WO2022190568A1 - Soupape de réglage de pression d'huile et dispositif de commande de réglage de distribution pour moteur à combustion interne - Google Patents

Soupape de réglage de pression d'huile et dispositif de commande de réglage de distribution pour moteur à combustion interne Download PDF

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Publication number
WO2022190568A1
WO2022190568A1 PCT/JP2021/047460 JP2021047460W WO2022190568A1 WO 2022190568 A1 WO2022190568 A1 WO 2022190568A1 JP 2021047460 W JP2021047460 W JP 2021047460W WO 2022190568 A1 WO2022190568 A1 WO 2022190568A1
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Prior art keywords
valve
spool
hole
spool valve
tongue
Prior art date
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PCT/JP2021/047460
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English (en)
Japanese (ja)
Inventor
海大 中野
Original Assignee
日立Astemo株式会社
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Filing date
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Publication of WO2022190568A1 publication Critical patent/WO2022190568A1/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
    • F16K15/00—Check valves
    • F16K15/14—Check valves with flexible valve members

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, there is one described in Patent Document 1 below.
  • the hydraulic control valve described in Patent Document 1 has a valve body having an advance port and a retard port, and a spool valve slidably arranged on the inner circumference of the valve body.
  • a plate-shaped check valve is arranged on the inner circumference of the spool valve so that both ends in the circumferential direction are overlapped with each other.
  • the spool valve is formed with a spool hole penetrating therethrough at a position facing the check valve in the radial direction, through which hydraulic oil can be introduced from the retard port.
  • the check valve includes a frame portion formed by rolling a plate-like member, and a plurality of tongue pieces integrally formed with the frame portion and arranged at regular intervals in the circumferential direction.
  • the tongue deforms radially inward to allow hydraulic fluid to flow from the plurality of spool holes into the spool valve.
  • FIG. 1 is a sectional view of a valve timing control device according to a first embodiment applied to an intake side of an internal combustion engine;
  • FIG. 1 is a front view showing the valve timing control device of the first embodiment with a front plate removed;
  • FIG. 4 is an exploded perspective view of the control valve;
  • FIG. 1 is a longitudinal sectional view of a control valve of a first embodiment;
  • FIG. Figure 5 is a cross-sectional view of the control valve taken along line AA of Figure 4;
  • FIG. 4 is a plan view showing a flat plate-shaped second check valve in an unfolded state;
  • FIG. 4 is a longitudinal sectional view showing a first movement position of the spool valve in the control valve of the first embodiment;
  • FIG. 4 is a longitudinal sectional view showing a second movement position of the spool valve in the control valve of the first embodiment
  • FIG. 5 is a longitudinal sectional view showing a third movement position of the spool valve in the control valve of the first embodiment
  • FIG. 10 is a longitudinal sectional view showing a fourth movement position of the spool valve in the control valve of the first embodiment
  • It is a sectional view of a control valve of a 2nd embodiment.
  • It is a sectional view of a control valve of a 3rd embodiment.
  • It is a cross-sectional view of a control valve of a fourth embodiment.
  • FIG. 11 is a plan view showing the second check valve of the fifth embodiment in an unfolded state
  • FIG. 11 is a plan view showing the second check valve of the sixth embodiment in an unfolded state
  • FIG. 20 is a plan view showing the second check valve of the seventh embodiment in an unfolded state;
  • FIG. 1 is a cross-sectional view of a first embodiment of a valve timing control device applied to an intake side of an internal combustion engine
  • FIG. 2 is a front view of the valve timing control device of the first embodiment with a front plate 11 removed.
  • 3 is an exploded perspective view of the control valve 26, and
  • FIG. 4 is a longitudinal sectional view of the control valve 26 of the first embodiment.
  • FIG. 5 is a cross-sectional view of control valve 26 taken along line AA of FIG.
  • FIG. 4 shows a state in which the second check valve 56 provided in the control valve 26 is in operation.
  • FIG. 6 is a plan view showing the flat plate-like second check valve 56 in an unfolded state.
  • the valve timing control device comprises a timing sprocket 1, which is a drive rotor that is rotationally driven by an engine crankshaft through a timing chain (not shown), and a timing sprocket 1.
  • a camshaft 2 on the intake side provided to be relatively rotatable, a phase changing mechanism 3 for changing the relative rotational phase between the timing sprocket 1 and the camshaft 2, and locking the phase changing mechanism 3 at the most retarded phase position.
  • a lock mechanism 4 and a hydraulic circuit 5 for operating the phase change mechanism 3 and the lock mechanism 4 are provided.
  • a timing pulley to which a rotational force is transmitted by a timing belt may be used as the drive rotor.
  • the timing sprocket 1 is formed in a disc shape, and has a gear portion 1a around which a timing chain is wound. Also, the timing sprocket 1 is provided integrally with a housing body 6a, which will be described later. The timing sprocket 1 constitutes a part of the drive rotor.
  • the camshaft 2 is rotatably supported on a cylinder head (not shown) via a plurality of cam bearings, and has a plurality of egg-shaped rotating cams on its outer peripheral surface for opening intake valves, which are engine valves (not shown). integrally fixed in axial position.
  • a female screw hole 2b into which a valve body (cam bolt) 13 (to be described later) is screwed is formed in the inner axial direction of one end portion 2a of the camshaft 2 in the rotation axis direction.
  • the phase changing mechanism 3 is composed of a housing 6 integrally provided with the timing sprocket 1 in the axial direction, and a driven rotating body housed in the housing 6 so as to be relatively rotatable.
  • a vane rotor 7 is provided.
  • the vane rotor 7 and the four shoes 8a to 8d integrally formed on the inner peripheral surface of the housing body 6a (to be described later) of the housing 6 create a plurality of spaces (four spaces in this embodiment) between the housing body 6a and the vane rotor 7. ) and a plurality (four in this embodiment) of advance hydraulic chambers 10, which are advance operation chambers.
  • the housing 6 is composed of a cylindrical housing body 6a, a front plate 11 closing the front end opening of the housing body 6a, and a rear plate 12 closing the rear end opening.
  • the housing main body 6a is formed in a substantially cylindrical shape from a so-called sintered metal material formed by sintering powdered metal.
  • Four shoes 8a-8d protrude from the inner peripheral surface of the housing body 6a, and four bolt insertion holes 6b are formed through each of the shoes 8a-8d in the axial direction.
  • the front plate 11 is press-formed to have a thickness smaller than that of the rear plate 12, and a large-diameter insertion hole 11a is formed through the center.
  • the front plate 11 seals the retard hydraulic chambers 9 and the advance hydraulic chambers 10 between the inner peripheral surface excluding the insertion hole 11a and the opposite side surface of the vane rotor 7.
  • Four bolt insertion holes 11b into which fixing members such as bolts B are inserted are formed through the front plate 11 at four locations in the circumferential direction.
  • the rear plate 12 is made of ferrous metal having the same diameter as that of the front plate 11 and is shaped like a disc, and is slightly thicker than the front plate 11 .
  • the rear plate 12 has an insertion hole 12a formed through the center thereof, into which one end portion 2a of the camshaft 2 is slidably inserted in the axial direction.
  • the rear plate 12 seals the retard hydraulic chambers 9 and the advance hydraulic chambers 10 with a side clearance between the inner peripheral surface excluding the insertion hole 12a and the opposite side surface of the vane rotor 7. It's becoming Further, the rear plate 12 is formed with four female threaded holes 12b at approximately equal intervals in the circumferential direction of the outer peripheral portion thereof, into which the bolts B are screwed.
  • the rear plate 12 has a lock hole 21, which will be described later, at a predetermined position on the inner surface of the housing body 6a.
  • the rear plate 12, the housing body 6a, and the front plate 11 are axially connected by four bolts B that are inserted into the bolt insertion holes 11b and screwed into the female screw holes 12b of the timing sprocket 1.
  • the vane rotor 7 is also integrally formed of a sintered metal material, and has a rotor portion 7a fixed to one end portion 2a of the camshaft 2 by a valve body 13 and an outer peripheral surface of the rotor portion 7a which is rotated at approximately 90° in the circumferential direction. It is composed of four vanes 14a to 14d radially projecting at spaced positions.
  • the rotor portion 7a is formed in a relatively large-diameter cylindrical shape, and has a bolt insertion hole 15 penetrating therethrough which is continuous with the internal threaded hole 2b of the camshaft 2 in the central axial direction.
  • the tip of one end 2a of the camshaft 2 is fitted in the circular fitting groove 16 formed in the rear end face of the rotor 7a from the rotation axis direction.
  • the vanes 14a-14d are arranged between the shoes 8a-8d with a relatively short radial projection length.
  • the three vanes 14b to 14d other than the one vane 14a have substantially the same width in the circumferential direction and are formed in a relatively thin plate shape.
  • the one vane 14a is formed to have a large width in the circumferential direction, and a part of the lock mechanism 4 is provided inside.
  • a seal member 17 for sealing between the inner peripheral surface of the housing body 6a and the outer peripheral surface of the rotor portion 7a is provided at the tip of the outer peripheral surface of each of the vanes 14a to 14d.
  • the other vanes 14b to 14d are not in contact with the opposing surfaces of the shoes 8c, 8d, and 8a facing each other in the circumferential direction, and are in a separated state. Therefore, the accuracy of contact between the vane rotor 7 and the shoe 8a is improved, and the speed of supplying hydraulic pressure to each retarding hydraulic chamber 9 and each advancing hydraulic chamber 10 is increased, so that the forward and reverse rotation responsiveness of the vane rotor 7 is improved. become.
  • each retard hydraulic chamber 9 and each advance hydraulic chamber 10 communicates with four retard passage holes 18 and four advance passage holes 19 formed along the inner radial direction from the inner peripheral surface of the rotor portion 7a. there is Each retard passage hole 18 and each advance passage hole 19 communicate with the hydraulic circuit 5 via a control valve 26 which will be described later.
  • 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 locks the vane rotor 7 by inserting a lock pin 20 which is provided to move back and forth with respect to the rear plate 12 and a tip portion 20a of the lock pin 20. It is composed of a lock hole 21 and an insertion/removal mechanism for inserting or releasing the insertion of the tip portion 20a of the lock pin 20 into the lock hole 21 depending on the starting state of the engine.
  • the lock pin 20 is slidably accommodated in a sliding hole 22 formed axially through the vane 14a.
  • the entire lock pin 20, including the tip portion 20a, is formed in a substantially cylindrical shape so that it can be easily inserted into the lock hole 21 from the axial direction.
  • the lock pin 20 is elastically mounted between the bottom surface of the concave groove formed in the inner axial direction from the rear end side and the inner end surface of the front plate 11, and biases the lock pin 20 in the advance direction (insertion direction).
  • a coil spring 23 is provided.
  • the lock hole 21 is formed at a predetermined position substantially in the radial direction of the rear plate 12 .
  • the lock hole 21 is formed in a circular shape having a diameter sufficiently larger than the outer diameter of the tip portion 20a of the lock pin 20 via an annular sleeve 21b, and is provided on the inner surface of the rear plate 12 to provide the most retarded angle of the vane rotor 7. It is formed at a position corresponding to the rotational position of the side.
  • the insertion/removal mechanism consists of a coil spring 23 that biases the lock pin 20 in the advance direction, and a release hydraulic circuit (not shown) that supplies hydraulic pressure to the pressure receiving chamber 21a in the lock hole 21 to retract the lock pin 20. It is configured. In this release hydraulic circuit, the hydraulic pressure selectively supplied to the retard hydraulic chamber 9 and the advance hydraulic chamber 10 is supplied to the pressure receiving chamber 21a through a predetermined oil hole and acts on the lock pin 20 in the backward direction. It is designed to
  • the hydraulic circuit 5 includes a supply portion 24, an oil pump 25 for discharging working oil pressure to the supply portion 24 from a discharge passage 25a, and respective retarding valves for the supply portion 24 according to the engine operating state.
  • a control valve (hydraulic control valve) 26 for switching the flow path between the passage hole 18 and each advance passage hole 19, and a discharge for discharging hydraulic oil from the hydraulic chambers 9 and 10 to an oil pan 27 via the control valve 26.
  • the supply portion 24 is formed in the bearing portion of the camshaft 2 or in the inner axial direction of the camshaft 2 .
  • a downstream end of the supply portion 24 communicates with a discharge passage 25 a of the oil pump 25 .
  • the upstream end portion of the supply portion 24 communicates with the bottom portion 2c of the female screw hole 2b of the camshaft 2, and faces a supply passage 29 provided in the valve body 13 to be described later via the bottom portion 2c. I'm in.
  • the oil pump 25 is of vane type or trochoid type, for example.
  • the control valve 26 is provided in the inner axial direction of the rotor portion 7a.
  • the control valve 26, as shown in FIGS. A cylindrical spool valve 31 disposed, a compression coil spring 32 that biases the spool valve 31 leftward in FIGS. and an electromagnetic actuator 33 that can be pressed.
  • the direction along the longitudinal direction of the cylindrical valve body 13 is defined as the "axial direction”, and the direction orthogonal to the axial direction is defined as the "radial direction”.
  • a direction around a direction is defined as a "circumferential direction”.
  • the side on which the second stopper member 55 described later is arranged is defined as “one axial side”
  • the side on which the first stopper member 48 described later is arranged is defined as the "axial side”. the other side of the direction”.
  • the valve body 13 is made of a ferrous metal material and functions as a cam bolt that fixes the vane rotor 7 to the one end 2a of the camshaft 2 from the axial direction.
  • the valve body 13 is formed in a hollow cylindrical shape with a valve hole 13a penetrating therethrough in the axial direction.
  • the valve body 13 includes a head portion 13b having a hexagonal outer peripheral surface, a shaft portion 13c to be inserted into the bolt insertion hole 15 of the rotor portion 7a of the vane rotor 7, and a distal end portion of the shaft portion 13c. , and a male threaded portion 13d screwed into the female threaded hole 2b of the camshaft 2. As shown in FIG.
  • the flange portion 13e on the root side of the head portion 13b is arranged in the insertion hole 11a of the front plate 11, and the seating surface 13f of the flange portion 13e is formed. is seated on the peripheral surface of the rotor portion 7a on the opening edge side of the bolt insertion hole 15 (see FIG. 1).
  • the shaft portion 13c is located near the head portion 13b in the axial direction. formed.
  • four advance ports 35 which are second ports, are penetrating the peripheral wall at equal intervals of 90° in the circumferential direction at positions closer to the male threaded portion 13d than the respective retard ports 34 of the shaft portion 13c.
  • Each retard port 34 and each advance port 35 are formed to have the same inner diameter.
  • Each retard port 34 and each advance port 35 has an inner opening facing the valve hole 13a, and an outer opening facing each retard passage hole 18 (see FIG. 2) and each advance passage hole 19 (see FIG. 2). is communicated with from the radial direction.
  • the sleeve 30 is formed of, for example, a synthetic resin material or a metal material in a cylindrical shape, and is composed of a sleeve body 36 and a flange portion 37 formed at the other axial end of the sleeve body 36 . ing.
  • the sleeve main body 36 has a small-diameter tubular portion 36a located at one end in the axial direction, and an inclined tubular wall portion 36b formed integrally with the small-diameter tubular portion 36a and having a diameter that increases from the small-diameter tubular portion 36a toward the other axial end. and a large-diameter tubular portion 36c formed integrally with the inclined tubular wall portion 36b and having a larger diameter than the small-diameter tubular portion 36a.
  • a first sleeve oil passage 38 and a second sleeve oil passage 39 are partitioned along the axial direction by a partition wall 36d integrally formed inside the small-diameter cylindrical portion 36a.
  • a valve housing recess 40 is formed inside the small-diameter cylindrical portion 36a.
  • the partition wall 36d has a cross-shaped cross section along the radial direction.
  • the opening on the other axial side of the first sleeve oil passage 38 communicates with the valve housing recess 40 .
  • a first end wall 36e that closes the axial end of the first sleeve oil passage 38 on the side opposite to the valve accommodating recess 40 is integral with the partition wall 36d at a position that radially overlaps the retarded angle port 34. is formed in
  • a second end wall 36f for closing the axial end of the second sleeve oil passage 39 on the flange portion 37 side is formed integrally with the axial end of the partition wall 36d on the valve housing recess 40 side. .
  • An opening on one side in the axial direction of the second sleeve oil passage 39 communicates with a drain passage 54 formed inside the cylindrical member 52, which will be described later.
  • the first sleeve oil passage 38 and the second sleeve oil passage 39 are formed parallel to each other along the axial direction of the valve body 13, and are positioned radially symmetrical to each other through the cross-shaped partition wall 36d, i.e., 180°. are formed in two symmetrical positions.
  • the first sleeve oil passage 38 and the second sleeve oil passage 39 are each formed in a fan-like radial cross-section by the partition wall 36d, thereby ensuring a large passage cross-sectional area.
  • the sleeve main body 36 is formed with an introduction port 38 a facing the valve housing recess 40 at the axial end on the first sleeve oil passage 38 side.
  • a rectangular first opening 36g opening to the first sleeve oil passage 38 is formed radially through the sleeve body 36 at a position near the first end wall 36e.
  • the first opening 36g communicates appropriately with each retard port 34 or each advance port 35 through one end side spool hole 50 and other end side spool hole 51 of the spool valve 31, which will be described later.
  • a rectangular second opening 36h facing the second sleeve oil passage 39 is formed radially through the sleeve main body 36 at a position near the second end wall 36f.
  • the second opening hole 36 h communicates the advance port 35 and the second sleeve oil passage 39 according to the movement position of the spool valve 31 .
  • a discharge port 36i is formed at one end in the axial direction of the second sleeve oil passage 39, and the discharge port 36i communicates with the oil pan 27 via a drain passage 66 and a discharge passage 28 of the cylindrical member 52, which will be described later. ing.
  • first end wall 36 e has a first inclined surface that guides hydraulic oil from the retard port 34 or the advance port 35 to the first sleeve oil passage 38 via the spool valve 31 .
  • second end wall 36 f has a second inclined surface that guides hydraulic oil from the advance port 35 through the spool valve 31 toward the second sleeve oil passage 39 .
  • the flange portion 37 is arranged inside an annular groove 13g formed in the inner peripheral surface of the tip portion of the shaft portion 13c.
  • the flange portion 37 is arranged so as to be axially sandwiched between a spring retainer 41 with which one axial end portion of the compression coil spring 32 is in elastic contact and a valve seat 44 to be described later.
  • the spring retainer 41 is formed of a metal plate in an annular shape, and a large-diameter insertion hole 41a is formed through the center along the axial direction.
  • the outer peripheral surface of the spring retainer 41 is press-fitted into the inner peripheral surface of the annular groove 13g, and the annular front end wall is in axial contact with the stepped surface 13h of the annular groove 13g via an O-ring 49.
  • the valve accommodation recess 40 accommodates a first check valve 42 that allows hydraulic oil to flow only in the direction from the supply passage 29 to the first sleeve oil passage 38 .
  • the first check valve 42 is composed of a valve member 43, a valve seat 44 on which the valve member 43 is seated, and a check spring 45 that biases the valve member 43 toward the valve seat 44 side.
  • the valve member 43 is made of a relatively hard metal, such as an iron-based metal, and is press-formed into a substantially cup-like shape. A significant gap is formed.
  • the valve member 43 includes a convex valve portion 46 that is seated on and off the valve seat 44 , and an axially extending outer periphery of one end of the valve portion 46 . and a guide portion 47 that is slidably guided with a minute clearance.
  • the valve portion 46 has a first spherical portion 46a formed in a spherical shape at its tip portion.
  • the first spherical portion 46 a receives the hydraulic pressure of hydraulic oil in the direction from the supply passage 29 toward the first sleeve oil passage 38 . Further, the first spherical portion 46a abuts or separates from the inner peripheral edge portion on one side of the passage hole 44a of the valve seat 44 in the axial direction, that is, is seated and separated.
  • the valve portion 46 has a second spherical portion 46b formed on the side opposite to the first spherical portion 46a. It is designed to be enforced.
  • the guide part 47 has four substantially rectangular communication holes 47a at equally spaced positions in the circumferential direction of the valve member 43 at the base of the valve part 46. As shown in FIG. When the valve member 43 moves to one side in the axial direction against the biasing force of the check spring 45 due to the hydraulic pressure acting on the first spherical surface portion 46 a , the tip portion 47 b of the guide portion 47 tilts the sleeve body 36 . It abuts against the cylindrical wall portion 36b.
  • the valve seat 44 is formed in the shape of a disk plate, and a passage hole 44a is formed through the central portion that is bulging and deformed toward the valve member 43 along the axial direction.
  • the valve seat 44 has an outer peripheral portion inserted into the inner peripheral side of the annular groove 13g from the axial direction.
  • the valve seat 44 is restrained from coming off to the outside of the valve body 13 by a substantially C-shaped first stopper member 48 , and the front end surface of the outer peripheral portion of the valve seat 44 is aligned with the axial end edge of the outer peripheral portion of the spring retainer 41 . is adapted to abut on the
  • the valve member 43 is designed to open and close the passage hole 44a by being seated and separated from the hole edge of the passage hole 44a.
  • the spring force of the check spring 45 is compressed and deformed by a predetermined hydraulic pressure acting on the first spherical portion 46a of the valve member 43 from the passage hole 44a.
  • the size is set to the extent that 44a is opened.
  • the first stopper member 48 is made of a metal material and is generally C-shaped.
  • the outer peripheral portion of the first stopper member 48 is fitted into the groove portion 13i formed on the inner peripheral surface of the annular groove 13g, so that the valve seat 44 and the like move to the other side in the axial direction and out of the valve body 13. and to prevent them from falling off.
  • a through hole 48a is formed in the center of the first stopper member 48 to communicate the supply passage 29 and the passage hole 44a.
  • the O-ring 49 is made of rubber and arranged between the step surface 13h of the annular groove 13g and the spring retainer 41.
  • the elastic force of the O-ring 49 presses the first stopper member 48 against the wall surface on the other axial side of the groove portion 13i through the spring retainer 41 and the valve seat 44, so that the spring retainer 41 and the like are axially disengaged. Suppresses stickiness. Further, the O-ring 49 liquid-tightly seals between the spring retainer 41 and the annular groove 13g.
  • the spool valve 31 is formed in a substantially cylindrical shape as shown in FIG. 3, and is provided so that the inner peripheral surface can slide axially with respect to the outer peripheral surface of the sleeve body 36 . Further, the spool valve 31 has first to third lands 31a to 31c on the outer peripheral surface of one axial end, an axial center and the other axial end. The width of the first land portion 31a along the axial direction of the valve body 13 is formed shorter than the width of the second and third land portions 31b, 31c along the axial direction of the valve body 13. As shown in FIG.
  • a one end side spool hole 50 is formed radially penetrating between the retard port 34 and the first sleeve oil passage 38 or a drain passage 54, which will be described later. It is
  • the one-end-side spool hole 50 has a bottom portion of a first outer annular recess 31d formed on the outer peripheral surface of the spool valve 31 and a first inner annular recess 31f formed on the inner peripheral surface of the spool valve 31. is radially penetrating between the bottom of the As shown in FIG. 5, a plurality (eight in this embodiment) of the one end spool holes 50 are formed at equal intervals in the circumferential direction.
  • the other end side spool hole 51 which appropriately communicates the retarded angle port 34 or the advanced angle port 35 with the first sleeve oil passage 38, extends in the radial direction. Penetration is formed.
  • the other end spool hole 51 has a bottom portion of a second outer annular recess 31e formed on the outer peripheral surface of the spool valve 31 and a second inner annular recess formed on the inner peripheral surface of the spool valve 31. 31g and the bottom portion thereof are radially penetratingly formed. A plurality (eight in this embodiment) of the other end side spool holes 51 are formed at equally spaced positions in the circumferential direction.
  • a first inner annular recess 31f is formed on the inner peripheral surface of the spool valve 31 at a position generally corresponding to the first outer annular recess 31d.
  • a second check valve 56 which will be described later, is provided in the first inner annular concave portion 31f.
  • a second inner annular recess 31g is formed on the inner peripheral surface of the spool valve 31 at a position substantially corresponding to the second outer annular recess 31e.
  • the compression coil spring 32 which is a biasing member, has one axial end elastically contacting the other axial end surface of the spool valve 31 and the other axial end elastically contacting the one axial end surface of the spring retainer 41 . is arranged between the spool valve 31 and the spring retainer 41 so as to contact the . Thereby, the compression coil spring 32 urges the spool valve 31 to one side in the axial direction.
  • a cylindrical member 52 is provided on one end face of the spool valve 31 in the axial direction to receive a pressing force toward the sleeve 30 side from the electromagnetic actuator 33 and transmit it to the spool valve 31 .
  • the cylindrical member 52 is integrally formed of a metal material, and as shown in FIG. 1, has an outer diameter that is large and small in the axial direction with an annular protrusion 52a interposed therebetween.
  • the cylindrical member 52 includes a large diameter tubular portion 52b on the spool valve 31 side, a small diameter tubular portion 52c on the push rod 62 side of the electromagnetic actuator 33, and between the large diameter tubular portion 52b and the small diameter tubular portion 52c. It has an integrally provided annular protrusion 52a.
  • a plurality (four in this embodiment) of supply holes 52d for supplying hydraulic oil that has passed through the outer circumference of the large-diameter tubular portion 52b extends through the large-diameter tubular portion 52b along the radial direction. formed.
  • the supply holes 52d are formed in a circular shape when viewed in the radial direction, and are arranged at equal intervals of 90° in the circumferential direction of the cylindrical member 52. As shown in FIG.
  • the small-diameter cylindrical portion 52c is formed in a bottomed shape, and the pressing portion 62a of the push rod 62 of the electromagnetic actuator 33 abuts axially on the distal end surface.
  • the small-diameter tubular portion 52c cooperates with the spring force of the compression coil spring 32 to hold the spool valve 31 at a predetermined position in the axial direction.
  • a plurality (four in this embodiment) of discharge holes 52e for discharging the working oil that has passed through the second sleeve oil passage 39 to the outside is formed through the small-diameter cylindrical portion 52c along the radial direction. ing.
  • the discharge holes 52e are formed in a circular shape when viewed from the radial direction, and are arranged at equal intervals of 90° in the circumferential direction of the cylindrical member 52. As shown in FIG.
  • the annular protrusion 52a has an annular shape protruding radially outward from the outer peripheral portion of one axial end of the large-diameter cylindrical portion 52b. As shown in FIG. 3, the annular protrusion 52a has four notches 52f formed at equal intervals of 90° in the circumferential direction of the cylindrical member 52. As shown in FIG. A fan-shaped portion 52g is provided between two cutout portions 52f adjacent in the circumferential direction of the cylindrical member 52. It is slidable on the surface.
  • the space between the cylindrical member 52 and the inner peripheral surface of the valve body 13 is retarded via the first outer annular recess 31 d when the spool valve 31 is moved to one side in the axial direction by the biasing force of the compression coil spring 32 .
  • a drain passage 54 that can communicate with the corner port 34 is formed.
  • the drain passage 54 is supplied with hydraulic pressure from each retarding hydraulic chamber 9 via the retarding port 34 and the first outer annular recess 31d.
  • the hydraulic pressure supplied to the drain passage 54 is discharged to the discharge passage 28 through a gap between the through hole 55a of the second stopper member 55 and the outer peripheral surface of the small-diameter cylindrical portion 52c, which will be described later.
  • a second stopper member 55 is provided at one end of the valve body 13 on the head 13b side.
  • the second stopper member 55 is made of a metal material and is generally C-shaped. This prevents it from moving in one direction and dropping out of the valve body 13 .
  • the second stopper member 55 has a substantially circular through hole 55a that penetrates in the axial direction.
  • the inner diameter of the through hole 55a is formed larger than the outer diameter of the small-diameter tubular portion 52c. As a result, the small-diameter cylindrical portion 52c is axially movable through the through hole 55a.
  • the second check valves 56 are formed by rolling a thin metal plate such as leaf spring steel (a plate-like member) into a circular shape, and are arranged at substantially equal intervals in the circumferential direction of the second check valves 56 using, for example, a laser.
  • a plurality of (two in this embodiment) plate-like tongue portions 57 are formed in the frame portion 58 .
  • the tongue portion 57 is provided at the center position of the frame portion 58 in the width direction.
  • the second check valve 56 is arranged inside the spool valve 31 with both ends in the circumferential direction overlapped with each other.
  • the second check valve 56 is arranged so as to be circumferentially rotatable with respect to the spool valve 31 .
  • the second check valve 56 may be arranged so as to be non-rotatable in the circumferential direction with respect to the spool valve 31 by fixing the outer surface of the frame body portion 58 to the inner peripheral surface of the spool valve 31 by bonding or the like. good.
  • the second check valve 56 When the second check valve 56 is arranged inside the spool valve 31, the second check valve 56 includes a substantially cylindrical frame portion 58 arranged on the inner periphery of the spool valve 31 and a spool hole on one end side. and two arcuate tongue portions 57 that are radially opposed to each other and that can be deformed radially inward upon receiving the hydraulic pressure from 50 .
  • the circumferential length of the tongue portion 57 of the second check valve 56 in the rolled state is at least It is set to the extent that the two one end side spool holes 50 can be closed from the inside.
  • the one end side spool hole 50a and the one end side spool hole 50 radially opposed to the spool valve 31 are defined as the "one end side spool hole 50b".
  • the tongue portion 57 that radially faces the one end spool hole 50a and the spool valve 31 is defined as a “first tongue portion 57a”
  • the tongue portion 57 that radially faces the one end spool hole 50b and the spool valve 31 is defined as a “first tongue portion 57a”.
  • the piece 57 is defined as a "second tongue piece 57b".
  • the first tongue portion 57a can switch between communication and non-communication between the one end side spool hole 50a and the inside of the spool valve 31 based on the working oil pressure from the one end side spool hole 50a.
  • the first tongue portion 57a is deformed inward in the radial direction by receiving the operating oil pressure from the one end side spool hole 50a. 31, and contacts the inner circumference of the spool valve 31 to restrict the flow of hydraulic oil from the inside of the spool valve 31 to the one end spool hole 50a. .
  • the first tongue piece 57a communicates and disconnects the one end spool hole 50a with the inside of the spool valve 31, and also connects the one end spool hole 50a and the root portion of the first tongue piece 57a in the circumferential direction. Communication and non-communication between the one end side spool hole 50c adjacent to the spool valve 31 and the inside of the spool valve 31 can also be switched. That is, the first tongue portion 57a is deformed inward in the radial direction by receiving the operating oil pressure from the one end side spool hole 50c. 31, and contacts the inner periphery of the spool valve 31 to restrict the flow of hydraulic oil from the inside of the spool valve 31 to the one end spool hole 50c. .
  • the second tongue portion 57b can switch between communication and non-communication between the one end side spool hole 50b and the inside of the spool valve 31 based on the hydraulic pressure from the one end side spool hole 50b.
  • the second tongue portion 57b is deformed radially inward upon receiving the hydraulic pressure from the one end spool hole 50b, and the spool valve 57b is connected to the one end spool hole 50b through the opening 65 formed after this deformation. 31, and contacts the inner periphery of the spool valve 31 to restrict the flow of hydraulic oil from the inside of the spool valve 31 to the one end spool hole 50b.
  • the second tongue piece 57b communicates and disconnects the one end spool hole 50b and the inside of the spool valve 31, and also allows the one end spool hole 50b and the root portion of the second tongue piece 57b to communicate with each other in the circumferential direction. Communication and non-communication between the one end side spool hole 50d adjacent to the spool valve 31 and the inside of the spool valve 31 can also be switched.
  • the second tongue portion 57b is deformed radially inward upon receiving the operating oil pressure from the one end spool hole 50d, so that the spool valve 57b is connected to the one end spool hole 50d via the opening 65 formed after this deformation. 31, and abuts against the inner circumference of the spool valve 31, thereby suppressing the flow of hydraulic oil from the inside of the spool valve 31 to the one end spool hole 50d. .
  • the first and second tongue portions 57a and 57b can switch between communication and non-communication of the one end spool holes 50a and 50c and the one end spool holes 50b and 50d that are adjacent in the circumferential direction. Even if the stop valve 56 rotates with respect to the spool valve 31, it is applied to the adjacent two one end side spool holes 50, 50 facing the first and second tongue portions 57a, 57b after rotation.
  • the number of tongue pieces 57 is set by the number of one end spool holes 50 . More specifically, the number of tongue portions 57 and the number of one-end spool holes 50 are set to be the same, or set to be a multiple of either. In this embodiment, the number of one end spool holes 50, which is eight, is set to be four times the number of tongue portions 57, which is two. In addition, “almost” in the above “circumferentially equally spaced positions" includes an error of ⁇ 5 degrees, for example, a manufacturing error.
  • the electromagnetic actuator 33 is mainly composed of a casing 59, a solenoid 60, a movable iron core 61, and a push rod 62, as shown in FIG.
  • the casing 59 is made of a synthetic resin material, and is provided with a connector portion 59a electrically connected to the control unit 63, which is an ECU, at its upper end.
  • the connector portion 59a has a pair of terminal strips 59b embedded in the casing 59, and one end of each of the terminal strips 59b is connected to the solenoid 60. As shown in FIG. On the other hand, the other ends exposed to the outside are connected to the terminals of the male connector on the control unit 63 side.
  • the movable iron core 61 has a cylindrical shape and is provided inside the bobbin 64 so as to be slidable in the axial direction.
  • the solenoid 60 When the solenoid 60 is not energized, the movable iron core 61 moves backward in one axial direction via the spool valve 31 , the cylindrical member 52 and the push rod 62 due to the spring force of the compression coil spring 32 .
  • the solenoid 60 is housed inside the casing 59 via a magnetic bobbin 64 .
  • the solenoid 60 is energized by being energized by the control unit 63 to move the movable iron core 61 forward, that is, to move the spool valve 31 to the other side in the axial direction against the spring force of the compression coil spring 32 .
  • the push rod 62 is integrally connected to the tip of the movable iron core 61, and the pressing part 62a at the tip abuts the tip of the small-diameter cylindrical part 36a of the cylindrical member 52 from the axial direction.
  • the spool valve 31 is continuously controlled to move between the maximum axial position on the other side and the maximum axial position on the one side according to the amount of power supplied to the solenoid 60 during non-energization and power supply.
  • the movable iron core 61 and the pressing portion 62a are pressed against the spring force of the compression coil spring 32 to the other side in the axial direction, and the position of the spool valve 31 is adjusted. is continuously moved.
  • 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 the current rotational phase of the camshaft 2 (not shown). Information signals from various sensors such as cam angle sensors are input. This allows the current engine operating state to be detected.
  • the control unit 63 cuts off the energization of the solenoid 60 of the electromagnetic actuator 33 to control the spool valve 31 to the first movement position, or outputs a pulse signal to the solenoid 60 to control the amount of energization (duty ratio). As a result, the spool valve 31 is continuously variably controlled to the second to fourth movement positions.
  • FIG. 7 is a longitudinal sectional view showing the first movement position of the spool valve 31 in the control valve 26 of the first embodiment.
  • FIG. 8 is a longitudinal sectional view showing the second movement position of the spool valve 31 in the control valve 26 of the first embodiment.
  • FIG. 9 is a longitudinal sectional view showing the third movement position of the spool valve 31 in the control valve 26 of the first embodiment.
  • FIG. 10 is a longitudinal sectional view showing the fourth movement position of the spool valve 31 in the control valve 26 of the first embodiment.
  • the oil pump 25 When the engine is stopped, the oil pump 25 is also stopped so that hydraulic oil is not supplied from the discharge passage 25a, and the power supply from the control unit 63 to the solenoid 60 is cut off. Therefore, as shown in FIG. 7, the spool valve 31 is held at the maximum one side position in the axial direction by the biasing force of the compression coil spring 32 (first movement position). At the first movement position, the annular protrusion 52a of the cylindrical member 52 is in contact with the hole edge of the through hole 55a of the second stopper member 55. As shown in FIG.
  • the retard port 34 communicates with the first sleeve oil passage 38 via the second outer annular recess 31e, the other end spool hole 51, the second inner annular recess 31g, and the first opening 36g. ing.
  • the advance port 35 passes through the gap of the compression coil spring 32 arranged between the outer peripheral surface of the sleeve 30 and the inner peripheral surface of the valve body 13 and the second opening 36h of the sleeve body 36, It communicates with the second sleeve oil passage 39 . Therefore, as indicated by arrow A in FIG. 7, the hydraulic oil in each advance hydraulic chamber 10 flows from each advance port 35 through the gap between the compression coil springs 32 and the second opening 36h to the second sleeve. It flows into the oil passage 39, passes through the drain passage 66 in the cylindrical member 52 from the second sleeve oil passage 39, and is discharged to the outside of the valve body 13 through each discharge hole 52e.
  • the oil pump 25 is also driven accordingly, and the operating oil pressure discharged to the discharge passage 25a is supplied to the supply passage 29 and the through hole 48a of the first stopper member 48. and acts on the first spherical portion 46a of the valve portion 46 of the valve member 43 through the .
  • the valve member 43 moves to one side in the axial direction of the valve body 13 against the biasing force of the check spring 45 and comes into contact with the inclined cylindrical wall portion 36 b of the sleeve body 36 .
  • the valve portion 46 With this movement of the valve member 43, the valve portion 46 is separated from the valve seat 44, and the working oil pressure increases to the gap between the valve portion 46 and the valve seat 44 and the pressure of the valve member 43 as indicated by arrow B in FIG. It flows into the first sleeve oil passage 38 through the communication hole 47a. Then, from the first sleeve oil passage 38, the operating oil pressure passes through the first opening hole 36g, the second inner annular recess 31g, the other end spool hole 51, the second outer annular recess 31e, and the retard port 34. It is supplied to the retarding hydraulic chamber 9 . As a result, the pressure inside each retarding hydraulic chamber 9 becomes high.
  • the spool valve 31 moves slightly toward the other end in the axial direction to the second movement position shown in FIG. .
  • the retarded angle port 34 communicates with the first sleeve oil passage 38 via the second outer annular recess 31e, the other end spool hole 51, the second inner annular recess 31g, and the first opening 36g.
  • the advance port 35 communicates with the first sleeve oil passage 38 via the second outer annular recess 31e, the other end spool hole 51, the second inner annular recess 31g and the first opening 36g.
  • the spool valve 31 moves to the other end in the axial direction to the third movement position.
  • the retard port 34 communicates with the drain passage 54 via the first outer annular recess 31d
  • the advance port 35 communicates with the second outer annular recess 31e, the other end spool hole 51, and the second inner annular recess 31e. It communicates with the first sleeve oil passage 38 via the recess 31g and the first opening 36g.
  • the working oil pressure in each retarding hydraulic chamber 9 flows through each retarding port 34 and the first outer annular recess 31d to the drain passage 54, as indicated by arrow D in FIG.
  • the valve is It is discharged outside the body 13 . Therefore, the pressure in each retarding hydraulic chamber 9 becomes low.
  • the hydraulic pressure discharged from the oil pump 25 to the discharge passage 25a passes through the supply passage 29 and the through hole 55a of the first stopper member 48 and acts on the first spherical portion 46a of the valve portion 46 of the valve member 43.
  • the valve member 43 moves to one side in the axial direction of the valve body 13 against the biasing force of the check spring 45 and comes into contact with the inclined cylindrical wall portion 36 b of the sleeve body 36 .
  • the valve portion 46 is separated from the valve seat 44, and the working oil pressure increases as indicated by the arrow E in FIG. It flows into the first sleeve oil passage 38 through the communication hole 47a.
  • the hydraulic pressure is supplied through the first opening hole 36g, the second inner annular recess 31g, the other end spool hole 51, the second outer annular recess 31e and the advance port 35. It is supplied to the advance hydraulic chamber 10 . Therefore, the pressure inside each advance hydraulic chamber 10 becomes high.
  • the energization amount (duty ratio) from the control unit 63 to the solenoid 60 is increased to near the maximum.
  • the spool valve 31 is pressed against the spring force of the compression coil spring 32 by the movable iron core 61 and the pressing portion 62a, thereby reaching the maximum position on the other side in the axial direction. 4 Move to the movement position. Therefore, the first land portion 31a of the spool valve 31 closes the drain passage 54 and cuts off the communication between the first outer annular recess 31d and the retardation port 34. Hydraulic pressure is stopped. At the same time, the retard port 34 communicates with the first spool hole 50 via the first outer annular recess 31d.
  • each retard hydraulic chamber 9 passes from the retard port 34 through the first outer annular recess 31 d and the one end spool hole 50 and acts on the outer peripheral surface of the second check valve 56 .
  • the second check valve 56 which is in elastic contact with the bottom surface of the second inner annular recess 31g, is disengaged by the operating hydraulic pressure.
  • Each tongue 57 deforms radially inwardly of the spool valve 31, thereby forming an opening 65 where the tongue 57 was before deformation.
  • the working oil pressure in each retarding oil pressure chamber 9 flows into the opening 65 through the first outer annular recess 31d and the one end spool hole 50.
  • each advance hydraulic chamber 10 As shown in FIG. Next, from this opening 65, the hydraulic pressure is rapidly supplied to each advance hydraulic chamber 10 through the second inner annular recess 31g, the other end spool hole 51 and the second outer annular recess 31e. Therefore, the internal pressure of each advance hydraulic chamber 10 can be rapidly increased, and the vane rotor 7 can be rapidly relatively rotated to the most advanced side.
  • the eight one-end-side spool holes 50 are provided in the circumferential direction of the cylindrical spool valve 31 , and the inner circumference of the spool valve 31 is provided in the circumferential direction of the spool valve 31 .
  • a second check valve 56 is provided having two tongues 57 which are substantially equally spaced. Each tongue portion 57 deforms radially inwardly of the spool valve 31 to allow hydraulic fluid to flow from each one end side spool hole 50 into the spool valve 31 . Therefore, since the two tongue portions 57 receive hydraulic pressure equally from the radial direction, the diameter of the substantially cylindrical frame portion 58 of the second check valve 56 is uniformly reduced.
  • the frame body portion 58 is uniformly reduced in diameter while eccentricity within the spool valve 31 is suppressed, and is held in a stable position within the spool valve 31 . Therefore, it becomes difficult for a partial region of the outer surface of the frame body portion 58 to locally apply a load to a partial region of the inner peripheral portion of the spool valve 31 , and the load causes a portion of the outer peripheral portion of the spool valve 31 to move. abuts against a partial region of the inner peripheral portion of the valve body 13, thereby suppressing friction between the two. Therefore, the operation of the spool valve 31 with respect to the valve body 13 can be improved.
  • the first tongue portion 57a deforms radially inward, thereby causing hydraulic oil to flow from the one end spool hole 50a of the plurality of one end spool holes 50 into the spool valve 31.
  • the second tongue portion 57b deforms inward in the radial direction so that hydraulic oil flows from the one end spool hole 50b of the plurality of one end spool holes 50 into the spool valve 31. Allow flow.
  • the first tongue portion 57 a and the second tongue portion 57 b are arranged so as to face each other in the radial direction of the spool valve 31 .
  • the force of moving the frame portion 58 due to the deformation of the first tongue portion 57a is offset by the force of moving the frame portion 58 due to the deformation of the second tongue portion 57b.
  • the position of the frame portion 58 inside the spool valve 31 is further stabilized. Therefore, the operation of the spool valve 31 with respect to the valve body 13 can be efficiently improved.
  • the first tongue portion 57a communicates and disconnects the one end spool hole 50a with the inside of the spool valve 31, and also allows the one end spool hole 50a and the first tongue portion 57a to communicate with each other in the circumferential direction. Communication and non-communication between the one end side spool hole 50c adjacent to the root portion side of the piece portion 57a and the inside of the spool valve 31 can also be switched.
  • the second tongue portion 57b communicates and disconnects the one end side spool hole 50b and the inside of the spool valve 31, and in addition, the root portion of the one end side spool hole 50b and the second tongue portion 57b in the circumferential direction.
  • the first tongue portion 57a and the second tongue portion 57b and the number of the one end side spool holes 50 whose communication and non-communication are switched by the first tongue portion 57a and the second tongue portion 57b Even if they do not correspond one-to-one, the first tongue portion 57a and the second tongue portion 57b are arranged at substantially equal intervals in the circumferential direction, and the one end spool holes 50 are arranged at equal intervals in the circumferential direction. As long as they are arranged, the first tongue portion 57a and the second tongue portion 57b of the second check valve 56 can function.
  • the second check valve 56 is arranged rotatably with respect to the spool valve 31 .
  • the eight one-end spool holes 50 are arranged at equal intervals in the circumferential direction of the spool valve 31, and the two tongue portions 57 are arranged at substantially equal intervals in the circumferential direction of the spool valve 31. Therefore, even when the second check valve 56 rotates, the first tongue portion 57a and the second tongue portion 57b receive hydraulic pressure from the corresponding one-end spool holes 50 at positions after rotation. .
  • FIG. 11 is a cross-sectional view of the control valve 26 of the second embodiment.
  • the number of tongue pieces 57 is the same as the number of one end spool holes 50 . That is, in the second embodiment, the number of tongue pieces 57 is two, and the number of one end side spool holes 50 is also two.
  • the two tongue portions 57 are a first tongue portion 57a and a second tongue portion 57b having the same shape
  • the two one end side spool holes 50 are the one end side spool having the same shape. holes 50a and 50b.
  • the two one end spool holes 50a and 50b are arranged to face each other in the radial direction of the spool valve 31 and extend over an angular range of about 160° in the circumferential direction of the spool valve 31. ing. That is, the one-end spool holes 50a and 50b are arranged at equal intervals in the circumferential direction of the spool valve 31, that is, at positions opposite to each other by 180°, and extend over an angular range of approximately 160° in the circumferential direction of the spool valve 31.
  • the first and second tongue portions 57a and 57b are provided at substantially equal intervals in the circumferential direction of the spool valve 31, that is, at 180° opposite sides.
  • the first tongue portion 57a is provided at a position facing the one end spool hole 50a and the spool valve 31 in the radial direction.
  • the length of the first tongue portion 57a along the circumferential direction of the spool valve 31 is smaller than the length of the one end side spool holes 50a and 50b along the circumferential direction of the spool valve 31. As shown in FIG.
  • the second tongue portion 57b is provided at a position facing the one end side spool hole 50b and the spool valve 31 in the radial direction.
  • the length of the second tongue portion 57b along the circumferential direction of the spool valve 31 is smaller than the length of the one end side spool holes 50a, 50b along the circumferential direction of the spool valve 31. As shown in FIG.
  • the one end spool holes 50a and 50b are arranged so as to face each other in the radial direction of the spool valve 31.
  • 57b are provided at substantially equal intervals in the circumferential direction of the spool valve 31, that is, at positions on the opposite side of 180°.
  • the diameter of the frame body portion 58 is uniformly reduced, so that the position of the frame body portion 58 inside the spool valve 31 is maintained, and the operation of the spool valve 31 with respect to the valve body 13 is improved.
  • FIG. 12 is a cross-sectional view of the control valve 26 of the third embodiment.
  • the number of tongue pieces 57 is the same as the number of one end spool holes 50 . That is, in the third embodiment, the number of tongue portions 57 is three, and the number of one end side spool holes 50 is also three. In other words, the three tongue portions 57 are the first tongue portion 57a, the second tongue portion 57b and the third tongue portion 57c having the same shape, and the three one end side spool holes 50 are the same. , one end side spool holes 50a, 50e, and 50f having a shape of .
  • the three one-end spool holes 50a, 50e, and 50f are arranged at equal intervals in the circumferential direction of the spool valve 31, that is, at positions shifted by 120°. extends over an angular range of approximately 80°.
  • the first, second and third tongue portions 57a, 57b, 57c are provided at substantially equal intervals in the circumferential direction of the spool valve 31, that is, at positions shifted by 120°.
  • the first tongue portion 57a is provided at a position facing the one end spool hole 50a and the spool valve 31 in the radial direction.
  • the length of the first tongue portion 57a along the circumferential direction of the spool valve 31 is approximately equal to the length of the one end side spool holes 50a, 50e, 50f along the circumferential direction of the spool valve 31. As shown in FIG.
  • the second tongue portion 57b is provided at a position facing the one end side spool hole 50e and the spool valve 31 in the radial direction.
  • the length of the second tongue portion 57b along the circumferential direction of the spool valve 31 is substantially equal to the length of the one end side spool holes 50a, 50e, 50f along the circumferential direction of the spool valve 31. As shown in FIG.
  • the third tongue portion 57c is provided at a position facing the one end side spool hole 50f and the spool valve 31 in the radial direction.
  • the length of the third tongue portion 57c along the circumferential direction of the spool valve 31 is approximately equal to the length of the one end side spool holes 50a, 50e, 50f along the circumferential direction of the spool valve 31. As shown in FIG.
  • the one-end spool holes 50a, 50e, and 50f are arranged at equal intervals in the circumferential direction of the spool valve 31, that is, at positions shifted by 120°.
  • the first, second and third tongue portions 57a, 57b, 57c are provided at substantially equal intervals in the circumferential direction of the spool valve 31, that is, at positions shifted by 120°.
  • the first, second and third tongue portions 57a, 57b and 57c are not opposed to the spool valve 31 in the radial direction, but are shifted from the first, second and third tongue portions 57a, 57b and 57c by 120°.
  • the working oil pressure uniformly acts on the outer surfaces of the third tongue pieces 57a, 57b, and 57c, and the diameter of the frame body 58 is also uniformly reduced, and the position of the frame body 58 inside the spool valve 31 is maintained. be. Therefore, the operation of the spool valve 31 with respect to the valve body 13 can be improved.
  • FIG. 13 is a sectional view of the control valve 26 of the fourth embodiment.
  • the number of tongue pieces 57 is twice the number of one end spool holes 50 . That is, in the fourth embodiment, the number of tongue pieces 57 is six, and the number of one end spool holes 50 is three.
  • the six tongue portions 57 are the first to sixth tongue portions 57a to 57f having the same shape
  • the three one end side spool holes 50 are the one end side spool hole 50a having the same shape. , 50e and 50f.
  • the three one-end spool holes 50a, 50e, and 50f are arranged at equal intervals in the circumferential direction of the spool valve 31, that is, at positions shifted by 120°. It extends over an angular range of about 80°.
  • the first to sixth tongue portions 57a to 57f are provided at substantially equal intervals in the circumferential direction of the spool valve 31, that is, at positions shifted by 60°.
  • the first tongue portion 57a and the second tongue portion 57b are provided at positions facing the one end side spool hole 50a and the spool valve 31 in the radial direction.
  • the third tongue portion 57c and the fourth tongue portion 57d are provided at positions facing the one end side spool hole 50e and the spool valve 31 in the radial direction.
  • the fifth tongue portion 57e and the sixth tongue portion 57f are provided at positions facing the one end side spool hole 50f and the spool valve 31 in the radial direction.
  • the lengths of the first to sixth tongue portions 57a to 57f along the circumferential direction of the spool valve 31 are shorter than the lengths of the one end side spool holes 50a, 50e, 50f along the circumferential direction of the spool valve 31.
  • the one end spool holes 50a, 50e, and 50f are arranged at equal intervals in the circumferential direction of the spool valve 31, that is, at positions shifted by 120°.
  • the to sixth tongue portions 57a to 57f are provided at substantially equal intervals in the circumferential direction of the spool valve 31, that is, at positions shifted by 60°.
  • the working oil pressure acts evenly on the outer surfaces of the first to sixth tongue pieces 57a to 57f, and the diameter of the frame portion 58 is also uniformly reduced. The position of the frame portion 58 inside the is held. Therefore, the operation of the spool valve 31 with respect to the valve body 13 can be improved.
  • FIG. 14 is a plan view showing the second check valve 56 of the fifth embodiment in an unfolded state.
  • the tongue piece portion 57 is not formed in a rectangular shape as a whole, but a rectangular portion 57g located on the root portion side and a circular portion formed integrally with the rectangular portion 57g. It has a shape combined with the portion 57h. Although four tongue portions 57 are provided as an example in FIG. can do.
  • the diameter of the frame portion 58 is evenly reduced to maintain the position of the frame portion 58 inside the spool valve 31, thereby improving the operation of the spool valve 31 with respect to the valve body 13.
  • FIG. 15 is a plan view showing the second check valve 56 of the sixth embodiment in an unfolded state.
  • the tongue portion 57 has a rectangular shape, but is provided at a position closer to one end side of the frame portion 58 in the width direction. 15, the tongue portion 57 is formed such that one long side portion 57i and a short side portion 57j positioned at the tip are adjacent to the frame body portion 58. As shown in FIG. Although four tongue portions 57 are provided as an example in FIG. can do.
  • the diameter of the frame portion 58 is evenly reduced, so that the position of the frame portion 58 inside the spool valve 31 is maintained, and the operation of the spool valve 31 with respect to the valve body 13 is improved.
  • FIG. 16 is a plan view showing the second check valve 56 of the seventh embodiment in an unfolded state.
  • the rectangular tongue portions 57 are provided in two stages in the width direction of the frame portion 58 and in four rows in the longitudinal direction of the frame portion 58, for a total of eight pieces. Note that the tongue portion 57 may be configured in any number of stages and rows as long as it has two or more stages and two or more rows.
  • the diameter of the frame portion 58 is evenly reduced, so that the position of the frame portion 58 inside the spool valve 31 is maintained, and the operation of the spool valve 31 with respect to the valve body 13 is improved.
  • control valve used for the hydraulic control valve based on the embodiment described above, for example, the following modes are conceivable.
  • a cylindrical valve body having a first port and a second port radially penetrating therethrough, and a valve body axially slidable on the inner circumference of the valve body.
  • a cylindrical spool valve arranged and provided with a plurality of spool holes in the circumferential direction; a frame portion arranged on the inner circumference of the spool valve and formed by rolling a plate-like member; and integrally with the frame portion. and a plurality of tongue portions arranged at equal intervals in the circumferential direction, the tongue portions being deformed radially inward to operate from the plurality of spool holes to the inside of the spool valve.
  • a check valve that allows the flow of oil and restricts the flow of hydraulic oil from the inside of the spool valve to the plurality of spool holes by abutting against the inner circumference of the spool valve.
  • the plurality of tongue pieces are deformed radially inward to prevent hydraulic fluid from flowing from a first spool hole of the plurality of spool holes to the inside of the spool valve.
  • a first tongue piece portion that restricts the flow of hydraulic oil from the inside of the spool valve to the first spool hole by contacting the inner circumference of the spool valve, and the first tongue portion that deforms radially inward to prevent the Hydraulic oil is allowed to flow from the second spool hole of the plurality of spool holes to the inside of the spool valve, and contacts the inner periphery of the spool valve to flow from the inside of the spool valve to the second spool hole. and a second tongue portion that suppresses the flow of hydraulic oil.
  • the first spool hole and the second spool hole are arranged to face each other in the radial direction of the spool valve, and the first tongue The portion and the second tongue portion are arranged so as to face each other in the radial direction of the spool valve.
  • the plurality of tongue pieces restricts the flow of hydraulic oil from a third spool hole of the plurality of spool holes to the inside of the spool valve.
  • the first spool hole, the first spool hole, The second spool hole and the third spool hole are arranged at equal intervals in the circumferential direction of the spool valve, and the first tongue portion, the second tongue portion and the third tongue portion are arranged in the spool valve. are arranged at regular intervals in the circumferential direction of the
  • the first tongue piece can switch communication and non-communication between the first spool hole and the spool hole adjacent in the circumferential direction of the spool valve. and the second tongue portion can switch between communication and non-communication between the second spool hole and the spool hole adjacent in the circumferential direction of the spool valve.
  • the check valve is rotatably arranged with respect to the spool valve.
  • the check valve is non-rotatably arranged with respect to the spool valve.
  • the hydraulic control valve is used in a valve timing control device for an internal combustion engine, and the valve timing control device receives rotational force from a crankshaft.
  • a driven rotor that rotates integrally with the camshaft; and a plurality of hydraulic chambers provided between the drive rotor and the driven rotor. It is arranged inside the driven rotor and supplies and discharges hydraulic oil to and from the plurality of hydraulic chambers.
  • a cylindrical valve body having a first port and a second port radially penetrating therethrough, and a valve body axially slidable on the inner circumference of the valve body.
  • a spool valve provided with a plurality of radially opposed spool holes formed thereon, a frame body portion disposed on the inner circumference of the spool valve and formed by rolling a plate-like member, and a frame body portion integrally formed with the frame body. and deforms radially inward of the spool valve to allow hydraulic fluid to flow from a first spool hole out of the plurality of spool holes into the spool valve, and contact the inner periphery of the spool valve.
  • a first tongue portion that is formed integrally with the frame body portion and deforms radially inward of the spool valve, the first tongue portion suppressing the flow of hydraulic oil from the inside of the spool valve to the first spool hole by coming into contact with the first tongue portion. This allows the hydraulic oil to flow from the second spool hole of the plurality of spool holes into the spool valve, and the second spool hole is allowed to flow from the inside of the spool valve by coming into contact with the inner circumference of the spool valve.
  • a check valve having a second tongue that restricts flow of hydraulic fluid to the spool bore.

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

Abstract

L'invention concerne une soupape de commande qui comprend : un corps de soupape tubulaire (13) ayant un orifice d'avance (35) et un orifice de retard (34) ; un distributeur à tiroir tubulaire (31) disposé de manière coulissante dans la périphérie interne du corps de soupape (13) et pourvu de huit trous de bobine côté extrémité (50) dans la direction circonférentielle ; et un second clapet de non-retour (56) ayant une partie de corps de cadre approximativement tubulaire (58) disposée dans la périphérie interne du distributeur à tiroir cylindrique (31) et une première partie de pièce de languette (57a) et une seconde partie de pièce de languette (57b) qui sont formées d'un seul tenant avec la partie de corps de cadre (58). Les première et seconde parties de pièce de languette (57a, 57b) sont disposées à des positions sensiblement équidistantes dans la direction circonférentielle du distributeur à tiroir cylindrique (31). Les première et seconde parties de pièce de languette (57a, 57b) sont déformées radialement vers l'intérieur du distributeur à tiroir cylindrique (31) lorsqu'elles sont appliquées avec une pression d'huile de travail à partir des trous de bobine côté extrémité correspondants (50). À ce moment, les première et seconde pressions d'huile de travail sont opposées l'une à l'autre à travers le distributeur à tiroir cylindrique (31) et maintiennent la position du second clapet de non-retour (56) par rapport au distributeur à tiroir cylindrique (31).
PCT/JP2021/047460 2021-03-12 2021-12-22 Soupape de réglage de pression d'huile et dispositif de commande de réglage de distribution pour moteur à combustion interne WO2022190568A1 (fr)

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JP2021-040279 2021-03-12
JP2021040279A JP2024065127A (ja) 2021-03-12 2021-03-12 油圧制御弁および内燃機関のバルブタイミング制御装置

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018135573A1 (fr) * 2017-01-19 2018-07-26 株式会社デンソー Dispositif d'ajustage du réglage de distribution
JP2018522189A (ja) * 2015-07-20 2018-08-09 デルフィ・オートモーティブ・システムズ・ルクセンブルク・エスア 弁
WO2018179651A1 (fr) * 2017-03-29 2018-10-04 株式会社ミクニ Soupape à clapets
WO2018194076A1 (fr) * 2017-04-21 2018-10-25 株式会社デンソー Dispositif de réglage de distribution
WO2020152965A1 (fr) * 2019-01-21 2020-07-30 日立オートモティブシステムズ株式会社 Soupape de commande utilisée pour dispositif de commande de réglage de distribution pour moteur à combustion interne, et système de commande de réglage de distribution pour moteur à combustion interne

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018522189A (ja) * 2015-07-20 2018-08-09 デルフィ・オートモーティブ・システムズ・ルクセンブルク・エスア 弁
WO2018135573A1 (fr) * 2017-01-19 2018-07-26 株式会社デンソー Dispositif d'ajustage du réglage de distribution
WO2018179651A1 (fr) * 2017-03-29 2018-10-04 株式会社ミクニ Soupape à clapets
WO2018194076A1 (fr) * 2017-04-21 2018-10-25 株式会社デンソー Dispositif de réglage de distribution
WO2020152965A1 (fr) * 2019-01-21 2020-07-30 日立オートモティブシステムズ株式会社 Soupape de commande utilisée pour dispositif de commande de réglage de distribution pour moteur à combustion interne, et système de commande de réglage de distribution pour moteur à combustion interne

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