WO2018100909A1 - Soupape à commande hydraulique et dispositif de commande du réglage de distribution d'un moteur à combustion interne - Google Patents

Soupape à commande hydraulique et dispositif de commande du réglage de distribution d'un moteur à combustion interne Download PDF

Info

Publication number
WO2018100909A1
WO2018100909A1 PCT/JP2017/037777 JP2017037777W WO2018100909A1 WO 2018100909 A1 WO2018100909 A1 WO 2018100909A1 JP 2017037777 W JP2017037777 W JP 2017037777W WO 2018100909 A1 WO2018100909 A1 WO 2018100909A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
axial direction
sleeve
oil
hydraulic control
Prior art date
Application number
PCT/JP2017/037777
Other languages
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 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 JP2018553705A priority Critical patent/JP6775032B2/ja
Priority to CN201780072543.6A priority patent/CN109983266B/zh
Publication of WO2018100909A1 publication Critical patent/WO2018100909A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/356—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
    • F16K3/26—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 with fluid passages in the valve member

Definitions

  • the present invention relates to a hydraulic control valve and a valve timing control device for an internal combustion engine.
  • Patent Document 1 As a conventional hydraulic control valve, for example, there is one described in Patent Document 1 below used in a valve timing control device for an internal combustion engine.
  • the hydraulic pressure pumped from an oil pump mechanically driven by the internal combustion engine is supplied into the sleeve from a supply port formed at one end of the sleeve in the axial direction.
  • This hydraulic pressure is selectively transferred from the through-opening portion of the sleeve to the retarded working chamber or advanced working chamber in the housing from the through-opening portion of the sleeve or from the advanced port on the advanced side according to the axial movement position of the hollow piston.
  • the relative rotation phase of the camshaft with respect to the sprocket is changed.
  • the present invention has been devised in view of the technical problems of the conventional hydraulic control valve, and an object thereof is to provide a hydraulic control valve capable of reducing the overall size and weight.
  • a cylindrical valve body having a plurality of ports penetrating in the radial direction, a sleeve that is housed and held inside the valve body, and has two oil passages inside, Between the inner periphery of the valve body and the outer periphery of the sleeve, the valve body is disposed so as to be movable in the axial direction, and any of the two systems of oil passages and the plurality of ports according to the axial movement position. And a spool valve that communicates with or shuts off the communication.
  • the hydraulic control valve can be reduced in size and weight.
  • FIG. 1 is an overall configuration diagram of a first embodiment showing a cross section of a valve timing control device applied to an intake side camshaft of an internal combustion engine according to the present invention. It is the whole valve timing control device schematic diagram showing the state where the vane rotor provided for this embodiment was controlled to the rotation position of the most advance angle phase. It is a disassembled perspective view of the hydraulic control valve provided for this embodiment.
  • the sleeve provided for this embodiment is shown partially in cross section, A is an overhead view from the rear, and B is an overhead view from the front. It is a principal part expanded sectional view of this embodiment.
  • the stopper member provided for this embodiment is shown, A is the perspective view seen from the back side, and B is the perspective view seen from the front.
  • each component parts such as a valve body of the hydraulic control valve provided for this embodiment, Comprising: The 1st position of the spool valve is shown. It is a longitudinal section showing the 1st position of a spool valve in the state where hydraulic oil was supplied to the hydraulic control valve of this embodiment. It is a longitudinal cross-sectional view which shows the 2nd position of the spool valve of the hydraulic control valve of this embodiment. It is a longitudinal cross-sectional view which shows the 3rd position of the spool valve of the hydraulic control valve of this embodiment. It is a disassembled perspective view of the hydraulic control valve provided for 2nd Embodiment of this invention. FIG. 14 is a sectional view taken along line AA in FIG. 13.
  • each component parts such as a valve body of the hydraulic control valve provided for this embodiment, Comprising: The 1st position of the spool valve is shown. It is a longitudinal section showing the 1st position of a spool valve in the state where hydraulic oil was supplied to the hydraulic control valve of this embodiment. It is a longitudinal cross-sectional view which shows the 3rd position of the spool valve of the hydraulic control valve of this embodiment.
  • FIG. 1 is a cross-sectional view of a valve timing control device according to a first embodiment applied to the intake side of an internal combustion engine
  • FIG. 2 is an overall configuration diagram of the valve timing control device
  • FIG. 3 is an exploded perspective view of a hydraulic control valve
  • FIG. 5 is an enlarged sectional view of a main part of the present embodiment
  • the valve timing control device is arranged along a timing sprocket 1 that is a driving rotating body that is rotationally driven by a crankshaft of an engine via a timing chain (not shown), and in the longitudinal direction of the engine.
  • the camshaft 2 on the intake side provided so as to be relatively rotatable with respect to the timing sprocket 1 and disposed between the timing sprocket 1 and the camshaft 2 to convert the relative rotational phases of the both 1 and 2
  • the driving rotating body may be a timing pulley to which a rotational force is transmitted by a timing belt.
  • the camshaft 2 is rotatably supported on a cylinder head (not shown) via a plurality of cam bearings, and a plurality of egg-shaped rotary cams for opening an intake valve, which is an engine valve (not shown), are opened on the outer peripheral surface. It is integrally fixed at an axial position.
  • a female screw hole 2b into which a cam bolt (valve body 27) described later is screwed is formed in the inner axial direction of the one end portion 2a of the camshaft 2.
  • the phase changing mechanism 3 is integrally provided in the timing sprocket 1 in the axial direction, and is provided in a housing 6 in which an internal working chamber is formed, and one end 2 a of the camshaft 2, which will be described later.
  • the vane rotor 7 that is a driven rotating body that is fixed from the axial direction through the valve body 27 that is rotatably accommodated in the housing 6 and the working chamber inside the housing 6 include an inner peripheral surface of the housing body 6a described later.
  • Each of which is divided by four shoes 8 and a vane rotor 7, and each of them is provided with a retard working chamber 9 as a first working chamber and an advance working chamber 10 as a second working chamber.
  • the housing 6 includes a cylindrical housing body 11 integrally formed of a so-called sintered metal material formed by sintering powder metal, and a front formed by press molding to close the front end opening of the housing body 11. It is comprised from the cover 12 and the timing sprocket 1 which obstruct
  • the housing body 11 is formed in a substantially cylindrical shape, and four shoes 8 project from the inner peripheral surface, and four bolt insertion holes 11 a are formed in the inner axial direction of the shoes 8. .
  • the timing sprocket 1, the housing body 11, and the front cover 12 are coupled in the axial direction by four bolts 13 that are inserted into the bolt insertion holes 12b and the bolt insertion holes 10a and are screwed into the female screws 1c. Yes.
  • the rotor portion 14 is formed in a relatively large-diameter cylindrical shape, and a bolt insertion hole 14a continuous with the female screw hole 2b of the camshaft 2 is formed through the central inner axial direction. Further, the front end portion of the one end portion 2a of the camshaft 2 is fitted in the circular fitting groove 14b formed on the rear end surface of the rotor portion 14 from the rotation axis direction.
  • Each of the vanes 15a to 15d has a relatively short projecting length in the radial direction, and is disposed between the shoes 8. Further, the three vanes 15b to 15d other than the one vane 15a are formed in a relatively thin plate shape with the circumferential widths set to be substantially the same. The one vane 15a is formed with a large width in the circumferential direction, and a part of the lock mechanism 4 is provided therein.
  • Seal members 16a and 16b for sealing between the inner peripheral surface of the housing body 11 and the outer peripheral surface of the rotor part 14 are provided on the outer peripheral surfaces of the vanes 15a to 15d and the tips of the shoes 8, respectively.
  • the other vanes 15b to 15d are in a separated state without coming into contact with the facing surfaces of the shoes 8 whose both side surfaces face each other in the circumferential direction. Therefore, the contact accuracy between the vane rotor 7 and the shoe 8 is improved, and the supply speed of hydraulic pressure to each of the working chambers 9 and 10 to be described later is increased, and the forward / reverse rotation response of the vane rotor 7 is improved.
  • each retarded working chamber 9 and each advanced working chamber 10 are hydraulic circuits through four retarded passage holes 17 and advanced passage holes 18 formed substantially along the radial direction inside the rotor portion 14. 5 communicates with each other.
  • the lock mechanism 4 holds the vane rotor 7 at the most retarded rotational position (position shown in FIG. 2) with respect to the housing 6.
  • the lock mechanism 4 is formed in a lock hole 19 formed at a predetermined position on the inner surface of the timing sprocket 1 and the inner axial direction of the first vane 15 a of the vane rotor 7.
  • a lock pin 21 which is provided in the pin receiving hole 20 so as to be able to move forward and backward, and has a small-diameter tip portion engaged with and disengaged from the lock hole 19, and a coil spring 22 (not shown) for urging the lock pin 21 toward the lock hole 19.
  • a release pressure receiving chamber (not shown) which is formed inside the lock hole 19 and releases the engagement by moving the lock pin 21 backward from the lock hole 19 against the spring force of the coil spring 22 by the supplied hydraulic pressure.
  • a lock passage 23 for supplying hydraulic pressure to the release pressure receiving chamber.
  • the lock hole 19 is formed in a circular shape that is sufficiently larger in diameter than the outer diameter of the small-diameter tip of the lock pin 21, and at the rotational position of the innermost surface of the timing sprocket 1 on the most retarded side of the vane rotor 7. It is formed in the corresponding position.
  • the lock pin 21 receives the hydraulic pressure supplied to the pressure-receiving chamber for release on the pressure-receiving surface at the tip and moves backward to come out of the lock hole 19 and is unlocked.
  • the tip of the coil spring 22 provided on the rear end side of the lock pin 21 is engaged with the lock hole 19 to lock the vane rotor 7 with respect to the housing 6.
  • this lock position is the rotational position of the vane rotor 7 on the most retarded angle side with respect to the housing 6.
  • the hydraulic circuit 5 is provided in a supply passage 24 formed in the internal axial direction of the camshaft 2 and the internal axial direction of the rotor portion 14, and the downstream side of the supply passage 24.
  • an oil pump 25 that discharges the hydraulic pressure from the discharge passage 25a to the supply passage 24, and an internal pumping direction of the rotor portion 14, and each of the retard passage passage holes with respect to the supply passage 24 according to the engine operating state.
  • 17 and hydraulic pressure control valve 26 for switching the flow path of each advance angle passage hole 18, and the hydraulic oil from each retard angle, advance angle working chamber 9, 10 is discharged to oil pan 51.
  • a discharge passage 43 A discharge passage 43.
  • the oil pump 25 is a general vane type or trochoid type, for example.
  • the hydraulic control valve 26 includes a valve body 27 made of an iron-based metal material that is a cam bolt that fixes the vane rotor 7 to the one end portion 2 a of the camshaft 2 in the axial direction; A sleeve 28 accommodated in a valve hole 27a formed penetrating in the inner axial direction of the valve body 27, and a spool valve 29 disposed between the outer peripheral surface of the sleeve 28 and the inner peripheral surface of the valve hole 27a. And a valve spring 30 that urges the spool valve 29 in the left direction in FIG. 1 and an electromagnetic actuator 31 that is an actuator that pushes the spool valve 29 in the other direction against the spring force of the valve spring 30. It is configured.
  • the valve body 27 is formed into a hollow cylindrical shape by a valve hole 27 a, and a shaft that is inserted into a head portion 27 b having an outer peripheral surface formed as a hexagonal surface and a bolt insertion hole 14 a of the rotor portion 14 of the vane rotor 7.
  • a portion 27c and a male screw portion 27d formed on the outer periphery of the tip portion of the shaft portion 27c and screwed into the female screw hole 2b of the camshaft 2 are configured.
  • the head portion 27 b is disposed in the insertion hole 12 a of the front cover 12 in a state where the valve body 27 is fastened to the camshaft 2, and the seating surface 27 f of the flange portion 27 e on the base side of the shaft portion 27 c is the rotor portion 14.
  • the bolt insertion hole 14a is seated on the peripheral surface on the opening edge side.
  • the shaft portion 27 c has four retard ports 32, which are the first ports, penetrating in the cross radial direction of the peripheral wall at a position near the head portion 27 b in the axial direction. Further, four advance ports 33, which are second ports, are formed so as to penetrate in the cruciform direction of the peripheral wall on the side portion closer to the tip of each retard port 32 of the shaft portion 27c.
  • each of the retard port 32 and each advance port 33 has an inner opening facing the valve hole 27 a, and an outer opening formed in each retard passage hole 17 and each advance passage hole 18. It communicates from the radial direction via the groove grooves 17a and 18a.
  • annular groove 34 is formed on the inner periphery of the tip of the shaft portion 27c.
  • the annular groove 34 is formed to have a predetermined axial length and is formed to have a diameter larger than the inner diameter of the inner peripheral surface of the valve hole 27a, and a step surface 34a along the radial direction is formed at the inner end. Has been.
  • the sleeve 28 is integrally formed of, for example, a synthetic resin material or a metal material. As shown in FIGS. 3, 4A, and B, an inner solid cylindrical sleeve body 28a and an axial direction of the sleeve body 28a are provided. And a flange portion 28b which is integrally provided at one end portion.
  • the sleeve main body 28a is divided into a first oil passage 36 and a second oil passage 37 by a partition wall 35 provided integrally therein, and the sleeve main body 28a is formed inside the flange portion 28b.
  • a valve housing recess 38 is formed. That is, the first and second oil passages 36 and 37 are formed along the axial direction by cutting out the solid interior of the sleeve main body 28a.
  • the sleeve main body 28a is formed such that the outer diameter of the portion corresponding to the valve housing recess 38 of the axial one end 28c on the flange portion 28b side is slightly larger.
  • Each guide groove 28d has a function of guiding hydraulic oil flowing between an outer peripheral surface of a ball valve body 45 described later to the inside of the sleeve main body 28a.
  • the partition wall 35 has a cross-section formed in a cross shape in a direction perpendicular to the axis, and includes four partition portions 35b, 35c, 35d, and 35e with the central shaft portion 35a as a center.
  • a first end wall 39 a that closes the axial end of the first oil passage 36 is integrally provided at the end of the partition wall 35 opposite to the valve housing recess 38 in the axial direction.
  • a second end wall 39b for closing the axial end portion of the second oil passage 37 is integrally provided at the end portion on the valve accommodating recess 38 side.
  • a protrusion 40 is provided that protrudes in the direction of the valve housing recess 38 in the form of extending the central shaft portion 35a.
  • the first oil passage 36 is formed with a rectangular first opening hole 36a formed in the vicinity of the first end wall 39a of the sleeve body 28a.
  • the first opening hole 36 a communicates with each retard port 32 or each advance port 33 as appropriate through a communication hole 29 c described later of the spool valve 29.
  • the valve housing recess 38 faces the inlet 36 b that is opposite to the first end wall 39 a of the first oil passage 36 in the axial direction.
  • first end wall 39a is formed with a first inclined surface 39c for guiding hydraulic oil from the first oil passage 36 to the first opening hole 36a on the inner surface on the first oil passage 36 side.
  • second end wall 39 b is formed with a second inclined surface 39 d that guides hydraulic oil from the first cylindrical passage 41 a to the second oil passage 37 on the inner surface on the second oil passage 37 side.
  • each retardation port 32 is formed between the outer peripheral surface of the cylindrical member 50 and the inner peripheral surface of the valve body 27 when the spool valve 29 is held at the maximum rightward movement position.
  • the oil pan 51 communicates with the two cylindrical passages 41b.
  • the flange portion 28 b is disposed inside the annular groove 34, and is provided between a spring retainer 42 on which one end portion of the valve spring 30 in the axial direction is held and a valve seat 46 described later. It is arrange
  • the spring retainer 42 is formed in an annular shape with a metal plate, and the outer peripheral portion 42a is formed in a substantially L-shaped cross section along the axial direction, and has a large diameter in the center.
  • An insertion hole 42b is formed through.
  • the outer peripheral portion 42 a has an outer peripheral surface press-fitted into the inner peripheral surface of the annular groove 34, and an annular front end wall 42 c is in contact with the step surface 34 a of the annular groove 34 from the axial direction.
  • the flange portion 28 b is formed so that the outer diameter is smaller than the inner diameter of the outer peripheral portion 42 a of the spring retainer 42.
  • a radial clearance C1 of, for example, about 0.4 mm is formed between the outer peripheral surface of the flange portion 28b and the outer peripheral portion 42a of the spring retainer 42.
  • An axial clearance C2 of about 0.02 mm is formed between the front end face of the flange portion 28b and the opposing face of the valve seat 46 that faces the front end face in the axial direction. Due to the presence of these clearances C 1 and C 2, the entire sleeve 28 is held so as to be slightly movable in the radial direction and the axial direction with respect to the valve body 27.
  • a check valve 44 is accommodated in the valve accommodating recess 38.
  • the check valve 44 includes a ball valve body 45, a valve seat 46 on which the ball valve body 45 is separated and seated, and a check spring 47 that biases the ball valve body 45 toward the valve seat 46. .
  • the ball valve body 45 is formed in a spherical shape with a metal material, and has an outer diameter that is sufficiently smaller than the inner diameter of the valve housing recess 38, and is compared between the outer surface and the inner peripheral surface of the valve housing recess 38. A large gap is formed.
  • the one end of the valve spring 30 is in elastic contact with the front end wall 42c of the spring retainer 42 as described above.
  • the other axial end portion is in elastic contact with the axial end surface of the spool valve 29 on the second land portion 29 b side to urge the spool valve 29 toward the electromagnetic actuator 31.
  • the electromagnetic actuator 31 includes a synthetic resin material casing 53, a solenoid 55 accommodated in the casing 53 via a magnetic bobbin 54, and an axial direction inside the bobbin 54.
  • a cylindrical movable iron core 56 provided slidably and a front end portion of the movable iron core 56 are integrally coupled, and a pressing portion 57a of the front end portion is formed on the bottom wall 50d of the small diameter cylindrical portion 50b of the cylindrical member 50.
  • a push rod 57 that abuts from the axial direction.
  • the casing 53 is integrally provided with a bracket 53a fixed to the cylinder head at a lower end portion, and a connector portion 53b electrically connected to a control unit 58 that is an ECU at the upper end portion.
  • the connector portion 53b is connected to the solenoid 55 at one end of a pair of terminal pieces 53c embedded almost entirely in the casing 53, while the other end exposed to the outside is on the control unit 58 side. Connected to the terminal of the male connector.
  • the casing 53 is liquid-tightly supported in the holding groove of the cylinder head by a seal ring 59 provided on the front end side.
  • the movable iron core 56 moves backward through the spool valve 29, the cylindrical member 50, and the push rod 57 by the spring force of the valve spring 30 when the solenoid 55 is not energized.
  • 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 in the figure.
  • An information signal from various sensors such as a cam angle sensor is input to detect the current engine operating state.
  • the control unit 58 cuts off the energization of the solenoid 55 of the electromagnetic actuator 31 and controls the spool valve 29 to the first movement position (position) or outputs a pulse signal to the solenoid 55.
  • the energization amount (duty ratio) is controlled so that the first and third positions are continuously variably controlled.
  • the advance working chambers 10 are maintained in a low pressure state as described above.
  • This second position is a case where the control unit 58 detects the engine operating state and is shifted from the first position or a case where the control unit 58 is shifted from the third position.
  • the hydraulic pressure fluctuation is eliminated.
  • the vane rotor 7 is held at a predetermined position between the most retarded angle and the most advanced angle.
  • the spool valve 29 is further slightly moved to the right as shown in FIG. 10 (third position).
  • the first land portion 29 a of the spool valve 29 opens the retard port 32 and is formed between the inner peripheral surface of the valve body 27 and the outer peripheral surface of the cylindrical member 50 with respect to the retard port 32.
  • the second cylindrical passage 41b is communicated.
  • the spool valve 29 causes the communication hole 29c and the advance port 33 to communicate with each other through the groove grooves 29d and 29e.
  • These controls are performed by controlling the energization amount (duty ratio) from the control unit 58 and appropriately changing the moving position of the spool valve 29 between the first to third positions, thereby allowing each retarded working chamber 9 or each OPA control which is a so-called normal control in which the relative rotation phase of the vane rotor 7 is changed by selectively supplying the discharge pressure of the oil pump 25 from the supply passage 24 to the advance angle working chamber 10 from the first oil passage 36. Is supposed to do.
  • control of the second position can be held at any intermediate position between the first position and the third position.
  • the vane rotor 7 can be held at any position between the most retarded position and the most advanced position. That is, for example, it is possible to freely control the position toward the most retarded angle position or the most advanced angle position, and further to an almost intermediate position between the most retarded angle position and the most advanced angle position.
  • the hydraulic control valve 26 of this embodiment is provided with a first oil passage 36 for supplying hydraulic oil and a second oil passage 37 for discharging hydraulic oil inside the sleeve 28, and communicates with the second oil passage 37.
  • a discharge flow path was formed in the direction of the internal axis of the valve body 27. That is, the hydraulic oil discharged from each advance angle working chamber 10 is discharged from the second oil passage 37 through the cylindrical member 50, the discharge hole 50e, the circular hole 52d, and the drain hole 52e from the internal axial direction of the valve body 27.
  • the oil pan 51 is discharged through the passage 43. Therefore, it is not necessary to form a special port such as a discharge port in the valve body 27 in addition to the retard port 32 and the advance port 33. Accordingly, the axial length of the valve body 27 can be sufficiently shortened.
  • the sleeve 28 is mainly formed with the first oil passage 36 and the second oil passage 37 along the axial direction, it is not necessary to increase the outer diameter thereof.
  • the spool valve 29 is also formed with only one communication hole 29c, so that it is not necessary to increase the rigidity, so that the wall thickness can be made as thin as possible. Therefore, the outer diameter of the entire valve body 27 can be made sufficiently small.
  • the overall valve timing control device can be further reduced in size and weight by reducing the outer diameter.
  • the check valve 44 is seated on the valve seat 46 and closes the passage hole 46a to prevent backflow of hydraulic oil from each retarded working chamber 9, so It becomes possible to hold the hydraulic oil. Therefore, the hydraulic pressure rise of each retarded working chamber 9 becomes good when the engine is restarted, and the vane rotor 7 can be quickly relatively rotated to the most retarded angle side.
  • FIGS. 11 to 13 show a second embodiment of the present invention, which mainly changes the internal oil passage structure of the sleeve 28 and the structure of the check valve 44 in the first embodiment. Also, the stopper member 52 and the like have been eliminated. In the following description, the same reference numerals as those in the first embodiment are used even if they are not shown.
  • the sleeve 28 is divided into a sleeve main body 60 that is a first member made of, for example, a synthetic resin material, and a passage constituting portion 61 that is a second member made of, for example, a synthetic resin material that is press-fitted and fixed inside the sleeve main body 60. Is formed.
  • the sleeve body 60 is formed in a bottomed cylindrical shape, and has a large-diameter portion 60a formed at one end in the axial direction.
  • the sleeve main body 60 has a flange portion 60b integrally at the outer end edge of the large-diameter portion 60a. ing.
  • a first opening hole 60c for supplying hydraulic oil is formed in a radial direction at a substantially central position in the axial direction, and a second opening hole 60d is formed in the vicinity of the large diameter part 60a at one end. It is formed penetrating in the direction.
  • an oil hole 60f for discharging hydraulic oil is formed through the bottom wall 60e of the other end of the sleeve body 60 in the axial direction.
  • a valve housing recess 64 in which the check valve 44 is housed is formed in the large diameter portion 60a.
  • the passage constituting portion 61 forms a passage between the sleeve main body 60 and the inner peripheral surface of the sleeve main body 60 while being accommodated and fixed inside the sleeve main body 60. Further, the axial length of the passage constituting portion 61 is formed from the inner bottom surface of the bottom wall 60e to the vicinity of the large diameter portion 60a. As shown in FIG. 12, the passage constituting portion 61 has a partition wall 61a having a substantially cross-shaped cross section in the direction perpendicular to the axis. The partition wall 61 a extends in the axial direction and partitions the two first oil passages 62 and the second oil passages 63 between the inner peripheral surface of the sleeve body 60.
  • the partition wall 61a is integrally provided with a first end wall 61b that abuts the bottom wall 60e of the sleeve body 60 from the axial direction at one end in the axial direction of each first oil passage 62 on the electromagnetic actuator 31 side.
  • a small protrusion 61c is provided on the outer surface of the first end wall 61b. The small protrusion 61c engages with the small hole 60g formed in the bottom wall 60e of the sleeve body 60 from the axial direction. The small protrusion 61c is engaged with the small hole 60g from the axial direction, thereby positioning the passage constituting portion 61 in the circumferential direction with respect to the sleeve main body 60.
  • the partition wall 61 a is integrally provided with a second end wall 61 d that closes the second oil passage 63 at one end in the axial direction of the second oil passage 63 on the large diameter portion 60 a side.
  • a through hole 61e communicating with the first opening hole 60c is formed through the peripheral wall constituting the outer peripheral portion of the first oil passage 62 in the radial direction.
  • first oil passages 62 and the second oil passages 63 are provided at symmetrical positions in the radial direction across the partition wall 61a. That is, the first oil passage 62 and the second oil passage 63 are formed in parallel along the axial direction of the sleeve body 60 as in the first embodiment, and are symmetric in the radial direction with respect to each other via the cross-shaped partition wall 35. Two positions are formed at positions, that is, symmetrical positions of 180 °.
  • the oil passages 62 and 63 are each formed in a sectional fan shape by a partition wall 61a.
  • the check valve 44 uses a cup-shaped valve body 65 having a U-shaped vertical cross section instead of a ball valve body, and a valve seat 66 is formed in a relatively thick disk shape.
  • the cup-shaped valve body 65 has a plurality of passage portions 65a cut along the axial direction on the outer periphery, and the outer surface of the central portion 65b is formed flat.
  • the cup-shaped valve body 65 is urged toward the valve seat 66 by a valve spring 67.
  • the large diameter cylindrical portion 70a is slidably disposed on the outer peripheral surface of the sleeve body 60.
  • the small diameter cylindrical portion 70b is provided in the guide hole 27h of the valve body 27 so as to be slidable in the axial direction.
  • a disk-shaped closing plate 71 is fixed by caulking at the opening end of the tip portion.
  • a pressing portion 57a of the push rod 57 of the electromagnetic actuator 31 is in contact with the front end surface of the closing plate 71 from the axial direction.
  • the electromagnetic actuator 31 has the same configuration as that of the first embodiment, and the movable iron core 56 and the push rod 57 are resisted against the spring force of the valve spring 69 according to the deenergization or the energization amount from the control unit 58 to the solenoid 55. Then, the spool valve 68 is pushed rightward (forward) in FIG. 13 to move the moving position of the spool valve 68 to the first position and the third position shown in FIGS.
  • the movement position of the spool valve 68 can be controlled to the position of the second position, which is an intermediate position between the first position and the third position, as in the first embodiment. It has become. [Effects of Second Embodiment] Since the hydraulic control valve 26 of the second embodiment is almost the same as that of the first embodiment, it will be briefly described.
  • the spool valve 68 is held at the first position in the maximum left direction by the spring force of the valve spring 69.
  • the outer surface of the central portion 65b of the cup-shaped valve body 65 is seated on the valve seat 66 by the spring force of the valve spring 67 to close the passage hole 66a.
  • the oil pump 25 is also driven. As shown by the arrow in FIG.
  • the passage hole 66a is opened by pushing back against the spring force.
  • the cup-shaped valve body 65 moves backward to the maximum until it abuts against the stepped portion between the sleeve main body 60 and the large-diameter portion 60a by the hydraulic pressure to ensure a sufficient flow rate of the supplied hydraulic oil.
  • the spool valve 68 connects each advance port 33 and the first cylindrical passage 41a.
  • the hydraulic oil in each advance angle working chamber 10 flows into the second oil passage 63 from the second opening hole 60d through each advance port 33 and the first cylindrical passage 41a.
  • the oil hole 60f is discharged into the oil pan 51 through each drain hole 70e and the discharge passage 43 through the discharge hole 70d.
  • the vane rotor 7 is maintained in the state of relative rotation to the most retarded position, and the valve timing of the intake valve is controlled to the retarded side. As a result, the startability of the engine is improved.
  • each retarded working chamber 9 flows into the second cylindrical passage 41b from each retarded passage hole 17 through the retarded port 32 as shown by arrows in the figure. From here, it flows into the small diameter cylindrical portion 70b through the discharge hole 70d, and is quickly discharged into the oil pan 51 through the drain hole 70e and the discharge passage 43.
  • the hydraulic oil pumped from the oil pump 25 flows into the first oil passages 36 via the check valves 44 as indicated by arrows. From here, it passes through the first opening hole 60c including the through hole 61e, passes through the groove grooves 68d and 68e, passes through the communication holes 68c and the advance port 33, and flows into the advance passage holes 18 to advance each advance. It is supplied to the corner working chamber 10.
  • the vane rotor 7 rotates relative to the maximum advance angle side, the valve timing of the intake valve reaches the maximum advance angle phase, the valve overlap with the exhaust valve increases, the intake charge efficiency increases, and the engine output increases. Torque can be improved.
  • the spool valve 68 can be held at a desired intermediate position (second position) between the maximum left position and the maximum right position by changing the energization amount from the control unit 58 to the solenoid 55. For example, it is possible to stabilize engine rotation and improve fuel efficiency during steady operation.
  • the present invention is not limited to the configuration of the above embodiment, and can be applied not only to the intake valve side but also to the exhaust valve side.
  • the hydraulic control valve can also be applied to devices other than the valve timing control device.
  • the actuator may be a hydraulic actuator in addition to the electromagnetic actuator.
  • the retarded and advanced ports 32 and 33 are closed and communicated with each other by means of the land portions 38a, 38b, 68a and 68b of the spool valves 29 and 68.
  • the state where the ports 32 and 33 are blocked is included, and includes a state where the ports 32 and 33 are slightly communicated with each other through a clearance between the land portions and the valve hole 27a.
  • a cylindrical valve body in which a plurality of ports are formed penetrating in a radial direction, a sleeve that is housed and held in the valve body and has two oil passages therein, and the valve body Between the inner periphery of the sleeve and the outer periphery of the sleeve so as to be movable in the axial direction of the valve body, and communicates with either of the two oil passages or the plurality of ports according to the axial movement position. Or a spool valve that cuts off the communication.
  • the two systems of oil passages are formed in the inner axial direction of the sleeve in a state of being partitioned from the first oil passage formed along the inner axial direction of the sleeve.
  • the second oil passage is formed.
  • one end side in the axial direction is opened in the axial direction, and the other opening side is formed with a first opening hole that is bent outward in the radial direction of the sleeve.
  • the second oil passage has a second opening hole that is bent outward in the radial direction of the sleeve on one end side in the axial direction, and the other end side is opened in the axial direction.
  • the opening on one end side of the first oil passage is an introduction port for introducing hydraulic oil
  • the opening on the other end side of the second oil passage is a discharge port for discharging hydraulic oil
  • the first oil passage is formed with a first inclined surface that guides hydraulic oil in a direction toward the first opening hole at a radially bent portion of the first opening hole from the other end side.
  • the second oil passage is formed with a second inclined surface for guiding the hydraulic oil in the direction of the second opening hole at a radial bending portion of the second opening hole from one end side.
  • the plurality of ports of the valve body include a first port and a second port, and the first port and the first opening hole in the first movement position among the movement positions of the spool valve in the axial direction.
  • the second port and the first opening hole are communicated via the communication hole in the second movement position, and the two land portions of the spool valve are provided in the third movement position.
  • the first port and the second port are closed.
  • the second port is provided through an annular gap passage formed between the inner peripheral surface of the valve body and the outer peripheral surface of the sleeve. To the second oil passage.
  • each of the first oil passage and the second oil passage is formed at two symmetric positions in the radial direction via a partition wall provided in the sleeve along the axial direction.
  • the partition wall is formed in a cross-shaped cross section in the direction perpendicular to the axis of the sleeve, and each of the two first oil passages and the second oil passage is formed in a fan shape.
  • the sleeve is formed in a solid cylindrical portion, and the first and second oil passages are formed in the inner axial direction of the cylindrical portion.
  • a valve housing recess is formed inside one end side of the sleeve in the axial direction, and the valve housing recess allows only the inflow of hydraulic oil from the introduction port to the first oil passage side.
  • a stop valve is provided.
  • the sleeve has a flange portion at one end in the axial direction
  • the valve body has an annular groove having a large step in the inner periphery of one end portion in the axial direction.
  • An outer peripheral portion of the valve seat on which the valve body of the check valve is seated is held, and the flange portion is disposed between the valve seat and the step surface of the annular groove.
  • a clearance is formed between the outer peripheral edge of the flange portion of the sleeve and the inner peripheral surface of the annular groove so that the sleeve can move in the radial direction.
  • the flange portion of the sleeve is formed with a clearance between both side surfaces and step surfaces of the valve seat and the annular groove so that the sleeve can move in the axial direction.
  • a bottomed cylindrical retainer is held in the annular groove, and the retainer has a cylindrical portion fixed to the inner peripheral surface of the annular groove, and an annular shape that contacts the stepped surface of the annular groove.
  • a bottom portion, and the tubular portion is restricted from moving in the axial direction by the valve seat coming into contact with an end edge opposite to the bottom portion from the axial direction.
  • a filtration filter is provided on the valve seat.
  • a spring member for biasing the spool valve toward the other end in the axial direction of the sleeve is disposed between the bottom of the retainer and the spool valve.
  • a spring member that biases the spool valve in the direction of the first movement position and an actuator that presses the spool valve in the direction of the second movement position against the spring force of the spring member. is doing.
  • the cylindrical member arranged between the spool valve and the actuator, and a discharge hole for communicating the discharge port of the second oil passage of the sleeve with the outside is provided on the peripheral wall of the cylindrical member. Is formed.
  • the cylindrical member is formed to have a large or small outer diameter through a stepped portion, and is provided on the outer periphery of the sleeve so as to be slidable.
  • the discharge hole is formed in the peripheral wall of the large-diameter cylindrical portion.
  • a stopper member for restricting the movement position of the spool valve in the maximum axial direction through the step portion of the cylindrical member is fixed to the inner periphery of the axial end of the valve body.
  • the stopper member has an insertion hole through which the tip of the cylindrical member can be inserted at the center, and at least one drain hole is formed at the hole edge of the insertion hole.
  • a valve body a sleeve that is housed and held in the valve body and has two systems of oil passages, and an inner periphery of the valve body and an outer periphery of the sleeve
  • a spool valve that is arranged so as to be movable in the axial direction of the valve body, and that connects or disconnects the two oil passages and the first port or the second port according to the axial movement position; have.
  • the two systems of oil passages are formed in the inner axial direction of the sleeve in a state of being partitioned from the first oil passage formed along the inner axial direction of the sleeve.
  • the second oil passage is formed.
  • one end side in the axial direction is opened in the axial direction, and a first opening hole that is bent outward in the radial direction of the sleeve is formed in the other end side.
  • the second oil passage has a second opening hole that is bent radially outward of the sleeve on one end side in the axial direction, and the other end side is opened in the axial direction.
  • the opening on one end side of the first oil passage is an introduction port for introducing hydraulic oil
  • the opening on the other end side of the second oil passage is a discharge port for discharging hydraulic oil
  • the first working chamber is a retarded working chamber that changes the relative rotational phase of the vane rotor with respect to the housing to the retarded side by applying hydraulic pressure
  • the second working chamber is operated by hydraulic pressure.
  • the advance working chamber changes the relative rotation phase of the vane rotor with respect to the housing to the advance side.
  • valve body is configured by a cam bolt that fixes the vane rotor to the camshaft.
  • a holding member for holding the sleeve so as to be movable in a direction perpendicular to the axis of the valve body is provided on the periphery.
  • the second working chamber changes the relative rotational phase of the vane rotor relative to the housing to the advanced side by the action of hydraulic pressure. It is an advance working chamber.
  • valve body is configured by a cam bolt that fixes the vane rotor to the camshaft, and a male screw that is screwed to a female screw formed in the camshaft is formed on an outer periphery of the valve body.
  • a holding member for holding the sleeve so as to be movable in a direction perpendicular to the axis of the valve body is provided on the periphery.
  • valve housing recess and the first oil passage are always in communication.
  • valve seat is formed in a disc plate shape having a passage hole formed in the center thereof, and an outer peripheral portion is press-fitted into an inner peripheral surface of the annular groove. Abutting on the part from the axial direction.
  • the filtration filter is fixed in a state of being sandwiched between the valve seat and a fixing portion.
  • valve seat is formed in a thick disk shape with a passage hole formed in the center, and the outer peripheral surface is press-fitted and fixed to the inner peripheral surface of the annular groove.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Valve Device For Special Equipments (AREA)
  • Multiple-Way Valves (AREA)

Abstract

L'invention concerne une soupape à commande hydraulique (26) comprenant des orifices de retard (32), qui communiquent avec un orifice de passage de retard (17), et des orifices d'avance (33), qui communiquent avec un orifice de passage d'avance (18), formés de manière adjacente dans une section d'une partie tige (27c) qui est proche d'une partie tête (27b) d'un corps de soupape(27). Des premier et second passages d'huile (36, 37) sont formés, le long de la direction axiale, dans une direction axiale interne d'un manchon (28), et des orifices de décharge (50e) qui communiquent avec le second passage d'huile sont formés dans un élément formant cylindre (50). Des orifices de vidange (52e) qui font communiquer les orifices de décharge et un carter d'huile sont formés dans un élément d'arrêt. L'huile de service déchargée depuis une chambre de travail de retard et une chambre de travail d'avance est déchargée depuis le second passage d'huile, les orifices de décharge et les orifices de vidange, par l'intermédiaire de premier et second passages cylindriques (41a, 41b). L'invention permet ainsi une réduction globale de la taille et du poids.
PCT/JP2017/037777 2016-11-30 2017-10-19 Soupape à commande hydraulique et dispositif de commande du réglage de distribution d'un moteur à combustion interne WO2018100909A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2018553705A JP6775032B2 (ja) 2016-11-30 2017-10-19 油圧制御弁及び内燃機関のバルブタイミング制御装置
CN201780072543.6A CN109983266B (zh) 2016-11-30 2017-10-19 液压控制阀及内燃机的阀正时控制装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-232314 2016-11-30
JP2016232314 2016-11-30

Publications (1)

Publication Number Publication Date
WO2018100909A1 true WO2018100909A1 (fr) 2018-06-07

Family

ID=62241518

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/037777 WO2018100909A1 (fr) 2016-11-30 2017-10-19 Soupape à commande hydraulique et dispositif de commande du réglage de distribution d'un moteur à combustion interne

Country Status (3)

Country Link
JP (1) JP6775032B2 (fr)
CN (1) CN109983266B (fr)
WO (1) WO2018100909A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021085401A (ja) * 2019-11-29 2021-06-03 株式会社デンソー バルブタイミング調整装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5759654B2 (fr) * 1978-09-14 1982-12-15 Ckd Corp
JP2012107677A (ja) * 2010-11-16 2012-06-07 Denso Corp 可変バルブタイミング装置
WO2016021328A1 (fr) * 2014-08-04 2016-02-11 日立オートモティブシステムズ株式会社 Valve oléo-hydraulique, et dispositif de commande de réglage de distribution pour moteur à combustion interne mettant en œuvre une valve oléo-hydraulique

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8322361B2 (en) * 2008-12-30 2012-12-04 General Electric Company Methods, apparatus and/or systems relating to controlling flow through concentric passages
DE102010019005B4 (de) * 2010-05-03 2017-03-23 Hilite Germany Gmbh Schwenkmotorversteller
US10145273B2 (en) * 2014-03-19 2018-12-04 Hitachi Automotove Systems, Ltd. Control valve for valve timing control device and valve timing control device for internal combustion engine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5759654B2 (fr) * 1978-09-14 1982-12-15 Ckd Corp
JP2012107677A (ja) * 2010-11-16 2012-06-07 Denso Corp 可変バルブタイミング装置
WO2016021328A1 (fr) * 2014-08-04 2016-02-11 日立オートモティブシステムズ株式会社 Valve oléo-hydraulique, et dispositif de commande de réglage de distribution pour moteur à combustion interne mettant en œuvre une valve oléo-hydraulique

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021085401A (ja) * 2019-11-29 2021-06-03 株式会社デンソー バルブタイミング調整装置
WO2021106892A1 (fr) * 2019-11-29 2021-06-03 株式会社デンソー Dispositif de réglage de calage de distribution
JP7200914B2 (ja) 2019-11-29 2023-01-10 株式会社デンソー バルブタイミング調整装置
US11965438B2 (en) 2019-11-29 2024-04-23 Denso Corporation Valve timing adjustment device

Also Published As

Publication number Publication date
CN109983266B (zh) 2020-11-27
CN109983266A (zh) 2019-07-05
JPWO2018100909A1 (ja) 2019-10-17
JP6775032B2 (ja) 2020-10-28

Similar Documents

Publication Publication Date Title
JP5270525B2 (ja) 制御弁装置
JP7157826B2 (ja) 内燃機関のバルブタイミング制御装置に用いられる制御弁及び内燃機関のバルブタイミング制御システム
US6263843B1 (en) Valve timing control device of internal combustion engine
US8955479B2 (en) Variable valve timing control apparatus of internal combustion engine and method for assembling the same
JP6084562B2 (ja) 油圧制御バルブ及び内燃機関のバルブタイミング制御装置に用いられる油圧制御バルブ
WO2016174957A1 (fr) Vanne de régulation de pression d'huile et dispositif de commande de temporisation de vanne pour moteur à combustion interne mettant en œuvre une vanne de régulation de pression d'huile
JP2018112080A (ja) 内燃機関のバルブタイミング制御装置の油圧制御弁と内燃機関のバルブタイミング制御装置
JP2019007515A (ja) 油圧制御弁
CN114761674A (zh) 阀正时调整装置
WO2018100909A1 (fr) Soupape à commande hydraulique et dispositif de commande du réglage de distribution d'un moteur à combustion interne
JP6295160B2 (ja) 電磁弁と、内燃機関のバルブタイミング制御装置に用いられる電磁弁並びに電磁アクチュエータ
JP2018059415A (ja) 油圧制御弁及び内燃機関のバルブタイミング制御装置
JP2017089777A (ja) 電磁弁
JP7064922B2 (ja) 内燃機関のバルブタイミング制御装置及び内燃機関のバルブタイミング制御装置に用いられる制御弁
JP6704823B2 (ja) 内燃機関のバルブタイミング制御装置の油圧制御弁及び内燃機関のバルブタイミング制御装置
JP2020186662A (ja) 内燃機関のバルブタイミング制御装置
JP2019007516A (ja) 油圧制御弁とバルブタイミング制御装置。
JP3817067B2 (ja) 内燃機関のバルブタイミング制御装置
WO2023210130A1 (fr) Soupape de commande et dispositif de commande de calage de distribution pour moteur à combustion interne utilisant ladite soupape de commande
JP7068495B2 (ja) 電磁弁と内燃機関のバルブタイミング制御装置
WO2023042527A1 (fr) Dispositif de commande de calage de distribution pour moteur à combustion interne
WO2022190568A1 (fr) Soupape de réglage de pression d'huile et dispositif de commande de réglage de distribution pour moteur à combustion interne
WO2020026659A1 (fr) Dispositif de commande de réglage de distribution pour moteur à combustion interne
WO2023037738A1 (fr) Dispositif de commande de calage de distribution pour moteur à combustion interne
JP2019074046A (ja) 内燃機関のバルブタイミング制御装置と、内燃機関のバルブタイミング制御装置に用いられる油圧制御弁。

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17875525

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2018553705

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17875525

Country of ref document: EP

Kind code of ref document: A1