WO2010007712A1 - 可変バルブタイミング調整装置用電磁弁および可変バルブタイミング調整システム - Google Patents
可変バルブタイミング調整装置用電磁弁および可変バルブタイミング調整システム Download PDFInfo
- Publication number
- WO2010007712A1 WO2010007712A1 PCT/JP2009/001246 JP2009001246W WO2010007712A1 WO 2010007712 A1 WO2010007712 A1 WO 2010007712A1 JP 2009001246 W JP2009001246 W JP 2009001246W WO 2010007712 A1 WO2010007712 A1 WO 2010007712A1
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- WIPO (PCT)
- Prior art keywords
- variable valve
- valve timing
- adjusting device
- oil
- spool
- Prior art date
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Classifications
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- 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
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- 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
- F01L1/02—Valve drive
- F01L1/022—Chain drive
-
- 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
- F01L1/02—Valve drive
- F01L1/024—Belt drive
-
- 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
- F01L2001/34426—Oil control valves
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- 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
- F01L2001/34426—Oil control valves
- F01L2001/3443—Solenoid driven oil control valves
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- 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
- F01L2001/34479—Sealing of phaser devices
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- 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
- F01L2001/34483—Phaser return springs
Definitions
- the present invention relates to an electromagnetic valve and a variable valve timing adjusting system for controlling a variable valve timing adjusting device for changing the opening / closing timing of an intake valve and an exhaust valve.
- a vane type variable valve timing device is provided between the timing pulley and the camshaft.
- the operation timing of the intake valve or exhaust valve is shifted relative to the engine rotation, and the exhaust gas.
- the electromagnetic valve 30 includes a spool 41 driven by a solenoid unit 50, and a valve housing 40 that accommodates the spool 41 so as to be slidable in the axial direction and forms a hydraulic path.
- the valve housing 40 includes an oil supply port 45 that is opened and closed by a spool 41 and communicates with an oil supply source, and advance and retard ports 43 and 44 that communicate with a variable valve timing device.
- a communication passage 90 is formed to connect the 45 with the advance side and retard side ports 43 and 44.
- the electromagnetic valve 30 is controlled by closing the hydraulic pressure supply to the variable valve timing device and supplying a minute flow rate in the intermediate holding operation of the variable valve timing device. At that time, there is an oil leak from a hydraulic path or the like, and the stability of the intermediate holding operation is lowered. Therefore, in Patent Document 1, a communication passage 90 is provided to supply an oil amount that compensates for an oil amount that leaks from a hydraulic path or the like, thereby ensuring stability in the intermediate holding operation of the variable valve timing adjusting device.
- the oil supply amount can be increased through the communication path in the intermediate holding operation of the variable valve timing device.
- the solenoid valve supplies a large amount of oil to the oil supply port.
- the advance port is on the oil supply side
- oil is supplied through the communication passage, but the retard port is on the oil discharge side, so the oil supply port is connected through the communication passage.
- the amount of oil leakage increases as a whole solenoid valve.
- the present invention has been made to solve the above-described problems, and increases the amount of oil leakage as a whole solenoid valve when the variable valve timing adjusting device is operated to the advance side or the retard side.
- an electromagnetic valve for a variable valve timing adjusting device and a variable valve timing adjusting system capable of ensuring a sufficient oil supply amount even when the variable valve timing adjusting device is operated in an intermediate holding state.
- a solenoid valve for a variable valve timing adjusting device includes a cylindrical valve housing in which a plurality of ports for supplying and discharging working fluid are formed in the variable valve timing adjusting device, and an axial movement within the valve housing.
- a spool composed of a plurality of land portions composed of a large diameter portion and a concave portion composed of a small diameter portion connecting the land portions, which adjust the supply / discharge amount of the working fluid flowing through the port according to the movement amount
- a solenoid part that houses a plunger that is a mover of a magnetic circuit that drives the spool, and a working fluid in the vicinity of an intermediate current value at an edge part of a plurality of land parts or a hole edge of a valve housing corresponding to the edge part A groove for adjusting the amount is formed.
- the variable valve timing adjusting device has a cylindrical valve housing in which a plurality of ports for supplying and discharging the working fluid are formed, and moves in the axial direction in the valve housing.
- a spool composed of a plurality of land portions composed of large-diameter portions and concave portions composed of small-diameter portions connecting the land portions for adjusting the supply and discharge amount of the working fluid flowing through the port, and a magnetic circuit for driving the spool
- a solenoid portion that accommodates a plunger that is a mover of the plurality of lands, and a groove portion that adjusts the amount of working fluid in the vicinity of the intermediate current value is formed at the edge portion of the plurality of land portions or the hole edge of the valve housing corresponding to the edge portion.
- variable valve timing control apparatus when the variable valve timing adjusting device is operated in the intermediate holding state, that is, when the solenoid valve is controlled near the intermediate current value, the flow rate of the working fluid It is possible to increase, the variable valve timing control apparatus can be stably controlled. Moreover, the fluid characteristic of the working fluid can be adjusted in the groove. Furthermore, oil leakage can be suppressed when the variable valve timing adjusting device is controlled to the advance side or the retard side.
- FIG. 1 is a diagram illustrating a configuration of a solenoid valve according to Embodiment 1.
- FIG. 3 is a diagram illustrating a configuration of a notch portion of the solenoid valve according to Embodiment 1.
- FIG. 3 is a graph showing a relationship between a solenoid valve current and an oil flow rate according to the first embodiment.
- FIG. 6 is a diagram illustrating a configuration of a solenoid valve according to Embodiment 3.
- FIG. 1 is a diagram illustrating a configuration of a variable valve timing adjustment system according to the first embodiment
- FIG. 2 is a diagram illustrating configurations of a variable valve timing adjustment device and an electromagnetic valve according to the first embodiment. 2 is a cross-sectional view taken along line AA in FIG.
- the variable valve timing (hereinafter referred to as “VVT”) adjustment system includes a camshaft 10 on the exhaust side of the engine, and a relative phase of the camshaft 10 with respect to an engine crankshaft (not shown) provided at the end of the camshaft 10.
- Oil is supplied to the electromagnetic valve 30 via the VVT adjusting device 20 that adjusts the angle, the electromagnetic valve 30 connected by the advance side oil passage 31 and the retard side oil passage 32 formed inside the crankshaft, and the oil supply passage 33.
- the oil pump 34 is configured to supply the oil.
- the VVT adjusting device 20 shields the housing 21 that rotates synchronously with the crankshaft, the case 22 having a plurality of shoes 22 a that protrudes inside to form the hydraulic chamber 23, and the hydraulic chamber 23 of the case 22 from the opposite side of the housing 21.
- the cover 24 and the housing 21, the case 22, and the fastening bolt 25 that fixes the cover 24 together are configured.
- the rotor 26 disposed inside the case 22 protrudes radially outward from the outer peripheral portion of the boss portion 26a and the boss portion 26a to move the hydraulic chamber 23 into the advance side hydraulic chamber 23a and the retard side hydraulic chamber 23b. And a plurality of vanes 26b. Further, a seal member 26c is provided at the tip of each vane 26b of the rotor 26 to contact the shoe 22a and block the flow of oil between the advance side hydraulic chamber 23a and the retard side hydraulic chamber 23b. . Between the seal member 26c and the advance side hydraulic chamber 23a, the relative position between the outer rotating body such as the housing 21, the case 22, and the cover 24 and the rotor 26 that is the inner rotating body is fixed. A locking mechanism 27 is provided. Further, an assist spring 28 is provided between the vane 26b of the rotor 26 and the shoe 22a of the case 22 to urge the vane 26b in the advance direction.
- the electromagnetic valve 30 includes a cylindrical valve housing 40, a spool 41 accommodated in the valve housing 40, a coil spring 42 that urges the spool 41 to an initial position (solenoid unit 50 side), and an attachment of the coil spring 42.
- a solenoid unit 50 that slides the spool 41 in the direction of the arrow X against the force is schematically configured.
- an advance side port 43 corresponding to the advance side oil passage 31, the retard side oil passage 32, the oil supply passage 33, the advance side drain passage 35, and the retard side drain passage 36, respectively.
- a retard side port 44, an oil supply port 45, an advance side drain port 46, and a retard side drain port 47 are formed.
- the advance angle side port 43 and the retard angle side port 44 are provided at positions obliquely opposite to the oil supply port 45, the advance angle side drain port 46, and the retard angle side drain port 47.
- a first land portion 41a, a second land portion 41b, a third land portion 41c, and a fourth land portion 41d having outer diameters corresponding to the inner diameter of the valve housing 40 are formed on the outer peripheral portion of the spool 41.
- Recesses 41e, 41f and 41g are provided between the portion 41a and the second land portion 41b, between the second land portion 41b and the third land portion 41c, and between the third land portion 41c and the fourth land portion 41d. Are formed respectively.
- the length of the second land portion 41 b in the axial direction of the spool 41 is slightly larger than the opening width of the advance side port 43 of the valve housing 40, and the length of the third land portion 41 c in the axial direction of the spool 41 is It is formed slightly larger than the opening width.
- One end of the valve housing 40 is fixed to the housing of the solenoid unit 50, and the other end of the spool 41 is in contact with the rod 51 in the solenoid unit 50.
- the electromagnetic valve 30 configured as described above generates a magnetic attractive force in the solenoid unit 50 by a control signal output from an ECU (not shown) based on information related to the operating state of the engine.
- the rod 51 moves in the direction of the arrow X, and the spool 41 that is in contact with the end of the rod 51 also slides in the axial direction integrally. Since the sliding stroke amount of the spool 41 changes in proportion to the current value applied in the solenoid unit 50, it can be controlled by changing the current value according to the operating state of the engine. Control is performed to relatively switch between the advance side oil passage 31 and the retard side oil passage 32, the oil supply passage 33, and the advance side drain passage 35 or the retard side drain passage 36 by the sliding movement of the spool 41. Do.
- FIG. 3 is a view showing a configuration of a valve housing and a spool of the solenoid valve according to the first embodiment. Further, FIG. 3 (a) shows a solenoid valve during the retard side operation of the VVT adjusting device, FIG. 3 (b) shows a solenoid valve during the intermediate holding operation, and FIG. 3 (c) shows a solenoid valve during the advance side operation.
- FIG. FIG. 3D is a cross-sectional view taken along the line BB in FIG.
- the spool 41 slides to a predetermined position against the spring force of the coil spring 42 in accordance with the current value applied to the solenoid unit 50.
- the advance angle side oil passage 31 and the advance angle side drain passage 35 communicate with each other, and the oil supply passage 33 and the retard angle side oil passage 32 communicate with each other.
- the oil is introduced into the retarded-side hydraulic chamber 23b via the oil supply path 33 and the retarded-side oil passage 32.
- the advanced-side oil path 31 and the advanced-side drain path Oil is discharged via 35. Note that, even when the VVT adjusting device 20 is controlled to the reference position and the solenoid valve 30 is turned off, the control state of FIG.
- the spool 41 slides to a predetermined position against the spring force of the coil spring 42 in accordance with the current value applied to the solenoid unit 50,
- the oil supply passage 33 maintains a state where it does not communicate with either the advance side oil passage 31 or the retard side oil passage 32. Even when the oil supply passage 33 is not in communication with the advance side and retard side oil passages 31 and 32, the second land portion 41b and the partition portion 40a of the valve housing 40, and the third land portion 41c and the valve housing.
- the flow rate of the oil flowing through the notch parts 60a, 60b, 60c described later is supplied to the advance side oil passage 31 and the retard side oil path 32.
- the spool 41 slides to a predetermined position against the spring force of the coil spring 42 according to the current value applied to the solenoid unit 50.
- the oil supply passage 33 and the advance side oil passage 31 communicate with each other, and the retard side oil passage 32 and the retard side drain passage 36 communicate with each other.
- oil is introduced into the advance side hydraulic chamber 23a via the oil supply passage 33 and the advance side oil passage 31, and the retard side oil passage 32 and the retard side drain passage from the retard side hydraulic chamber 23b. Oil is discharged via 36.
- the notch portion 60 provided in the second land portion 41b and the third land portion 41c will be described with reference to FIGS. 3 (b) and 3 (d).
- Three notches 60a, 60b, 60c are formed at equal intervals on the circumferences of the edge portions 41b ', 41c' facing each other between the second land portion 41b and the third land portion 41c.
- the notch portions 60a, 60b, 60c on the edge portion 41b 'and the notch portions 60a, 60b, 60c on the edge portion 41c' are arranged at opposing positions and formed in the same shape.
- FIG. 4 is a diagram showing a notch portion 60a provided in the edge portion 41c ′ of the third land portion 41c.
- the notch portion 60 a is formed by cutting the edge portion 41 c ′ of the third land portion 41 c into a chord shape, that is, so that the circumferential groove width gradually changes along the axial direction of the spool 41. Further, the notch portion 60a is formed in an arc shape having a semi-circle or less, and the edge portion 41c ′ and the notch portion 60a intersect at an angle of 90 ° or more, so that the occurrence of burrs during processing is suppressed. be able to.
- the notch portion 60 As a method of forming the notch portion 60, for example, a processing method of cutting with an end mill or the like from the radially outward direction of the second and third land portions 41b and 41c, and the like can be mentioned. Since the notch portion 60 can be formed by cutting that enables high-precision processing, the flow rate characteristic of the oil can be adjusted with high accuracy.
- the flow rate of oil supplied from the oil supply passage 33 to the advance side and retard side oil passages 31, 32 can be increased.
- the oil flow rate required to stably maintain the intermediate holding operation of the VVT adjusting device 20 can be sufficiently secured.
- FIG. 5 is a graph showing the relationship between the control current value to the solenoid valve 30 and the oil flow rate in the solenoid valve 30 corresponding to the opening of the solenoid valve 30.
- the opening degree of the advance side oil passage 31 and the retard side oil passage 32 of the electromagnetic valve 30 is determined by a control current value applied from the ECU to the solenoid unit 50 as shown in FIG. That is, when the solenoid valve control current value is in the retarded side region with respect to the center line Y, the oil supply passage 33 communicates with the retarded side oil passage 32 as shown in FIG.
- the hydraulic pressure is supplied to the retarding-side hydraulic chamber 23b, and the oil flow is set so that the hydraulic pressure in the advancing-side hydraulic chamber 23a is discharged.
- the opening degree of the retard side port 44 is increased and the oil flow rate to the retard side hydraulic chamber 23b is increased.
- the notch portions 60 provided in the second and third land portions 41b and 41c are located on the oil supply side where the oil supply passage 33 and the retard side oil passage 32 communicate with each other, and the notches Since the sealing is performed at the inner diameter portion of the valve housing 40 corresponding to the portion 60, the oil is not discharged to the advance side drain passage 35 through the notch portion 60, and the amount of oil leakage increases as the solenoid valve 30 as a whole. None do.
- the oil supply passage 33 communicates with the advance side oil passage 31 as shown in FIG.
- the hydraulic pressure is supplied to the advance side hydraulic chamber 23a, and the oil flow is set so that the hydraulic pressure in the retard side hydraulic chamber 23b is discharged.
- the opening of the advance side port 43 increases and the oil flow rate to the advance side hydraulic chamber 23a increases.
- the notch portions 60 provided in the second and third land portions 41b and 41c are located on the oil supply side where the oil supply passage 33 and the advance side oil passage 31 communicate with each other. Since the sealing is performed at the inner diameter portion of the valve housing 40 corresponding to the portion 60, the oil is not discharged to the retarded-side drain path 36 through the notch portion 60, and the amount of oil leakage increases as the solenoid valve 30 as a whole. None do.
- the intermediate current value indicated by the center line Y becomes the control current value (R point or Q point) according to the operating state of the engine.
- the VVT adjusting device 20 has an assist spring 28 that urges the vane 26b to the advance side as represented by the exhaust side VVT adjusting device, the camshaft 10 may be delayed depending on the operating state of the engine.
- the angular torque and the biasing torque by the assist spring 28 are balanced.
- the solenoid valve 30 is controlled with an intermediate current value (Q point). As shown in FIG.
- the solenoid valve 30 during the intermediate holding operation of the VVT adjusting device 20 is such that the oil supply passage 33 communicates with both the advance side oil passage 31 and the retard side oil passage 32.
- the oil leaking from the clearance between the second land portion 41b and the partition portion 40a and the third land portion 41c and the partition portion 40b is supplied to the advance side hydraulic chamber 23a and the retard side hydraulic chamber 23b.
- the supply flow rate from the solenoid valve 30 is only a leakage from the clearance and is significantly reduced.
- the fluctuation torque on the camshaft 10 acts on the rotor 26, so that the rotor 26 swings in a range of about 2 ° around the target control angle. This swing causes the hydraulic chambers 23a, 23b and Hydraulic pulsations are generated in the oil passages 31 and 32.
- the hydraulic chambers 23a and 23b and the oil passages 31 and 32 in the VVT adjusting device 20 there is oil leaking from the gaps between the component parts, and the hydraulic pulsation may increase the amount of leakage from these gaps. .
- the VVT adjusting device 20 is held in the middle against the retarding torque of the camshaft 10.
- the solenoid valve 30 is always controlled at the point P on the higher current side than the intermediate current value.
- the solenoid valve control current point P
- the oil flow rate greater than the oil flow rate leaking from the clearance portion between the second and third land portions 41b and 41c and the partition portions 40a and 40b is advancing side hydraulic chamber 23a. Therefore, the stability of the intermediate holding operation of the VVT adjustment device 20 is rarely impaired.
- the electromagnetic valve 30 is replaced with the electromagnetic valve. Even when the control is performed in the vicinity of the intermediate current value of the control current, the oil flow rate to the advance side and retard side oil passages 31 and 32 can be increased via the notch portion 60, and the VVT adjusting device 20 can be stabilized. Control becomes possible. Furthermore, the flow characteristics of the oil supplied to the advance side and retard side oil passages 31 and 32 can be made uniform. Furthermore, it is possible to increase the flow rate in the intermediate holding area that is used most frequently when running on an actual vehicle, for example, to prevent contamination and oil sludge generated due to low flow rate and oil stagnation inside the OCV. can do.
- the plurality of notch portions 60 are configured to be discontinuously provided on the circumferences of the edge portions 41b ′ and 41c ′ of the second and third land portions 41b and 41c, An edge portion exists in a part of the land portions 41 b and 41 c, and foreign matter can be prevented from entering the gap between the valve housing 40 and the spool 41.
- the circumferential groove width of the notch portion 60 is configured to gradually change along the axial direction of the spool 41, the electromagnetic valve control current from the vicinity of the intermediate current value.
- the oil flow rate rises quickly, the oil flow rate changes with a slight change in the solenoid valve control current, and the control response performance of the solenoid valve 30 near the intermediate current value is improved.
- the notch portion 60 is formed in an arc shape of a semicircle or less, the notch portion 60 and the edge portions 41b ′ and 41c ′ of the second and third land portions 41b and 41c are provided.
- the crossing can be performed at 90 ° or more, and the generation of burrs can be suppressed when the notch portion 60 is formed and processed.
- the three notch portions 60a, 60b, 60c are formed at equal intervals in the second and third land portions 41b, 41c, they are formed in the housing 40. Even when the positional relationship between each port 43, 44, 45, 46, 47 and the spool 41 is different, the variation in the oil flow rate can be reduced.
- the notch portion 60 is formed and processed by cutting, high-precision processing can be performed by cutting, and the flow rate characteristics of the solenoid valve can be adjusted with high accuracy. it can.
- the configuration is shown in which three notches 60a, 60b, 60c are formed at equal intervals in the circumferential direction of one land 41b, 41c.
- the four notch portions 60 may be formed at equal intervals in the circumferential direction, and the number of the notch portions 60 to be formed is not particularly limited.
- FIG. 6 is a view showing a configuration of a solenoid valve according to Embodiment 2 of the present invention
- FIG. 6 (b) is a sectional view taken along the line CC of FIG. 6 (a).
- the configuration in which the chord-shaped notches 60a, 60b, and 60c are provided on the edge portions 41b ′ and 41c ′ of the second and third land portions 41b and 41c has been described.
- channel 61 in the edge part of the 2nd and 3rd land parts 41b and 41c is shown.
- the taper groove 61 is continuously formed in the circumferential direction on the circumference of each edge portion where the second land portion 41b and the third land portion 41c face each other. Further, the taper groove 61 is a taper-shaped groove whose depth gradually changes along the axial direction of the spool 41, and the groove becomes shallower as it advances toward the second and third land portions 41b and 41c. The groove is formed deeper as it goes to the side of 41f.
- the tapered groove 61 can also be formed by cutting or the like.
- the solenoid valve 30 maintains the state where the oil supply passage 33 is not in communication with either the advance side oil passage 31 or the retard side oil passage 32. To do.
- the flow rate of oil flowing through the tapered groove 61 is supplied to the advance side and retard side oil passages 31, 32. Is done.
- the spool 41 moves in the direction in which the oil supply passage 33 and the retard side oil passage 32 communicate with each other in the solenoid valve 30, and the second and third land portions 41b, 41c. Is located on the oil supply side where the oil supply passage 33 and the retard-side oil passage 32 communicate with each other, so that the oil whose flow rate has increased via the taper groove 61 is advanced side drain. The oil is not discharged into the passage 35, and the amount of oil leakage does not increase as a whole of the solenoid valve 30.
- the spool 41 moves in the direction in which the oil supply passage 33 and the advance side oil passage 31 communicate with each other, and the taper provided in the second and third land portions 41b and 41c. Since the groove 61 is positioned on the oil supply side where the oil supply passage 33 and the advance side oil passage 31 communicate with each other, the oil whose flow rate has increased through the tapered groove 61 is discharged to the retard side drain passage 36. The oil leakage amount of the solenoid valve 30 as a whole does not increase.
- the tapered groove 61 is continuously formed in the circumferential direction on the circumference of the edge portions 41b ′ and 41c ′ of the second and third land portions 41b and 41c. Therefore, even when the control is performed near the intermediate current value of the solenoid valve control current, the oil flow rate to the advance side and retard side oil passages 31 and 32 can be increased via the taper groove 61. Stable control of the VVT adjusting device 20 becomes possible. Furthermore, the flow characteristics of the oil supplied to the advance side and retard side oil passages 31 and 32 can be made uniform. Moreover, since the continuous processing becomes possible and the processing becomes easy, the manufacturing cost can be suppressed.
- the oil flow rate rises from the vicinity of the intermediate current value of the solenoid valve control current.
- the oil flow rate changes with a slight change in the solenoid valve control current, and the control response performance near the intermediate current value of the solenoid valve control current is improved.
- FIG. FIG. 7 is a diagram showing the configuration of the solenoid valve according to Embodiment 3 of the present invention.
- the configuration in which the second and third land portions 41b and 41c are provided with the notch portions 60a, 60b, and 60c or the tapered groove 61 is shown.
- the second and second land portions 41b and 41c are provided.
- connects the 3 land parts 41b and 41c is shown.
- the through hole 62 is formed at the hole edge of the valve housing 40c so that the oil passage between the second land portion 41b and the third land portion 41c communicates with the advance side oil passage 31 and the retard side oil passage 32. Is formed.
- This through hole 62 can also be formed by cutting or the like.
- the spool 41 moves in the direction in which the oil supply passage 33 and the retard side oil passage 32 communicate with each other in the solenoid valve 30, and the penetration formed in the vicinity of the third land portion 41c.
- the hole 62 maintains a state of communicating with the retarded angle side oil passage 32, and the through hole 62 formed in the vicinity of the second land portion 41b is blocked by the second land portion 41b and does not communicate with the advanced angle side oil passage 31. .
- the through hole 62 does not open to the oil discharge side, the oil whose flow rate has increased through the through hole 62 is not discharged to the advance side drain path 35, and the solenoid valve 30 as a whole. The amount of oil leakage will not increase.
- the spool 41 moves in the direction in which the oil supply passage 33 and the advance side oil passage 31 communicate with each other, and the through hole 62 formed in the vicinity of the second land portion 41b advances.
- the through-hole 62 formed in the vicinity of the third land portion 41c is blocked by the third land portion 41c and is not in communication with the retarded-side oil passage 32 while maintaining the state of communicating with the corner-side oil passage 31.
- the through hole 62 does not open to the oil discharge side, the oil whose flow rate has increased through the through hole 62 is not discharged to the retard side drain path 36, and the electromagnetic valve 30 as a whole. The amount of oil leakage will not increase.
- the oil flow rate to the advance side and retard side oil passages 31 and 32 can be increased, and the VVT adjusting device 20 can be stably controlled. Furthermore, the flow characteristics of the oil supplied to the advance side and retard side oil passages 31 and 32 can be made uniform.
- the configuration in which the two through holes 62 are provided in the hole edge of the valve housing 40c is shown.
- the plurality of through holes 62 are spaced substantially evenly in the circumferential direction of the hole edge of the valve housing 40c. You may comprise so that it may provide.
- the solenoid valve for a variable valve timing adjusting device increases the amount of oil leakage as a whole when the variable valve timing adjusting device is operated to the advance side or the retard side.
- a plurality of ports for supplying and discharging the working fluid are formed in the variable valve timing adjusting device so that a sufficient oil supply amount can be secured even when the variable valve timing adjusting device is operated in the intermediate holding state.
- a cylindrical housing that is moved in the axial direction and adjusts the supply and discharge amount of the working fluid that flows through the port according to the movement amount
- Solenoid that houses a spool composed of a small-diameter concavity that connects the land and a plunger that is a mover of a magnetic circuit that drives the spool
- a groove for adjusting the amount of working fluid in the vicinity of the intermediate current value is formed at the edge of the plurality of lands, or at the hole edge of the housing corresponding to the edge. Therefore, it is suitable for use in an electromagnetic valve for a variable valve timing adjusting device provided to relatively rotate the camshaft.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
Description
実施の形態1.
図1は実施の形態1に係る可変バルブタイミング調整システムの構成を示す図、図2は実施の形態1に係る可変バルブタイミング調整装置および電磁弁の構成を示す図である。なお、図2の可変バルブタイミング調整装置は、図1におけるA-A線断面図である。
可変バルブタイミング(以下、VVTと称する)調整システムは、エンジンの排気側のカムシャフト10、カムシャフト10の端部に設けられたエンジンのクランクシャフト(図示せず)に対するカムシャフト10の相対的位相角を調整するVVT調整装置20、クランクシャフト内部に形成された進角側油通路31および遅角側油通路32により接続される電磁弁30、および油供給路33を介して電磁弁30に油を供給するオイルポンプ34などで構成されている。
電磁弁30の進角側油通路31および遅角側油通路32の開度は、図5に示すようにECUからソレノイド部50に印加される制御電流値により決定される。即ち、電磁弁制御電流値が中心線Yに対して遅角側領域にある場合には、図3(a)に示したように油供給路33が遅角側油通路32と連通してVVT調整装置20を遅角方向へ移動させるために遅角側油圧室23bに油圧が供給され、進角側油圧室23aの油圧が排出されるように油の流れが設定される。この遅角側領域では、制御電流値が小さくなれば遅角側ポート44の開度が大きくなり遅角側油圧室23bへの油流量が増える。
排気側VVT調整装置に代表されるようにVVT調整装置20内にベーン26bを進角側に付勢するアシストスプリング28を有している場合には、エンジンの運転状態によって、カムシャフト10の遅角方向のトルクとアシストスプリング28による付勢トルクが釣り合う点が存在する。通常、この釣り合う点でVVT調整装置20を中間保持する場合には、電磁弁30は中間電流値(Q点)で制御される。VVT調整装置20の中間保持動作時の電磁弁30は、図3(b)に示したように油供給路33が進角側油通路31および遅角側油通路32のどちらとも連通しておらず、第2ランド部41bと仕切り部40a、および第3ランド部41cと仕切り部40bとのクリアランス部から漏れ出る油が進角側油圧室23aおよび遅角側油圧室23bに供給されている。
図6は、この発明の実施の形態2に係る電磁弁の構成を示す図であり、図6(b)は図6(a)のC-C線断面図である。上述した実施の形態1では、第2および第3ランド部41b,41cのエッジ部41b´,41c´に弦形状のノッチ部60a,60b,60cを設ける構成を示したが、この実施の形態2では第2および第3ランド部41b,41cのエッジ部にテーパ溝61を設ける構成を示す。
図7は、この発明の実施の形態3に係る電磁弁の構成を示す図である。上述した実施の形態1および2では、第2および第3ランド部41b,41cにノッチ部60a,60b,60cあるいはテーパ溝61を設ける構成を示したが、この実施の形態3では第2および第3ランド部41b,41cに接するバルブハウジング40cに貫通孔62を設ける構成を示す。
Claims (11)
- ロータを進角方向に付勢する付勢部材を備えた可変バルブタイミング調整装置に給排する作動流体量を調整する可変バルブタイミング調整装置用電磁弁において、
前記可変バルブタイミング調整装置に前記作動流体の給排を行う複数のポートが形成された円筒形状のバルブハウジングと、
前記バルブハウジング内を軸方向に移動し、当該移動量に応じて前記ポートを介して流れる前記作動流体の給排量を調整する、大径部からなる複数のランド部と当該ランド部を接続する小径部からなる凹部とで構成されるスプールと、
前記スプールを駆動する磁気回路の可動子であるプランジャを収めるソレノイド部とを備え、
前記複数のランド部のエッジ部、または前記エッジ部に対応するバルブハウジングの穴縁に中間電流値近傍の作動流体量を調整する溝部を形成したことを特徴とする可変バルブタイミング調整装置用電磁弁。 - 溝部は、ランド部の円周方向に連続して形成したことを特徴とする請求項1記載の可変バルブタイミング調整装置用電磁弁。
- 溝部は、スプールの軸方向に沿って深さを徐々に変化させたテーパ形状であることを特徴とする請求項2記載の可変バルブタイミング調整装置用電磁弁。
- 溝部は、ランド部の円周方向に不連続に形成したことを特徴とする請求項1記載の可変バルブタイミング調整装置用電磁弁。
- 溝部は、スプールの軸方向に沿って周方向の溝幅を徐々に変化させた弦形状であることを特徴とする請求項4記載の可変バルブタイミング調整装置用電磁弁。
- 溝部は、ランド部に対して半円以下の円弧状であることを特徴とする請求項5記載の可変バルブタイミング調整装置用電磁弁。
- 溝部は、ランド部の円周方向、またはバルブハウジングの穴縁の円周方向に略均等な間隔で形成したことを特徴とする請求項4記載の可変バルブタイミング調整装置用電磁弁。
- 対向するランド部のエッジ部に同一形状の溝部を形成したことを特徴とする請求項2記載の可変バルブタイミング調整装置用電磁弁。
- 対向するランド部のエッジ部に同一形状の溝部を形成したことを特徴とする請求項4記載の可変バルブタイミング調整装置用電磁弁。
- 溝部は、切削加工により形成することを特徴とする請求項1記載の可変バルブタイミング調整装置用電磁弁。
- クランクシャフトからの駆動力を吸気カムシャフトあるいは排気カムシャフトへ伝達するハウジングと、前記ハウジングに固定され、内部に突出して複数の油圧室を形成する複数のシューを有するケースと、前記吸気カムシャフトあるいは排気カムシャフトの端部に固定され、前記油圧室を進角側油圧室と遅角側油圧室とに区画する複数のベーンを有するロータと、前記ロータを進角方向に付勢する付勢部材とを備えた可変バルブタイミング調整装置と、
前記可変バルブタイミング調整装置の前記進角側油圧室および前記遅角側油圧室に給排する作動流体量を調整する電磁弁とを備え、
前記電磁弁は、
前記可変バルブタイミング調整装置に前記作動流体の給排を行う複数のポートが形成された円筒形状のバルブハウジングと、
前記バルブハウジング内を軸方向に移動し、当該移動量に応じて前記ポートを介して流れる前記作動流体の給排量を調整する、大径部からなる複数のランド部と当該ランド部を接続する小径部からなる凹部とで構成されるスプールと、
前記スプールを駆動する磁気回路の可動子であるプランジャを収めるソレノイド部とを備え、
前記複数のランド部のエッジ部、または前記エッジ部に対応するバルブハウジングの穴縁に中間電流値近傍の作動流体量を調整する溝部を形成することを特徴とする可変バルブタイミング調整システム。
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CN2009801230991A CN102066701B (zh) | 2008-07-17 | 2009-03-19 | 可变阀定时调整装置用电磁阀及可变阀定时调整*** |
US12/989,750 US9689285B2 (en) | 2008-07-17 | 2009-03-19 | Solenoid valve for variable valve timing control devices, and variable valve timing control system |
DE112009001211T DE112009001211T5 (de) | 2008-07-17 | 2009-03-19 | Solenoidventil für Steuereinrichtungen der variablen Ventilzeitsteuerung, und Steuersystem der variablen Ventilzeitsteuerung |
JP2010520734A JP5284358B2 (ja) | 2008-07-17 | 2009-03-19 | 可変バルブタイミング調整装置用電磁弁および可変バルブタイミング調整システム |
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JP5427210B2 (ja) * | 2011-07-05 | 2014-02-26 | 本田技研工業株式会社 | ソレノイドおよび電磁弁 |
JP5655771B2 (ja) * | 2011-09-15 | 2015-01-21 | 株式会社デンソー | 電磁アクチュエータ |
DE102011085693A1 (de) * | 2011-11-03 | 2013-05-08 | Schaeffler Technologies AG & Co. KG | Nockenwellenversteller |
JP6546167B2 (ja) * | 2014-06-30 | 2019-07-17 | 株式会社小松製作所 | ストローク検出装置 |
US10018269B2 (en) * | 2014-10-31 | 2018-07-10 | GM Global Technology Operations LLC | Normally high acting linear force solenoid |
US9797280B2 (en) * | 2015-10-09 | 2017-10-24 | Ford Global Technologies, Llc | Camshaft thrust bearing lubrication system |
JP2019199870A (ja) * | 2018-05-18 | 2019-11-21 | アイシン精機株式会社 | 弁開閉時期制御装置 |
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US20110048348A1 (en) | 2011-03-03 |
JPWO2010007712A1 (ja) | 2012-01-05 |
CN102066701A (zh) | 2011-05-18 |
DE112009001211T5 (de) | 2012-01-12 |
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US9689285B2 (en) | 2017-06-27 |
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