through a bolt hole 94 of the solenoid cover 91 taken and with a corresponding female thread 121 of the belt cover 12 threadably engaged to the solenoid cover 91 and the belt cover 12 to attach to each other. An inner diameter D1 of the bolt hole 94 of the solenoid cover 91 is larger than an outer diameter D2 of the bolt 93 , Even in a case where the position of the solenoid cover 91 relative to the belt cover 12 slightly different, therefore, the bolt can 93 the solenoid lid 91 and the belt cover 12 attach to each other.
  • The solenoid lid 91 extends from the belt cover 12 to the valve timing adjusting device 20 and is at one of a radially inner side surface and a radially outer side surface of the valve timing adjusting device 20 Slippery fit. In the first embodiment, a radially outer wall of the solenoid cover contacts 91 a radially inner side surface (an inner wall surface) 271 of the center hole 27 the front wall 24 of the housing wing 22 lubricious. That is, a radially outer side surface of the solenoid cover 91 and the radially inner side surface 721 of the housing 21 are fitted to each other lubriciously. To a passport location where the solenoid lid 91 to the valve timing adjusting device 20 is slidably fitted, is hereinafter referred to as a bearing section.
  • An oil lock 95 which is configured into an annular shape is located on a side of the bearing portion on which the solenoid 90 is placed. The oil lock 95 is made of, for example, rubber, elastomer or silicone. The oil lock 95 is on the front wall 24 of the housing 21 Press fit and slidably contacts the outer wall of the solenoid cover 91 , The oil lock 95 limits leakage of oil from the oil reservoir 77 that is between the radially inner side of the solenoid cover 91 and the valve timing adjusting means 20 is formed in the room 16 that is on the outside of the case 21 and the solenoid lid 91 located and the belt 9 receives.
  • In a case where the oil seal 95 on the housing 21 is attached, the oil seal turns 95 integral with the housing 21 , The solenoid lid 91 is on the belt cover 12 with the bolts 93 fastened, each of which through the corresponding bolt hole 94 is included. The housing 21 therefore turns in one piece with the oil seal 95 and slidably contacts the solenoid lid 91 , on the belt cover 12 is attached. At this time, the radially outer side surface (serving as a sliding surface) of the solenoid cover is 91 and the radially inner side surface (serving as a sliding surface) of the housing 21 Slidably fitted to each other. Since there is a small gap between these sliding surfaces, the sliding surfaces become a fraction of the oil in the oil reservoir 77 supplied to enable a suitable sliding movement between the sliding surfaces. A connection between the solenoid cover 91 and the oil seal 95 is further supplied with a proportion of the oil supplied to these sliding surfaces to between the solenoid lid 91 and the oil seal 95 to allow a suitable sliding movement.
  • The above-described bearing portion limits occurrence of deviation between an axis of the tubular solenoid cover 91 and the rotation axis of the valve timing adjusting means 20 , In the case where the oil seal 95 on the housing 21 Therefore, leakage of the oil through the gap between the oil seal can be fixed 95 and the solenoid lid 91 be limited. In a case where the oil seal 95 on the solenoid lid 91 is attached, alternatively, a leakage of the oil through a gap between the oil seal 95 and the radially inner wall of the housing 21 limited.
  • The bearing section is also located on the side of the oil reservoir 77 of the oil seal 95 , The bearing section can therefore be filled with oil from the oil reservoir 77 be supplied.
  • The solenoid 90 is on an axial side of the valve timing adjusting device 20 placed and is the valve timing adjustment device 20 across from. The solenoid 90 is on a radially inner side of the solenoid cover 91 placed. The radially outer side of the solenoid 90 is therefore due to the solenoid lid 91 surround.
  • The solenoid 90 has a solenoid main body 96 and the pressing pin 92 on. The pressing pin 92 stands from the solenoid main body 96 to the side of the coil 62 in front.
  • The solenoid main body 96 is operated by an excitation from an electronic control unit (ECU), not shown, around the press pin 92 to drive axially. The pressing pin 92 can the coil 62 towards the spring 79 press.
  • The oil pressure with which the advance chambers 95 be supplied, and the oil pressure with which the delay chambers 46 be supplied by the movement of the coil 62 controlled. The solenoid 90 thereby controls the operation of driving the valve timing adjusting means 20 ,
  • The housing 21 and the solenoid 90 be through the bearing section, through the solenoid lid 91 and the case 21 is formed, coaxially adjusted relative to each other (coaxially), so that the axis of rotation of the housing 21 and the press pin 92 of the solenoid 90 be placed along the common axis. In this way, the pressing pin 92 of the solenoid 90 the sink 62 along the axis of rotation of the housing 21 is placed, press reliably.
  • The operation of the valve timing adjustment system 1 is described next.
  • <Engine starting time>
  • As in 1 and 2 is shown in a state in which the machine 2 stopped, the stopper piston 50 in the interior of the ring 51 recorded, and the vane rotor 40 becomes at the most retarded position relative to the housing 21 held. In a state immediately after starting the machine 2 become the delay chambers 46 , the forwarding chambers 45 , the first pressure chamber 53 and the second pressure chamber 54 not supplied with a sufficient amount of oil, so the stopper piston 50 is maintained in the accommodated state in which the stopper piston 50 in the interior of the ring 51 is included. It is therefore possible to generate a striking sound by bumping between the housing 21 and the wing rotor 40 due to a fluctuation of the torque applied to the camshaft 5 is created, until a time of supplying the respective oil pressure chambers 30 to limit with the oil.
  • <After the machine starts>
  • After the start of the machine 2 will if any oil pressure chamber 30 from the oil pump 191 supplied with a sufficient amount of oil, the stopper piston 50 from the ring 51 against the driving force of the spring 52 by the oil pressure of the first pressure chamber 53 and the oil pressure of the second pressure chamber 54 away. The rotation of the wing rotor 40 relative to the housing 21 This is made possible.
  • <Time of a feed forward operation>
  • In the advance operation of the valve timing adjusting system 1 take the solenoid 90 a corresponding command from the ECU and removes (or releases) the pressing force that the coil 62 the oil pressure control valve 60 towards the spring 79 pressed. This will make the advance chambers 45 through the supply gate 65 , the forwarding gate 64 and the advance oil channels 47 from the oil pressure supply passage 18 supplied with oil. The oil of the delay chambers 46 in contrast, is through the delay gate 66 and the rear groove and hole portion 73 to the inner oil channel 76 , the oil reservoir 77 and the outlet oil channel 68 discharged. In this way, the oil pressure of Vorverlegungskammern 45 to the wings 42 created, and thereby becomes the vane rotor 40 relative to the housing 21 rotated in the Vorverlegungsrichtung.
  • <Time of a delay operation>
  • In the deceleration operation of the valve timing adjusting system 1 pushes the solenoid 90 the sink 62 the oil pressure control valve 60 through the press pin 92 towards the spring 79 , In this way, the delay chambers become 64 through the supply gate 65 , the delay gate 66 and the delay oil channels 48 from the oil pressure supply passage 18 supplied with oil. The oil of the forwarding chambers 45 In contrast, this is done by the advance oil channels 47 through the forwarding gate 64 and the front groove and hole section 71 to the inner oil channel 76 , the oil reservoir 77 and the outlet oil channel 68 output. In this way, the oil pressure of the delay chambers 46 to the wings 42 created, and thereby becomes the vane rotor 40 relative to the housing 21 rotated in the direction of deceleration.
  • <Intermediate holding mode>
  • If the vane rotor 40 reaches the target phase, limits the oil pressure control valve 60 the output of the oil pressure from the delay chambers 46 and the oil pressure from the advance chambers 45 to the oil pan 19 , At this time, the delay chambers become 46 and the advance chambers 45 through the delay oil channels 48 and the advance oil channels 47 from the oil pressure supply passage 18 supplied with a tiny amount of oil pressure. The wing rotor 40 is thereby kept in the target phase.
  • <Time of a machine stop>
  • If a command, the machine 2 stops during the service life of the valve timing adjustment system 1 is output, the vane rotor 40 relative to the housing 21 rotated in the retard direction by the operation, which is similar to the above-discussed decelerating operation, and the vane rotor 40 is stopped at the most delayed position. In this state, when the operation of the oil pump 191 is stopped to reduce the pressure of the first pressure chamber 53 and a reduction in the pressure of the second pressure chamber 54 to effect the stopper piston 50 by the driving force of the spring 52 in the interior of the ring 51 driven. In this state, the machine becomes 2 stopped.
  • The advantages of the first embodiment are described below.
    • (1) According to the first embodiment, the solenoid cover extends 91 which is configured in the tubular shape and the radially outer side of the solenoid 90 surrounds to the valve timing adjustment device 20 and is slidable to the radially inner side surface 271 of the housing 21 the valve timing adjusting device 20 fit.
  • This will cause the radial positional deviation between the solenoid lid 91 and the valve timing adjusting means 20 limited. That is, misalignment between the axis of the solenoid cover 91 configured in the tubular shape and the rotation axis of the valve timing adjusting means 20 is limited. It is thereby possible to form the gap between the housing 21 and the oil seal 95 or the formation of the gap between the solenoid lid 91 and the oil seal 95 caused by the misalignment between the axis of the solenoid cover 91 and the rotation axis of the valve timing adjusting means 20 causes to be limited. The valve timing adjustment system 1 thus can the oil-tight condition, with the oil seal 95 is implemented, sustained, and can inadvertently oil leakage from the oil reservoir 77 in the room 16 (the room 16 who the belt 9 limit) caused by the misalignment of the axes.
    • (2) In the first embodiment, the oil lock is 95 between the case 21 and the solenoid lid 91 placed.
  • In this way it is possible to inadvertently leak oil into the room 16 that is in the exterior of the case 21 is bound to be caused by the misalignment of the axes. In the valve timing adjusting system 1 of the present embodiment can thereby the belt 9 used to drive the power between the crankshaft 3 and the valve timing adjusting means 20 transferred to.
  • The bearing portion may further include the misalignment between the axis of the solenoid cover 91 and the rotation axis of the valve timing adjusting means 20 limit, and thereby can a wall thickness of the oil seal 95 be uniform in the circumferential direction. The oil lock 95 can thus unintentional oil leakage from the oil reservoir 77 Confidently limiting, which is caused by the misalignment between the axes.
    • (3) In the first embodiment, there is the bearing portion in which the solenoid cover 91 and the valve timing adjusting means 20 fitted together, on the side of the oil seal 95 on the oil reservoir 77 is placed.
  • In this way, the sliding surfaces of the solenoid cover 91 and the valve timing adjusting means 20 , which form the bearing section, supplied by the oil reservoir with oil. Thus, wear of these sliding surfaces is limited. In the valve timing adjusting system 1 This makes it possible for the misalignment between the axis of the solenoid cover 91 and the rotation axis of the valve timing adjusting means 20 to limit.
    • (4) In the first embodiment, the solenoid lid is 91 on the belt cover 12 built.
  • In this way, the vibrations generated by the valve timing adjusting means 20 from the machine 2 to the solenoid lid 91 be transferred through the belt cover 12 absorbed. The valve timing adjustment system 1 Thus, the misalignment between the axis of the solenoid cover 91 and the rotation axis of the valve timing adjusting means 20 limit.
  • Further, according to the first embodiment, the solenoid lid 91 coming from the solenoid 90 is provided separately, to the valve timing adjusting device 20 Slippery fit. At the time of testing the solenoid 90 or at the time of replacing the solenoid 90 can therefore be the solenoid 90 from the solenoid lid 91 be removed while the solenoid lid 91 and the valve timing adjusting means 20 are fitted together. As a result, it is possible to stick the oil of the oil reservoir 77 on the belt 9 to limit.
  • In the first embodiment, the inner diameter D1 of the bolt hole 94 of the solenoid cover 91 larger than the outer diameter D2 of the bolt 93 ,
  • At the time of attaching the solenoid cover 91 and the belt cover 12 with the bolts 93 can thereby a difference between the inner diameter D1 of the bolt hole 94 and the outer diameter D2 of the bolt 93 serve as an adaptation game, the positional deviation between the solenoid lid 91 and the belt cover 12 can absorb. At the time of fixing the bolts 93 in the state where the rotation axis of the valve timing adjusting means 20 and the axis of the solenoid cover 91 Coaxially held, thus, the positional deviation of the solenoid cover 91 relative to the belt cover 12 through the adjustment clearance of the bolt hole 94 of the solenoid cover 91 be absorbed.
  • Second Embodiment
  • 5 shows a second embodiment of the present disclosure. In the second embodiment, the solenoid cover extends 91 from the belt cover 12 to the valve timing adjusting device 20 and is at a radially outer side surface 211 of the housing 21 the valve timing adjusting device 20 Slippery fit. That is, the radially inner side surface of the solenoid cover 91 and the radially outer side surface 211 of the housing 21 Slidably contact each other and thereby form the bearing section.
  • The oil lock 95 is placed on the radially outer side of this bearing section.
  • According to the second embodiment, advantages similar to those of the first embodiment can be obtained.
  • (Third Embodiment)
  • 6 shows a third embodiment of the present disclosure. In the third embodiment, the solenoid cover extends 91 from the belt cover 12 to the valve timing adjusting device 20 and is at a radially outer side surface 212 of the housing 21 the valve timing adjusting device 20 Slippery fit. That is, the radially inner side surface of the solenoid cover 91 and the radially outer side surface 212 of the housing 21 Slidably contact each other and thereby form the bearing section.
  • The oil lock 95 is located on one side of this bearing section, on which the solenoid 90 is placed.
  • According to the third embodiment, advantages similar to those of the first and second embodiments can be obtained.
  • (Fourth Embodiment)
  • 7 shows a fourth embodiment of the present disclosure. In the fourth embodiment, the socket 43 of the wing rotor 40 in a tubular shape having a bottom configured. A tubular section 56 the socket 43 extends through the center hole 27 the front wall 24 of the housing wing 22 and jump from the center hole 27 towards the side of the solenoid 90 in front.
  • In the fourth embodiment, the solenoid cover extends 91 from the belt cover 12 to the valve timing adjusting means 20 and is at a radially outer side surface 431 the socket 43 of the wing rotor 40 Slippery fit. That is, the radially inner side surface of the solenoid cover 91 and the radially outer side surface 431 the socket 43 of the wing rotor 40 Slidably contact each other and thereby form the bearing section.
  • The oil lock 95 is placed on the radially outer side of this bearing section.
  • According to the fourth embodiment, advantages similar to those of the first to third embodiments are obtained.
  • (Fifth Embodiment)
  • 8th shows a fifth embodiment of the present disclosure. In the fifth embodiment, the socket is 43 of the wing rotor 40 through the middle hole 27 the front wall 24 of the housing wing 22 added.
  • In the fifth embodiment, the solenoid cover extends 91 from the belt cover 12 to the valve timing adjusting device 20 and is at a radially inner side surface 432 the socket 43 of the wing rotor 40 Slippery fit. That is, the radially outer side surface of the solenoid cover 91 and the radially inner side surface 432 the socket 43 of the wing rotor 40 Slidably contact each other and thereby form the bearing section.
  • The oil lock 95 is located on the side of this bearing section, on which the solenoid 90 is placed.
  • According to the fifth embodiment, advantages similar to those of the first to fourth embodiments can be obtained.
  • (Sixth Embodiment)
  • 9 to 11 show a sixth embodiment of the present disclosure. In the sixth embodiment, the solenoid cover 91 and the valve timing adjusting means 20 fitted together. As in 9 is shown, however, is an inner diameter D3 of the solenoid cover 91 equal to an inner diameter D4 of the center hole 27 the front wall 24 of the housing wing 22 ,
  • In the sixth embodiment, the center hole is used 27 (more precisely, the wall of the center hole 27 ) of the front wall 24 of the housing wing 22 as an example of "a tubular portion of the valve timing adjusting means located on the side on which the solenoid is placed".
  • A manufacturing method of the valve timing adjusting system of the sixth embodiment is described with reference to FIG 10 and 11 described below.
  • In a connecting step 101 First of all, the vane rotor 40 the valve timing adjusting device 20 through the sleeve 61 configured in the tubular bolt shape with the camshaft 5 connected.
  • In a centering step (further referred to as an aligning step) 102 , as in 10 Next, a tensioner will be shown 200 with an inner wall of the solenoid cover 91 and an inner wall of the center hole 27 of the housing wing 22 is contactable from the inside of the solenoid cover 91 into the interior of the center hole 27 introduced. An outer diameter of the tensioning device 200 used in the sixth embodiment is equal to or slightly smaller than the inner diameter D3 of the solenoid cover 91 and the inner diameter D4 of the center hole 27 of the housing wing 22 along the length of the tensioning device 200 from one axial end to the other axial end of the tensioning device 200 , In this way, the tensioner touches 200 the inner wall of the solenoid lid 91 and the inner wall of the center hole 27 of the housing wing 22 , This will cause the solenoid lid 91 and the valve timing adjusting means 20 relative to each other by the tensioning device 200 Coaxially adjusted (coaxially placed).
  • After the centering step 102 becomes step installing at a solenoid lid 103 the bolt 93 through the bolt hole 94 of the solenoid cover 91 introduced and with the female thread 121 in the belt cover 12 is formed, screwed engaged. In this way, the solenoid lid 91 and the belt cover 12 attached to each other. Since the inner diameter D1 of the bolt hole 94 of the solenoid cover 91 larger than the outer diameter D2 of the bolt 93 is, even in a case where the position of the solenoid cover 91 relative to the belt cover 12 slightly different, the bolt 93 the solenoid lid 91 and the belt cover 12 attach to each other.
  • After attaching the solenoid cover 91 and the belt cover 12 the tensioning device is attached to each other 200 from the middle hole 27 of the housing wing 22 and the solenoid lid 91 away.
  • In a solenoid mounting step 104 then becomes the solenoid 90 in the interior of the solenoid lid 91 built-in. In this way, the manufacture (assembly) of the valve timing adjusting system becomes 1 completed.
  • In the sixth embodiment, the inner diameter D3 of the solenoid cover 91 equal to the inner diameter D4 of the center hole 27 in the valve timing adjustment device 20 formed on the side on which the solenoid 90 is placed.
  • In this way, at the time of manufacture of the valve timing adjusting system 1 the tensioning device 200 from the inside of the solenoid lid 91 in the middle hole 27 of the housing 21 the valve timing adjusting device 20 Introduced to the solenoid lid 91 and the valve timing adjusting means 20 coaxial with each other (coaxially). The solenoid lid 91 and the valve timing adjusting means 20 can thus be assembled while the axis of the solenoid cover 91 and the rotation axis of the valve timing adjusting means 20 coaxially held together.
  • (Seventh Embodiment)
  • 12 and 13 show a seventh embodiment of the present disclosure. In the seventh embodiment, the inner diameter D3 of the solenoid cover 91 larger than the inner diameter D4 of the center hole 27 the front wall 24 of the housing wing 22 ,
  • In the seventh embodiment, the center hole is used 27 (more precisely, the wall of the center hole 27 ) of the front wall 24 of the housing wing 22 as an example of "a tubular portion of the valve timing adjusting means located on the side on which the solenoid is placed".
  • As in 13 is shown, even in a seventh embodiment, similar to the sixth embodiment, at the time of manufacturing the valve timing adjusting system 1 a tensioning device 201 used to the solenoid lid 91 and the valve timing adjusting means 20 coaxial with each other (coaxially).
  • The tensioning device 201 at the time of manufacture of the valve timing matching system 1 of the seventh embodiment, has a portion connected to the inner wall of the solenoid cover 91 is contactable, and a portion which is connected to the inner wall of the center hole 27 of the housing wing 22 is capable of being touched; on. An outer diameter of the section of the tensioning device 201 that with the inner wall of the solenoid cover 91 is contactable, is equal to or slightly smaller than the inner diameter of the solenoid cover 91 , An outer diameter of the section of the tensioning device 201 with the inner wall of the center hole 27 of the housing wing 22 is also equal to or slightly smaller than the inner diameter D4 of the center hole 27 of the housing wing 22 , In this way, the tensioner touches 201 the inner wall of the solenoid lid 91 and the inner wall of the center hole 27 of the housing wing 22 , The solenoid lid 91 and the valve timing adjusting means 20 can thereby relative to each other by the clamping device 201 coaxially adjusted (coaxially placed).
  • According to the seventh embodiment, advantages similar to those of the sixth embodiment can be obtained.
  • (Eighth Embodiment)
  • 14 and 15 show an eighth embodiment of the present disclosure. In the eighth embodiment, the inner diameter D3 of the solenoid cover 91 larger than an inner diameter D5 of the tubular portion 56 the socket 43 of the wing rotor 40 ,
  • In the eighth embodiment, the tubular portion serves 56 the socket 43 of the wing rotor 40 as an example of "a tubular portion of the valve timing adjusting means located on the side on which the solenoid is placed".
  • As in 15 is even in the eighth embodiment at the time of manufacture of the valve timing adjustment system 1 a tensioning device 202 used to the solenoid lid 91 and the valve timing adjusting means 20 coaxial with each other (coaxially).
  • The tensioning device 202 at the time of manufacture of the valve timing adjustment system 1 of the eighth embodiment has a portion connected to the inner wall of the solenoid cover 91 is contactable, and a portion which is connected to the inner wall of the tubular portion 56 the socket 43 of the wing rotor 40 is touchable on. An outer diameter of the section of the tensioning device 202 that with the inner wall of the solenoid cover 91 is contactable, is equal to or slightly smaller than the inner diameter D3 of the solenoid cover 91 , An outer diameter of the section of the tensioning device 202 connected to the inner wall of the tubular section 56 the socket 43 of the wing rotor 40 is also equal to or slightly smaller than the inner diameter D5 of the tubular portion 56 the socket 43 of the wing rotor 40 , In this way, the tensioner touches 202 the inner wall of the solenoid lid 91 and the inner wall of the tubular portion 56 the socket 43 of the wing rotor 40 , The solenoid lid 91 and the valve timing adjusting means 20 can thereby relative to each other by the clamping device 202 coaxially adjusted (coaxially placed).
  • According to the eighth embodiment, advantages similar to those of the sixth and seventh embodiments can be obtained.
  • Ninth Embodiment
  • 16 shows a ninth embodiment of the present disclosure. In the ninth embodiment, the valve timing adjusting means 20 a drain hole 57 on that between the oil spillway 15 and the oil reservoir 77 makes a connection. The oil outlet space 15 located in the exterior of the camshaft 5 and is open to the atmosphere. The drain hole 57 extends in the axial direction of the rotation axis of the valve timing adjusting means 20 through the front wall 24 of the housing wing 22 , the wing rotor 40 and the rear lid 23 ,
  • In the ninth embodiment, the oil from the oil reservoir 77 through the drain hole 57 to the oil spillway 15 be issued. The oil pressure coming from the oil reservoir 77 to the oil lock 95 is created, is thereby reduced. It is thus possible the oil-tight condition, with the oil seal 95 is implemented, and it is thereby possible to oil leakage from the oil reservoir 77 in the room 16 in which the belt 9 is placed, limit.
  • (Tenth embodiment)
  • 17 and 18 show a tenth embodiment of the present disclosure. In the cross-sectional view of 18 is a structure located on the radially outer side of the solenoid cover 91 is omitted for simplicity.
  • In the tenth embodiment, the bearing portion has a plurality of oil grooves 97 on in a radially outer side wall of the tubular section 56 the socket 43 are formed. The oil grooves 97 extend in the axial direction of the rotation axis of the valve timing adjusting device 20 , The oil grooves 97 are successively at generally equal intervals in a circumferential direction of the tubular portion 56 the socket 43 arranged. The oil grooves 97 stand with the oil reservoir 77 in connection.
  • In the tenth embodiment, the sliding surfaces of the solenoid cover 91 and the socket 43 from the oil grooves 97 be supplied with oil. Thus, even after an age, the wear of these sliding surfaces can be limited. This allows the valve timing adjustment system 1 the misalignment between the axis of the solenoid cover 91 and the rotation axis of the valve timing adjusting means 20 limit.
  • Eleventh Embodiment
  • 19 shows a key characteristic of an eleventh embodiment of the present disclosure. In the cross-sectional view of 19 similar to the cross-sectional view of 18 is, the structure is on the radially outer side of the solenoid cover 91 is omitted for simplicity.
  • In the eleventh embodiment, the bearing portion has a plurality of oil grooves 98 on that in a radially inner side wall of the solenoid cover 91 are formed. The oil grooves 98 extend in the axial direction of the solenoid cover 91 , The oil grooves 98 are successively at generally equal intervals in a circumferential direction of the solenoid cover 91 arranged. The oil grooves 98 stand with the oil reservoir 77 in connection.
  • According to the eleventh embodiment, advantages similar to those of the tenth embodiment can be obtained.
  • (Twelfth embodiment)
  • 20 shows a twelfth embodiment of the present disclosure. In the twelfth embodiment, an eyelet (serving as a damper member) 99 in the bolt hole 94 of the solenoid cover 91 built-in. The eyelet 99 is configured in an annular shape and made of rubber, elastomer or silicone. The eyelet 99 is between the inner wall of the bolt hole 94 and the bolt 93 placed.
  • In the twelfth embodiment, the eyelet 99 the vibrations coming from the machine 2 by the valve timing adjusting means 20 to the solenoid lid 91 be conducted, absorb. The valve timing adjustment system 1 Thus, the misalignment between the axis of the solenoid cover 91 and the rotation axis of the valve timing adjusting means 20 limit.
  • Thirteenth Embodiment
  • 21 shows a thirteenth embodiment of the present disclosure. In the thirteenth embodiment, the valve timing adjusting means 20 a support spring 58 on, on a radially outer side of the socket 43 is placed. The support spring 58 is a torsion coil spring. An end part of the support spring 58 is with a pen 59 standing at the front wall 24 of the housing 21 is attached, in engagement, and the other end of the support spring 58 is with a groove 591 in the socket 43 is formed, engaged. The support spring 58 drives the vane rotor 40 relative to the housing 21 in the advance direction.
  • In the thirteenth embodiment, the assist spring 58 in the oil reservoir 77 built-in, so the support spring 58 with the oil of the oil reservoir 77 can be supplied. The wear of the support spring 58 that is caused by aging can thus be limited.
  • (Fourteenth Embodiment)
  • 22 FIG. 14 shows a fourteenth embodiment of the present disclosure. FIG. In the fourteenth embodiment, similarly to the thirteenth embodiment, the valve timing adjusting means 20 the support spring 58 in the oil reservoir 77 on.
  • Further, in the fourteenth embodiment, the radially inner side surface of the solenoid cover contacts 91 and the radially outer side surface 212 of the housing 21 slidably one another to form the bearing section. The oil lock 95 is further built on the side of the bearing portion, which is the solenoid 90 turned away.
  • In the fourteenth embodiment, it is possible to eliminate the misalignment between the axis of the solenoid cover 91 and the rotation axis of the valve timing adjusting means 20 in the valve timing adjusting system 1 that is the support spring 58 has to limit.
  • (Fifteenth Embodiment)
  • 23 FIG. 15 shows a fifteenth embodiment of the present disclosure. FIG. In the fifteenth embodiment, the radially inner side surface of the solenoid cover touch 91 and the radially outer side surface 611 the sleeve 61 slidable each other to form the bearing section. The radially outer side surface 611 Of the head 63 the sleeve 61 , which forms the bearing portion, is configured in a cylindrical tubular shape.
  • The oil lock 95 is also on the side of the bearing section where the solenoid 90 placed, installed.
  • In the fifteenth embodiment, advantages similar to those discussed in the first to fifth embodiments can be obtained.
  • Other Embodiments
    • (1) In the foregoing embodiments, the valve timing adjusting system is 1 , the opening and closing timing of the intake valves 10 adapts, discusses. In another embodiment, the valve timing adjustment system 1 an opening and closing timing of the exhaust valves 11 to adjust.
    • (2) In the foregoing embodiments, the valve timing adjusting means is 20 on the camshaft 5 the machine 2 attached. Alternatively, in another embodiment, the valve timing adjusting device may 20 on the camshaft 5 the machine 2 be attached.
    • (3) In the foregoing embodiments, the oil lock is 95 on the front wall 24 of the housing 21 Slidably attaches and lubricates the outer wall of the solenoid cover 91 , In another embodiment, alternatively, the oil seal 95 by press fitting on the solenoid lid 91 be attached and can the wall of the housing 21 lubricious touch.
  • In such a case, the housing rotates 21 and slidably touches the oil seal 95 attached to the solenoid lid 91 is attached. At this time, the radially outer side surface (serving as the sliding surface) of the solenoid cover is 91 and the radially inner side surface (serving as the sliding surface) of the housing 21 Slidably fitted to each other. Since there is a small gap between these sliding surfaces, the sliding surfaces become a fraction of the oil in the oil reservoir 77 supplied to enable a suitable sliding movement between the sliding surfaces. A connection between the housing 21 and the oil seal 95 is further supplied with a proportion of the oil supplied to these sliding surfaces, to a suitable sliding movement between the housing 21 and the oil seal 95 to enable.
    • (4) In the foregoing embodiments, the oil lock is 95 on the front wall 24 of the housing 21 fixed by press fitting. In another embodiment, alternatively, the oil seal 95 on a groove, not shown, in the front wall 24 of the housing 21 is formed by fitting the oil seal 95 be attached in the groove, not shown, or may be on the front wall 24 of the housing 21 be attached by binding (with a binding agent). Similarly, in the case where the oil cap is attached to the solenoid cap, various methods may be used to attach the cap to the solenoid cap.
  • As discussed above, the present disclosure is not limited to the foregoing embodiments, and the foregoing embodiments may be modified within the spirit and scope of the present disclosure.
  • QUOTES INCLUDE IN THE DESCRIPTION
  • This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.
  • Cited patent literature
    • DE 102004062037 A1 [0003, 0004]

Claims (14)

  1. Valve timing adjustment system comprising: a valve timing adjusting device ( 20 ), which are provided with a drive shaft ( 3 ) of an internal combustion engine ( 2 ) or a driven shaft ( 5 . 6 ) driven by the drive shaft ( 3 ) is rotatable integrally, wherein the valve timing adjusting means ( 20 ) from the drive shaft ( 3 ) to the driven shaft ( 5 . 6 ) transmits a torque and a relative rotational phase between the drive shaft ( 3 ) and the driven shaft ( 5 . 6 ) to an opening and closing timing of a valve ( 10 . 11 ), which is driven by the driven shaft ( 5 . 6 ) to be opened and closed; a solenoid ( 90 ), which is in an axial direction of an axis of rotation of the valve timing adjusting device (FIG. 20 ) on one side of the valve timing adjusting device ( 20 ) is arranged and the valve timing adjustment device ( 20 ), wherein the solenoid ( 90 ) an operation of driving the valve timing adjusting means (FIG. 20 ) controls; and a solenoid lid ( 91 ) which is configured in a tubular shape and a radially outer side of the solenoid ( 90 ), wherein the solenoid lid ( 91 ) to the valve timing adjusting device ( 20 ) and to a radially inner side surface ( 271 . 432 ) or a radially outer side surface ( 211 . 212 . 431 ) the valve timing adjusting device ( 20 ) is slidably fitted.
  2. A valve timing adjusting system according to claim 1, wherein said valve timing adjusting means (14) 20 ) has the following features: a housing ( 21 ), driven by a drive force from the drive shaft ( 3 ) is rotated; and a vane rotor ( 40 ), which has a rotor ( 41 ) attached to the driven shaft ( 5 . 6 ), and a wing ( 42 ) extending from the rotor ( 41 ) extends radially outward and an oil pressure chamber ( 30 ) located in an interior of the housing ( 21 ) is placed in a forwarding chamber ( 45 ) and a delay chamber ( 46 ), wherein the vane rotor ( 40 ) relative to the housing ( 21 ) is rotatable; and the solenoid lid ( 91 ) has a radially inner side surface ( 271 ) or a radially outer side surface ( 211 . 212 ) of the housing ( 21 ), or a radially inner side surface ( 432 ) or a radially outer side surface ( 431 ) of the wing rotor ( 40 ) slidably touched.
  3. Valve timing adjustment system according to claim 2, wherein the vane rotor ( 40 ) a socket ( 43 ) which is configured in a tubular shape and on the rotor ( 41 ) and through a hole in the housing ( 21 ) is formed towards the solenoid ( 90 ) projects; and the solenoid lid ( 91 ) has a radially inner side surface ( 432 ) or a radially outer side surface ( 431 ) of the socket ( 43 ) slidably touched.
  4. Valve timing adjustment system according to claim 2 or 3, comprising an oil lock ( 95 ) which is configured in an annular shape and between the housing ( 21 ) and the solenoid lid ( 91 ), wherein the oil seal ( 95 ) leakage of oil from an oil reservoir ( 77 ) located between a radially inner side of the solenoid cover ( 91 ) and the valve timing adjustment device ( 20 ) is formed into a room ( 16 ) located in an exterior of the housing ( 21 ) and the solenoid cover ( 91 ) is limited.
  5. A valve timing adjusting system according to claim 4, wherein a location at which said solenoid lid 91 ) to the radially inner side surface ( 271 . 432 ) or the radially outer side surface ( 211 . 212 . 431 ) the valve timing adjusting device ( 20 ) is slidably fitted on one side of the oil seal ( 95 ), on which the oil reservoir ( 77 ) is placed.
  6. Valve timing adjustment system according to claim 4 or 5, comprising a support spring ( 58 ) in the oil reservoir ( 77 ) is placed and the vane rotor ( 40 ) relative to the housing ( 21 ) drives in an advancing direction.
  7. Valve timing adjustment system according to one of claims 1 to 6, which has a drain hole ( 57 ) which extends in the axial direction of the rotation axis of the valve timing adjusting means (Fig. 20 ) by the valve timing adjusting device ( 20 ) extends between an oil discharge space ( 15 ), which is open to an atmosphere, and the oil reservoir ( 77 ) make a connection.
  8. Valve timing adjustment system according to one of claims 1 to 7, the at least one oil groove ( 97 ) located in at least one of the solenoid lids ( 91 ) or the valve timing adjustment device ( 20 ) is formed at a location where the solenoid lid ( 91 ) the valve timing adjusting device ( 20 ) is slidably contacted, wherein the at least one oil groove ( 97 ) with the oil reservoir ( 77 ).
  9. Valve timing adjustment system according to one of claims 1 to 8, wherein the solenoid cover ( 91 ) to a belt cover ( 12 ), which is a belt ( 9 ), which is a driving force of Drive shaft ( 3 ) to the valve timing adjusting device ( 20 ) transmits.
  10. Valve timing adjustment system according to claim 9, comprising a bolt ( 93 ) through a bolt hole ( 94 ) of the solenoid cover ( 91 ) and the solenoid cover ( 91 ) and the belt cover ( 12 ), wherein an inner diameter (D1) of the bolt hole (D1) 94 ) of the solenoid cover ( 91 ) greater than an outer diameter (D2) of the bolt ( 93 ).
  11. Valve timing adjustment system according to claim 10, comprising a damper member ( 99 ) which is configured in an annular shape and between an inner wall of the bolt hole ( 94 ) of the solenoid cover ( 91 ) and the bolt ( 93 ) is placed.
  12. A valve timing adjusting system according to any one of claims 1 to 11, including an oil pressure control valve (15). 60 ), which in a center of rotation of the valve timing adjustment device ( 20 ) and changes an oil pressure with which the valve timing adjustment device ( 20 ), wherein the solenoid cover ( 91 ) to a radially outer side surface ( 611 ) of the oil pressure control valve ( 60 ) is slidably fitted, rather than to the radially inner side surface ( 271 . 432 ) or the radially outer side surface ( 211 . 212 . 431 ) the valve timing adjusting device ( 20 ) to be fitted smoothly.
  13. Valve timing adjustment system comprising: a valve timing adjusting device ( 20 ), which are provided with a drive shaft ( 3 ) of an internal combustion engine ( 2 ) or a driven shaft ( 5 . 6 ) driven by the drive shaft ( 3 ) is rotatable integrally, wherein the valve timing adjusting means ( 20 ) from the drive shaft ( 3 ) to the driven shaft ( 5 . 6 ) transmits a torque and a relative rotational phase between the drive shaft ( 3 ) and the driven shaft ( 5 . 6 ) to an opening and closing timing of a valve ( 10 . 11 ), which is driven by the driven shaft ( 5 . 6 ) to be opened and closed; a solenoid ( 90 ), which is in an axial direction of an axis of rotation of the valve timing adjusting device (FIG. 20 ) on one side of the valve timing adjusting device ( 20 ) and the valve timing adjustment device ( 20 ), wherein the solenoid ( 90 ) operation of driving the valve timing adjusting means (16) 20 ) controls; and a solenoid lid ( 91 ) which is configured in a tubular shape and a radially outer side of the solenoid ( 90 ), wherein the solenoid lid ( 91 ) to the valve timing adjusting device ( 20 ), and an inner diameter (D3) of the solenoid cover (FIG. 91 ) equal to or greater than an inner diameter (D4, D5) of a tubular portion ( 27 . 56 ) the valve timing adjusting device ( 20 ) located on a side on which the solenoid ( 90 ) is placed.
  14. A method of manufacturing a valve timing adjusting system according to claim 13, comprising the following steps: a connecting step ( 101 ) for connecting the valve timing adjusting device ( 20 ) with the driven shaft ( 5 ); a centering step ( 102 ) for coaxial adjustment of the solenoid cover ( 91 ) and the valve timing adjustment device ( 20 ) relative to each other by inserting a tensioning device ( 200 . 201 . 202 ) with an inner wall of the solenoid cover ( 91 ) and an inner wall of the tubular portion ( 27 . 56 ) the valve timing adjusting device ( 20 ) is contactable from an interior of the solenoid cover ( 91 ) into an interior of the tubular portion ( 27 . 56 ) the valve timing adjusting device ( 20 ); a solenoid lid incorporating step ( 103 ) for building the solenoid cover ( 91 ) to a belt cover ( 12 ), which has a belt that drives a torque of the drive shaft ( 3 ) to the valve timing adjusting device ( 20 ) transmits, protects, after the centering step ( 102 ); and a solenoid-mounting step ( 104 ) for building the solenoid ( 90 ) into the interior of the solenoid cover ( 91 ) after removal of the tensioning device ( 200 . 201 . 202 ) from the tubular section ( 27 . 56 ) the valve timing adjusting device ( 20 ) and the solenoid lid ( 91 ).
DE102015113615.5A 2014-08-26 2015-08-18 Valve timing adjustment system and manufacturing method thereof Granted DE102015113615A1 (en)

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JP2018135842A (en) 2017-02-23 2018-08-30 アイシン精機株式会社 Valve opening/closing timing control device
JP2020139448A (en) * 2019-02-28 2020-09-03 株式会社デンソー Valve timing adjuster
JP2020159198A (en) * 2019-03-25 2020-10-01 株式会社デンソー Hydraulic oil control valve and valve timing adjuster
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JP2016044652A (en) 2016-04-04

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