WO2016021328A1 - Valve oléo-hydraulique, et dispositif de commande de réglage de distribution pour moteur à combustion interne mettant en œuvre une valve oléo-hydraulique - Google Patents

Valve oléo-hydraulique, et dispositif de commande de réglage de distribution pour moteur à combustion interne mettant en œuvre une valve oléo-hydraulique Download PDF

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Publication number
WO2016021328A1
WO2016021328A1 PCT/JP2015/068489 JP2015068489W WO2016021328A1 WO 2016021328 A1 WO2016021328 A1 WO 2016021328A1 JP 2015068489 W JP2015068489 W JP 2015068489W WO 2016021328 A1 WO2016021328 A1 WO 2016021328A1
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WO
WIPO (PCT)
Prior art keywords
control valve
hydraulic control
valve
hydraulic
axial direction
Prior art date
Application number
PCT/JP2015/068489
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English (en)
Japanese (ja)
Inventor
保英 ▲高▼田
Original Assignee
日立オートモティブシステムズ株式会社
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Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Priority to JP2016540111A priority Critical patent/JPWO2016021328A1/ja
Publication of WO2016021328A1 publication Critical patent/WO2016021328A1/fr

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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
    • F01L1/356—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 making the angular relationship oscillate, e.g. non-homokinetic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
    • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members

Definitions

  • the present invention relates to, for example, a hydraulic control valve used in a valve timing control device that variably controls the valve timing of an intake valve or an exhaust valve of an internal combustion engine according to an operating state.
  • this hydraulic control valve is a cylindrical valve body that is inserted and disposed inside a vane rotor that is fixed from one axial end of the camshaft in the axial direction, and is accommodated and fixed inside the valve body.
  • a solenoid to be pressed.
  • a plurality of ports communicating with the advance hydraulic chamber, the retard hydraulic chamber, and the like are formed through the peripheral wall along the radial direction.
  • the plurality of communication passages are formed along the axial direction in the axial direction of the outer peripheral surface, and a plurality of communication holes are formed in the end portions and peripheral walls in the axial direction of the communication passages.
  • the spool valve slides in the axial direction by a control current output from the control unit to the solenoid, and controls each communication hole of the sleeve and the opening area of the communication hole via an oil hole formed in the peripheral wall. It is like that.
  • the communication passage and each port are appropriately communicated, so that the oil pumped from the oil pump is retarded from the advance hydraulic chamber of the vane rotor.
  • the hydraulic chamber is selectively supplied and discharged to change the relative rotational phase of the camshaft with respect to the crankshaft.
  • An object of the present invention is to provide a hydraulic control valve that does not require high dimensional accuracy of components while improving the degree of freedom of the layout in the axial direction of the port.
  • the invention according to claim 1 is provided with a cylindrical valve body in which a plurality of ports through which hydraulic fluid flows in the radial direction of the peripheral wall is formed, and is slidable in the axial direction inside the valve body.
  • a cylindrical shape in which a plurality of communication holes communicating with the plurality of ports are formed along the radial direction according to the sliding position, and a communication path communicating with each communication hole is formed along the inner axial direction.
  • a partition member that is housed and fixed in the inner axial direction of the spool valve and partitions the communication passage into a plurality of passage portions from the radial direction.
  • the present invention it is possible to reduce the manufacturing cost because high dimensional accuracy of the component parts is not required while improving the degree of freedom of the layout in the axial direction of the port.
  • FIG. 1 is an overall configuration diagram showing a cross section of a valve timing control apparatus to which a hydraulic control valve according to the present invention is applied. It is a front view which shows the state by which the vane rotor provided to this embodiment was hold
  • FIG. 5 is a sectional view taken along line AA in FIG. 4. It is a front view of the valve body provided for this embodiment.
  • FIG. 6 is a longitudinal sectional view on the valve body side showing a state in which the spool valve of the electromagnetic switching valve provided in the present embodiment has moved to the maximum rightward position, where A is a sectional view taken along line BB in FIG.
  • FIG. 6 is a sectional view taken along line CC of FIG. 6 is a longitudinal sectional view on the valve body side showing a state in which the spool valve of the electromagnetic switching valve provided in the present embodiment has moved to an intermediate position in the axial direction, where A is a sectional view taken along line BB in FIG.
  • FIG. 6 is a sectional view taken along line CC of FIG.
  • FIG. 6 is a longitudinal sectional view on the valve body side showing a state where the spool valve of the electromagnetic switching valve provided in the present embodiment has moved to the maximum leftward position, where A is a sectional view taken along line BB in FIG. FIG. 6 is a sectional view taken along line CC of FIG.
  • the valve timing control device is arranged along a longitudinal direction of the engine, and a sprocket 1 that is a driving rotary body that is rotationally driven by a crankshaft of the engine via a timing chain (not shown). And is arranged between the intake side camshaft 2 provided so as to be rotatable relative to the sprocket 1 and between the sprocket 1 and the camshaft 2, and converts the relative rotational phase of the both 1 and 2.
  • the sprocket 1 is formed in a substantially thick disk shape, has a gear portion 1a around which the timing chain is wound, and is configured as a rear cover that closes a rear end opening of the housing described later. In the center, a support hole 1b through which the one end 2a of the camshaft 2 is rotatably supported is formed.
  • the camshaft 2 is rotatably supported by a cylinder head 01 via a plurality of cam bearings 02, and a plurality of egg-shaped rotary cams for opening an intake valve, which is an unillustrated engine valve, are shafts on the outer peripheral surface.
  • a bolt hole 6 into which a cam bolt 50 to be described later is screwed is formed in the direction of the internal axis of the one end portion 2a.
  • the bolt hole 6 is formed along the internal axial direction from the distal end side of the one end portion 2a, and is formed to have a stepped diameter from the opened front end side toward the inner bottom portion.
  • a large diameter portion 6a having a diameter, a stepped portion 6b formed in a tapered shape from the rear end of the large diameter portion 6a, and a female screw portion 6c formed from the rear end to the rear end portion of the stepped portion 6b. And is composed of.
  • the phase change mechanism 3 includes a housing 7 that is integrally provided on the sprocket 1 in the axial direction, and a later-described valve body that becomes a cam bolt at one end 2 a of the camshaft 2.
  • a vane rotor 9 which is a driven rotating body fixed in an axial direction through 50 and rotatably accommodated in the housing 7 and an operation chamber inside the housing 7 are arranged on an inner peripheral surface of a housing body 7a described later.
  • a retarded hydraulic chamber 11 and an advanced hydraulic chamber 12 which are a retarded working chamber and an advanced working chamber, respectively, which are separated by four protruding shoes 10 and the vane rotor 9.
  • the housing 7 includes a cylindrical housing body 7a integrally formed of sintered metal, a front cover 13 that is formed by press molding and closes the front end opening of the housing body 7a, and a rear cover that closes the rear end opening. It is comprised from the said sprocket 1 which is.
  • the housing body 7a, the front cover 13, and the sprocket 1 are fastened and fixed together by four bolts 14 that pass through the bolt insertion holes 10a of the shoes 10.
  • the front cover 13 has a relatively large-diameter insertion hole 13a formed through the center thereof, and seals the inside of each hydraulic chamber 11, 12 with the outer peripheral side inner peripheral surface of the insertion hole 13a. .
  • the vane rotor 9 is integrally formed of a metal material, and has a rotor portion 15 fixed to one end portion 2a of the camshaft 2 by a valve body 50; It consists of four vanes 16a to 16d projecting radially at the interval positions.
  • the rotor portion 15 is formed in a cylindrical shape having a relatively large diameter, and has a bolt insertion hole 15a continuous with the female screw hole 6c of the camshaft 2 in the central internal axial direction. The tip end surface of the one end portion 2a of the shaft 2 is in contact.
  • each of the vanes 16a to 16d is formed with a relatively short protruding length, and is disposed between the shoes 10 and has a circumferential width that is set to be substantially the same. It is formed in a plate shape. Seal members 17a and 17b for sealing between the inner peripheral surface of the housing body 7a and the outer peripheral surface of the rotor portion 15 are provided on the outer peripheral surfaces of the vanes 16a to 16d and the tips of the shoes 10, respectively. .
  • the vane rotor 9 rotates relative to the retard side as shown by a one-dot chain line in FIG. 2, the projecting surface 10b formed on the opposing side surface of the one shoe 10 that the one side surface of the first vane 16a faces.
  • the rotational position on the maximum retarding angle side is regulated in contact with.
  • the other side surface of the first vane 16a is in contact with the opposite side surface 10c of the other shoe 10 and the maximum advance angle side rotation is performed.
  • the position is regulated.
  • the other vanes 16b to 16d are in a separated state without coming into contact with the facing surfaces of the shoes 10 whose both side surfaces face each other in the circumferential direction. Therefore, the contact accuracy between the vane rotor 9 and the shoe 10 is improved, and the supply speed of hydraulic pressure to each of the hydraulic chambers 11 and 12 to be described later is increased, and the forward / reverse rotation response of the vane rotor 9 is increased.
  • the retard hydraulic chambers 11 and the advance hydraulic chambers 12 described above are defined between both side surfaces of the vanes 16a to 16d in the forward / reverse rotation direction and both side surfaces of the shoes 10, respectively.
  • the angle hydraulic chamber 11 and each advance hydraulic chamber 12 are respectively connected to a hydraulic circuit 5 described later via a retard side communication passage 11a and an advance side communication passage 12a formed substantially radially inside the rotor portion 15. Communicating with
  • the lock mechanism 4 holds the vane rotor 9 at the most retarded angle rotation position (the one-dot chain line position in FIG. 2) with respect to the housing 7.
  • the lock mechanism 4 includes a lock hole constituting portion 1c (described only in FIG. 1) that is press-fitted and fixed at a predetermined position on the inner peripheral side of the sprocket 1, and the lock hole.
  • the lock hole 24 formed in the component 1c and the sliding hole 27 formed in the inner axial direction of the first vane 16a having the maximum width of the vane rotor 9 are provided so as to be capable of moving forward and backward, and a small-diameter distal end portion 25a is provided.
  • a lock pin 25 that engages and disengages with each lock hole 24, a coil spring 26 that urges the lock pin 25 toward the lock hole 24, and the lock pin 25 that is formed inside the lock hole 24 and that is supplied with hydraulic pressure.
  • a release pressure receiving chamber (not shown) that releases the engagement by retreating each lock hole 24 against the spring force of the coil spring 26, and a lock passage for supplying hydraulic pressure to the release pressure receiving chamber , It is composed mainly from.
  • the lock hole 24 is formed in a circular shape having a diameter sufficiently larger than the outer diameter of the small-diameter tip portion 25a of the lock pin 25, and the rotation of the inner side surface of the sprocket 1 on the most retarded side of the vane rotor 9 is performed. It is formed at a position corresponding to the position.
  • the lock pin 25 is moved backward by receiving the hydraulic pressure supplied to the pressure receiving chamber for release on the pressure receiving surface of the tip portion 25a, and the tip portion 25a is moved by the spring force of the coil spring 26 provided on the rear end side.
  • the vane rotor 9 is locked into the housing 7 by engaging with the lock hole 24.
  • release pressure receiving chamber is supplied with the same hydraulic pressure as that supplied to the retard hydraulic chamber 11, and the lock pin 25 is moved backward against the spring force of the coil spring 26 by this hydraulic pressure. It is like that.
  • the hydraulic circuit 5 includes a retard passage 18 for supplying and exhausting hydraulic pressure to and from each retard hydraulic chamber 11 via a retard communication passage 11a, and each advance hydraulic pressure.
  • An advance passage 19 for supplying and discharging hydraulic pressure to and from the chamber 12 via the advance side communication passage 12a, the lock passage for supplying and discharging hydraulic pressure to and from the release pressure receiving chamber, and the respective retard and advance angles
  • An oil pump 20 that selectively supplies hydraulic oil to the passages 18 and 19, and a single electromagnetic switching valve that is a hydraulic control valve that switches between the retard passage 18 and the advance passage 19 according to the engine operating state. 21.
  • each of the retard passage 18 and the advance passage 19 is connected to a retard port 18a and an advance port 19a of a valve body 50, which will be described later, of the electromagnetic switching valve 21, while the other end is disposed on the other end side.
  • the retard angle advance chambers 11a and 12a communicate with the retard angle hydraulic chambers 11 and the advance angle hydraulic chambers 12 respectively.
  • the lock passage communicates with the retard passage 18 so that the hydraulic pressure supplied to and discharged from the retard hydraulic chamber 11 is supplied to and discharged from the release pressure receiving chamber.
  • the oil pump 20 is a general one such as a trochoid pump that is rotationally driven by an engine crankshaft, and hydraulic oil sucked from the oil pan 23 through the suction passage 20b by rotation of the outer and inner rotors. It is discharged through the discharge passage 20a, a part of which is supplied from the main oil gallery M / G to each sliding part of the internal combustion engine, and the other is supplied to the electromagnetic switching valve 21 side. ing.
  • a filtration filter (not shown) is provided on the downstream side of the discharge passage 20a, and excess hydraulic oil discharged from the discharge passage 20a is returned to the oil pan 23 through the drain passage 22 to be appropriate.
  • a non-illustrated flow rate control valve for controlling the flow rate is provided.
  • the electromagnetic switching valve 21 is a three-port, three-position proportional valve, and slides in a bottomed cylindrical valve body 50 and an internal axis direction of the valve body 50.
  • a cylindrical spool valve 51 provided movably, a columnar sleeve 52 that is a partition member inserted and fixed inside the spool valve 51, and a disk-like shape that is press-fitted into one end opening of the spool valve 51.
  • the retainer 53, a valve spring 54 which is elastically mounted between the retainer 53 and the bottom surface of the valve body 50 and biases the spool valve body 51 in the right direction in FIG.
  • a solenoid part 55 which is an actuator provided at one end of the valve body 50 and moves the spool valve 51 in the left direction in the figure against the spring force of the valve spring 54, is mainly constituted. It has been.
  • the valve body 50 is formed of a ferrous metal material and functions as a cam bolt as described above.
  • the hexagonal head 50a on the solenoid part 55 side, and the head A cylindrical shaft portion 50b that extends in the axial direction from the base portion of 50a, and an outer diameter that is formed on the distal end side of the cylindrical shaft portion 50b and that opposes the reduced diameter step portion 6b of the camshaft 2 from the radial direction.
  • the sliding hole 50e is formed mainly in the direction.
  • annular stopper 56 for restricting the maximum sliding position of the spool valve 51 toward the solenoid 55 is press-fitted and fixed to the inner peripheral surface of a large-diameter groove formed on the inner tip side.
  • the cylindrical shaft portion 50b is provided with four retard ports 18a and advance ports 19a formed in the peripheral wall so as to penetrate each other along the cross radial direction.
  • the conical portion 50c has a step-conical introduction chamber 57 formed between the outer peripheral surface and the large-diameter portion 6a and the step portion 6b of the camshaft 2, and a portion of the peripheral wall near the cylindrical shaft portion 50b.
  • An introduction port 58 communicating with the introduction chamber 57 is formed penetrating along the radial direction.
  • the spool valve 51 is made of an aluminum alloy material, and has a holding hole 59 that is a communication path through which the sleeve 52 is inserted and held in the inner axial direction.
  • a first groove groove 60 is formed on the outer peripheral surface between the one side guide portion 51a on the retainer 53 side and the first land portion 51c adjacent to the one guide portion 51a.
  • a second groove groove 61 is formed between the first land portion 51c and the second land portion 51d adjacent thereto so as to communicate with the advance port 19a as appropriate.
  • a third groove groove 62 is formed between the second land portion 51d and the third land portion 51e adjacent to the second land portion 51d.
  • the third groove groove 62 communicates appropriately with the retard port 18a and the advance port 19a.
  • a fourth groove groove 63 communicating with the retard port 18a as appropriate is formed.
  • the first communication hole 60a to the fourth communication hole 63a which are always in communication with the holding hole 59 at predetermined angular positions in the circumferential direction, are radially formed on the respective bottom walls. Each is formed through.
  • the first to fourth communication holes 60a to 63a are formed at predetermined angular positions in the circumferential direction of the groove grooves 60 to 63, and the first and third communication holes 60 and 62 are formed at substantially the same angular position.
  • the second and fourth communication holes 61 and 63 are formed at an angular position of about 90 °.
  • a drain plug 64 is press-fitted and fixed to the open end of the spool valve 51 opposite to the retainer 53.
  • the drain plug 64 is formed in a bottomed cylindrical shape, and the spool valve 51 is disposed at one end in the axial direction.
  • An annular flange portion 64a that is press-fitted and fixed in one end opening of 51 is integrally provided, and a drain hole 64b is formed in the inner axial direction.
  • a pair of opening holes 64c communicating with the drain hole 64b and the outside are formed at a substantially central position in the axial direction of the drain plug 64 along the radial direction.
  • the flange portion 64 a is press-fitted and fixed to one end opening portion of the spool valve 51, and cooperates with the retainer 53 to hold both end edges of the sleeve 52 from the axial direction to hold the sleeve 52 in the spool valve 51.
  • the movement in the axial direction is regulated.
  • the sleeve 52 is integrally formed of a synthetic resin material in an elongated rod shape, and the outer peripheral surfaces of both axial end portions 52a and 52b formed in a cylindrical shape are held by the spool valve 51.
  • the hole 59 is inserted into and fixed to the inner peripheral surface of the hole 59 through a small clearance or by fitting with a gap, and between the both end portions 52a and 52b, four first to fourth four partition walls 52c having a substantially cross-shaped cross section are provided. It is partitioned into fourth passage portions 65a to 65d.
  • each of the passage portions 65a to 65d is formed in a substantially V-shaped cross section by the partition wall 52c, and is formed long along the axial direction between the both end portions 52a and 52b. ing. Further, both end portions in the axial direction of the first passage portion 65a and the second passage portion 65b formed in an axially symmetric position with the first passage portion 65a are closed by the built-up portions 52d.
  • the third passage portion 65c and the fourth passage portion 65d that is axially symmetric with the third passage portion 65c have a pair of discharge holes 66a and 66b at both ends in the axial direction. The discharge hole 66a on the end side always communicates with the drain hole 64b of the drain plug 64.
  • Each of the passage portions 65a to 65d appropriately communicates with the fourth communication hole 63a of the fourth groove groove 63 on the retard passage 18 side according to the axial sliding position of the spool valve 51.
  • the second communication groove 61a of the second groove groove 61 on the advance angle passage 19 side communicates with the second communication hole 61a as appropriate.
  • the retainer 53 is press-fitted and fixed to the inner peripheral surface of the open end of the one end portion 51a of the spool valve 51, and a through hole 53a is formed through the center of the retainer 53.
  • the solenoid portion 55 includes a solenoid casing 71 fixed to a chain cover (not shown) with a bolt 70 via a bolt 70, and is housed and held inside the solenoid casing 71, so as to control the engine.
  • ECU A coil 72 from which a control current is output from 37, a cylindrical fixed yoke 73 fixed to the inner peripheral side of the coil 72, and an axially slidable inside the fixed yoke 73
  • the movable plunger 74 is integrally formed with the distal end portion of the movable plunger 74, and the distal end portion 75 a abuts against the drain plug 64 in the axial direction, and resists the spring force of the valve spring 54.
  • 1 mainly includes a drive rod 75 that presses 51 in the left direction in FIG.
  • the solenoid casing 71 is held in the holding hole of the chain cover by a seal ring 76, and a synthetic resin connector 77 having a terminal 78 electrically connected to the ECU 37 at the rear end side. Is attached.
  • the solenoid unit 55 moves the spool valve 51 to three positions in the front-rear axis direction by the relative pressure between the control current of the ECU 37 and the valve spring 54, and
  • the spool valve 51 communicates with the second groove groove 61 to the fourth groove groove 63 (second communication hole 61a to fourth communication hole 63a) and the retardation port 18a and the advance port 19a corresponding to the radial groove in the radial direction.
  • the open ends of the retard port 18a and the advance port 19a are closed by the land portions 51c to 51e to block communication.
  • the first groove groove 60 and the introduction port 58 are always in communication at any sliding position of the spool valve 51. Therefore, the hydraulic pressure discharged from the oil pump 20 is introduced from the introduction chamber 57 to the introduction port 58.
  • the first groove groove 60 (first communication hole 60a) is always supplied into the first and second passage portions 65a and 65b of the sleeve 52.
  • an internal computer detects a crank angle sensor (engine speed detection), an air flow meter, an engine water temperature sensor, an engine temperature sensor, a throttle valve opening sensor, and a current rotation phase of the camshaft 2 which are not shown.
  • Information signals from various sensors such as a cam angle sensor are input to detect the current engine operating state, and as described above, a control current is output to the coil 72 of the electromagnetic switching valve 21 or the current supply is cut off.
  • the movement position of the spool valve 51 is controlled to selectively switch the ports.
  • the energization to the solenoid unit 55 is also cut off, so that the spool valve 51 has a spring force of the valve spring 54 as shown in FIG. Is held at the maximum rightward position (first position).
  • the advance port 19a of the valve body 50 is communicated with the second groove groove 61 (second communication hole 61a) of the spool valve 51 by the spool valve 51, and the third and fourth passage portions 65c of the sleeve 52 are communicated. , D are communicated (see FIG. 7A).
  • the introduction port 58 communicates with the first groove groove 60 (first communication hole 60a), the first and second passage portions 65a and 65b, and the passage portions 65a and 65b and the retardation port 18a. Communication is made (see FIG. 7B).
  • the hydraulic oil in the advance hydraulic chamber 12 passes through the second communication hole 61a from the advance port 19a and is discharged from the third and fourth passage portions 65c and 65d. It is discharged to the outside through the drain hole 64b and the opening hole 64c of the drain plug 64 through 66a. Thereby, the inside of each advance hydraulic chamber 12 becomes a low pressure.
  • the oil pump 20 is also stopped, so that no hydraulic pressure is supplied to the retard / advance hydraulic chambers 11 and 12, so that the vane rotor 9 is connected to the camshaft 2. Due to the negative alternating torque acting, as shown by the one-dot chain line in FIG. 2, the sprocket 1 rotates relative to the counterclockwise direction (most retarded angle direction). Therefore, the intake valve is controlled so that the valve timing is the most retarded phase.
  • each retarded hydraulic chamber 11 is in a high pressure state. Accordingly, since the vane rotor 9 is maintained in the state of relative rotation to the most retarded position, the valve timing of the intake valve is controlled to the retard side. Therefore, the engine startability is improved.
  • each of the retarded hydraulic chamber 11 and the advanced hydraulic chamber 12 has no hydraulic oil discharged from the inside thereof, and at the same time, the hydraulic fluid pumped from the oil pump 20 As shown in FIG. 8B, the supply to the hydraulic chambers 11 and 12 is interrupted.
  • the vane rotor 9 is held at an intermediate position between the most retarded angle and the most advanced angle, as shown by the solid line in FIG. Therefore, the valve timing of the intake valve is controlled to an intermediate phase between the most retarded angle and the most advanced angle, so that the engine rotation can be stabilized and fuel consumption can be improved during steady operation.
  • the introduction port 58 and the first groove groove 60 communicate with each other, and the first communication hole 60a communicates with the first and second passage portions 65a and 65b and the advance port 19a.
  • each retarded hydraulic chamber 11 passes through the fourth communication hole 63a, the third and fourth passage portions 65c, 65d from the retard port 18a, and the discharge hole 66a.
  • the water is discharged to the outside through the drain hole 64b and the opening hole 64c.
  • the inside of each retarded hydraulic chamber 11 becomes a low pressure.
  • the hydraulic fluid pumped from the oil pump 20 to each advance hydraulic chamber 12 passes through the first passage hole 60a, the first and second passage portions 65a, 65b, etc., as indicated by arrows in FIG. 9B. When supplied, each advance hydraulic chamber 12 becomes high pressure.
  • the vane rotor 9 rotates in the clockwise direction and relatively rotates to the maximum advance side, as indicated by the two-dot chain line in FIG.
  • the valve timing of the intake valve becomes the most advanced angle phase
  • the valve overlap of the exhaust valve increases
  • the intake charging efficiency increases
  • the output torque of the engine can be improved.
  • the ECU 37 controls the movement of the spool valve 51 in the axial direction by energizing or shutting off the electromagnetic switching valve 21 with a predetermined energization amount in accordance with the operating state of the engine, thereby controlling the first position. Control to the third position. As a result, the phase change mechanism 3 and the lock mechanism 4 are controlled to control the camshaft 2 to the optimum relative rotational position with respect to the sprocket 1, so that the valve timing control accuracy can be improved.
  • the spool valve 51 is slidably provided in the valve body 50, and the sleeve 52 having a relatively simple passage portion is fixed inside the spool valve 51.
  • the entire structure of the switching valve 21 can be simplified.
  • the sleeve 52 is merely fixed in the spool valve 51, high dimensional accuracy is not required for the sleeve 52, so that the manufacturing work cost can be reduced also in this respect.
  • the sleeve 52 does not require the high dimensional accuracy and can be formed of a synthetic resin material, so that the weight of the electromagnetic switching valve 21 can be reduced.
  • the metal spool valve 51 and the synthetic resin sleeve 52 have different coefficients of thermal expansion, when the temperature of the hydraulic oil (engine oil) is low at the time of cold start, for example, Although the clearance between 51 and 52 increases, when the temperature becomes higher than a predetermined temperature during steady operation, the thermal expansion coefficient on the sleeve 52 side increases and the clearance decreases. That is, the outer peripheral surfaces of both end portions 52a and 52b of the sleeve 52 and the outer end surfaces of the four cross-shaped partition walls 52c are in close contact with the inner peripheral surface of the spool valve 51, thereby reducing the clearance.
  • first passage portion 65a and the second passage portion 65b partitioned by the sleeve 52, and the third passage portion 65c and the fourth passage portion 65d are respectively formed at axially symmetric positions, and these first and second passage portions are formed. Since the hydraulic pressure flowing through the passage portions 65a and 65b is for supply and the hydraulic pressure flowing through the third and fourth passage portions 65c and 65d is for discharge and the hydraulic pressure is of the same system, it acts on the sleeve 52. You can balance the pressure.
  • the axial length of the bolt hole 6 of the one end portion 2a of the camshaft 2 can be shortened. For this reason, it is possible to suppress a decrease in rigidity on the one end 2a side of the camshaft 2, and in particular, it is possible to suppress a decrease in torsional rigidity.
  • valve body 50 is formed such that the outer diameter of the tip end portion (conical portion 50c) is smaller than the inner diameter of the bolt hole 6 of the camshaft 2, the introduction chamber 57 and the like are formed using this space portion. It becomes possible to do. For this reason, the flow path structure comprised by the said introduction chamber 57, the introduction port 58, etc. can be simplified.
  • the single electromagnetic switching valve 21 performs two functions for controlling the hydraulic pressure to the retard hydraulic chamber 11 and the advanced hydraulic chamber 12 and controlling the hydraulic pressure to the release pressure receiving chamber. Therefore, the degree of freedom of layout on the engine body is improved and the cost can be reduced.
  • each passage hole is closed by the sliding position of the spool valve 51 of the electromagnetic switching valve 21 and the vane rotor 9 is held at the intermediate phase position, this holding property is improved.
  • the present invention is not limited to the configuration of the above embodiment, and the case where the hydraulic control valve is applied to a valve timing control device has been shown.
  • a valve timing control device for example, an automatic transmission of a vehicle, etc. It is also possible to apply to other devices.
  • valve timing control device can be applied not only to the intake side but also to the exhaust side.
  • the spool valve 51 from an iron-based metal and the sleeve 52 from an aluminum alloy material.
  • the holding hole 59 of the spool valve 51 is divided into four first to fourth passage portions 65a to 65d by the four partition walls 52c having a substantially cross-shaped cross section as described above. If the holding hole 59 is divided into at least two passage portions by the sleeve 52, the hydraulic pressure can be supplied to and discharged from the hydraulic chambers 11 and 12, respectively.

Abstract

L'invention fournit une valve oléo-hydraulique qui améliore le degré de liberté d'aménagement dans une direction axiale de chaque orifice, et qui ne requiert pas une grande précision dimensionnelle pour les composants qui la constituent. Une valve de distribution à commande par électro-aimant (21) est équipée : d'un corps de valve (50) qui consiste en un verrou de came liant un rotor à aubes (9) à une partie extrémité (2a) d'un arbre à came (2) ; d'un distributeur à tiroir cylindrique (51) sous forme de cylindre métallique qui est agencé de manière à permettre son coulissement libre dans la direction axiale à l'intérieur du corps de valve, et qui assure la commutation entre alimentation et évacuation d'une huile de fonctionnement vers une chambre hydraulique de retard (11) et une chambre hydraulique d'avance (12) ; d'un manchon (52) en résine synthétique inséré et fixé dans la partie interne du distributeur à tiroir cylindrique (51) ; et d'une partie solénoïde (55) déplaçant le distributeur à tiroir cylindrique (51) dans la direction axiale. Le manchon (52) est formé de sorte que l'intérieur d'un orifice de support (59) de la partie interne du distributeur à tiroir cylindrique (51), est divisé dans la direction radiale en quatre parties trajets (65a à 65d) par une paroi division (52c) cruciforme en plan transversal, et celles-ci sont destinées à l'alimentation et à l'évacuation de chacune desdites chambres hydrauliques.
PCT/JP2015/068489 2014-08-04 2015-06-26 Valve oléo-hydraulique, et dispositif de commande de réglage de distribution pour moteur à combustion interne mettant en œuvre une valve oléo-hydraulique WO2016021328A1 (fr)

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JP2016540111A JPWO2016021328A1 (ja) 2014-08-04 2015-06-26 油圧制御弁及び該油圧制御弁が用いられた内燃機関のバルブタイミング制御装置

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WO2018100909A1 (fr) * 2016-11-30 2018-06-07 日立オートモティブシステムズ株式会社 Soupape à commande hydraulique et dispositif de commande du réglage de distribution d'un moteur à combustion interne
JP2020056357A (ja) * 2018-10-02 2020-04-09 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置
JP2020159198A (ja) * 2019-03-25 2020-10-01 株式会社デンソー 作動油制御弁およびバルブタイミング調整装置
JP2020159195A (ja) * 2019-03-25 2020-10-01 株式会社デンソー 作動油制御弁およびバルブタイミング調整装置

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US7389756B2 (en) * 2005-11-03 2008-06-24 Schaeffler Kg Control valve for an apparatus for variable setting of the control times of gas exchange valves of an internal combustion engine
JP2009063022A (ja) * 2007-09-04 2009-03-26 Denso Corp 電動スプール弁
JP2013068308A (ja) * 2011-09-26 2013-04-18 Hitachi Automotive Systems Ltd 油圧制御弁及びスプール弁体作動状態検出装置

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Publication number Priority date Publication date Assignee Title
US7389756B2 (en) * 2005-11-03 2008-06-24 Schaeffler Kg Control valve for an apparatus for variable setting of the control times of gas exchange valves of an internal combustion engine
JP2009063022A (ja) * 2007-09-04 2009-03-26 Denso Corp 電動スプール弁
JP2013068308A (ja) * 2011-09-26 2013-04-18 Hitachi Automotive Systems Ltd 油圧制御弁及びスプール弁体作動状態検出装置

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018100909A1 (fr) * 2016-11-30 2018-06-07 日立オートモティブシステムズ株式会社 Soupape à commande hydraulique et dispositif de commande du réglage de distribution d'un moteur à combustion interne
CN109983266A (zh) * 2016-11-30 2019-07-05 日立汽车系统株式会社 液压控制阀及内燃机的阀正时控制装置
JPWO2018100909A1 (ja) * 2016-11-30 2019-10-17 日立オートモティブシステムズ株式会社 油圧制御弁及び内燃機関のバルブタイミング制御装置
CN109983266B (zh) * 2016-11-30 2020-11-27 日立汽车系统株式会社 液压控制阀及内燃机的阀正时控制装置
JP2020056357A (ja) * 2018-10-02 2020-04-09 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置
JP2020159195A (ja) * 2019-03-25 2020-10-01 株式会社デンソー 作動油制御弁およびバルブタイミング調整装置
WO2020196403A1 (fr) * 2019-03-25 2020-10-01 株式会社デンソー Soupape de commande d'huile hydraulique et dispositif de réglage de synchronisation de soupape
JP2020159198A (ja) * 2019-03-25 2020-10-01 株式会社デンソー 作動油制御弁およびバルブタイミング調整装置
CN113631799A (zh) * 2019-03-25 2021-11-09 株式会社电装 工作油控制阀和阀正时调整装置
JP7196712B2 (ja) 2019-03-25 2022-12-27 株式会社デンソー 作動油制御弁およびバルブタイミング調整装置
JP7226001B2 (ja) 2019-03-25 2023-02-21 株式会社デンソー 作動油制御弁およびバルブタイミング調整装置
US11649741B2 (en) 2019-03-25 2023-05-16 Denso Corporation Hydraulic oil control valve and valve timing adjustment device
CN113631799B (zh) * 2019-03-25 2023-10-20 株式会社电装 工作油控制阀和阀正时调整装置

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