DE102019100111A1 - Valve timing - Google Patents

Abstract

A valve timing controller (A) includes: a driving-side rotating member (20) that rotates synchronously with a crankshaft (1) of an internal combustion engine (E); an output side rotary member (30) coaxially arranged with a rotation axis (X) of the drive side rotary member and integrally rotating with a camshaft (5); an advance and a retard chamber (Ca, Cb) formed between the drive-side and drive-side rotation members; a lock mechanism (L) which can make a transition to a locked state by providing a lock member (25) engageable with a lock recess portion (27); a connecting bolt (40) disposed coaxially with the rotating shaft connecting the driven side rotating member to the camshaft and having an inner space (40R), and a valve unit (Vb) providing supply and discharge of a fluid with respect to the advance and controls the retard chamber and the locking recess portion.

Description

TECHNICAL AREA

This disclosure relates to a valve timing controller that controls the relative rotational phase between a driving-side rotating member and a driven-side rotating member by means of a fluid pressure and keeps the relative rotational phase in a predetermined phase by means of a locking mechanism.

BACKGROUND

JP 2015-078635 A (Publication 1 ) discloses a technique as a valve timing controller configured as described above in which the axis of a driving-side rotating member and the axis of a driven-side rotating member are coaxially arranged, the relative rotational phase between the driving-side rotating member and the driven-side by means of a control of a solenoid valve being coaxial is arranged with the axis of the drive-side rotary member, is controlled and the relative rotational phase between the drive-side rotary member and the driven-side rotary member is held in an intermediate locking phase.

In the publication 1 an interlocking mechanism is formed so as to enable a transition to a locked state in the interlock phase in which the relative rotational phase between the drive-side rotating member and the driven-side rotating member becomes the most advanced phase and the most retarded phase. With this configuration, the relative rotational phase is adjusted by supplying and discharging a fluid with respect to an advance chamber and a retard chamber by controlling the spool of the solenoid valve, and the transition of the interlock mechanism to the locked state and the release of the locked state are performed.

According to the publication 1 According to the disclosed technology, portions (hereinafter referred to as locking portions) for transition of the interlocking mechanism to the locked state are set at both end positions of the operating range of the slider. In a case where the spool position is set in one of the lock portions, a fluid is discharged from a lock recess portion while continuing to supply fluid to the advance chamber or the retard chamber.

For example, in a valve timing provided with a solenoid valve in which a lock portion is set at a position adjacent to an advance range, the solenoid valve is configured such that the flow rate of the fluid supplied to the advance chamber increases as the slider moves approaches the lock area. This characteristic that a fluid increases according to a spooling operation is set in a range extending from the advancing range to the locking range, and the flow rate reaches its maximum in a state where the spool is at the outer end of the locking portion , Accordingly, in a state where the slider is in the lock phase, the relative rotational phase is rapidly shifted in the advance direction. In addition, even after reaching the interlocking phase by the relative rotational phase, the relative velocity between a locking member and the recessed portion is still high, and therefore engagement between the locking member and the recessed portion may not be possible.

For a transition of the locking mechanism to the locked state, it is important that a fluid is discharged from the recessed portion and the pressure in this recessed portion is sufficiently low. In the case of shifting the relative rotational phase at high speed, the relative rotational phase may reach the interlocking phase in a situation where the fluid in the recessed portion has not been sufficiently discharged and the fluid in the recessed portion is pressurized. In some cases, engagement between the locking member and the recessed portion is not possible in this situation.

One possible configuration for suppressing this disadvantage is a configuration having a phase control valve that controls fluid supply / fluid discharge with respect to the advance chamber and the retard chamber, and a lock control valve that controls a lock mechanism. With this configuration, the pressure of the fluid in the lock recess portion is lowered by discharging the fluid from the lock control valve when a lock mechanism transits to the locked state. In addition, in this state, the relative rotational phase is shifted based on a control of the phase control valve at a relatively low speed, and then a reliable transition to the locked state is possible.

However, the configuration with the two types of valves leads to an increase in the size of the device and an increase in the number of components, and therefore it can not be easily used.

Thus, there is a need for valve timing that allows a reliable transition of a locking mechanism to a locked state while using only a single slider.

SUMMARY

A valve timing according to an aspect of this disclosure includes a drive-side rotating member that rotates synchronously with a crankshaft of an internal combustion engine, an output-side rotating member disposed coaxially with an axis of rotation of the driving-side rotating member, and integral with a cam opening / closing valve An advance chamber and a retard chamber formed between the drive-side rotating member and the driven-side rotating member rotate a lock mechanism capable of transitioning to a locked state in an intermediate phase between relative rotational phases of the drive-side rotating member and the driven-side The rotary member is to perform by having a locking member which is provided in one of the drive-side rotary member and the driven-side rotary member and having a Verriegelungsvertiefungsabschnit t is formed, which is formed in the other of the drive-side rotary member and the driven-side rotary member, a connecting bolt, which is arranged coaxially with the rotational axis, the output-side rotary member connected to the camshaft and an inner space formed coaxially with the rotational axis is, and a valve unit, which controls a supply and a discharge of a fluid with respect to the advance chamber, the retard chamber and the Verriegelungsvertiefungsabschnitt on. The valve unit has a sleeve in contact with an inner circumference of the inner space of the connecting bolt, a slider operable along the axis of rotation in the sleeve, a solenoid that adjusts a position of the slider, and an advance opening associated with the advance chamber Connection, a retard opening, which communicates with the retard chamber and a locking opening, which communicates with the locking recess portion, which are formed as through holes on the connecting bolt and the sleeve, on. An operating portion of the spool is provided with a phase control portion which supplies the fluid to the advance or retard opening in a state of supply of the fluid to the lock opening, and a lock portion containing the fluid of the advance or retard opening in a state of discharging the fluid Locking opening, provided at a position adjacent to the phase control area. The advance opening and the retard opening are provided with a flow rate limiting unit which limits fluid flow in an opening of the advance opening and the retard opening to which the fluid is supplied when the slider is set in the lock area.

According to this configuration, in a case where the slider is set in the lock area, for example, the lock area of the valve unit is formed at a position adjacent to the advance range as an example of the phase control area, the fluid of the advance chamber in a situation in which the fluid is discharged from the lock recess portion out of the lock hole. Specifically, in this configuration, a flow rate control section restricts the flow of the fluid flowing to the advance opening, and therefore, an increase in the relative displacement speed in the advance direction can be suppressed, and a sufficient time for discharging fluid from the lock opening from the lock recess section can occur the suppression of the speed of the relative displacement can be ensured. As a result, a fluid pressure in the locking recess portion can be sufficiently lowered until the relative rotational phase reaches the intermediate phase, and further, the relative speed between the locking member and the locking recess portion can be lowered. When the relative rotational phase reaches the intermediate phase, the locking member can be reliably brought into engagement with the locking recess portion.

Accordingly, the valve timing is designed to allow a reliable transition of the locking mechanism to the locked state when using the single slider.

According to another configuration, the flow rate limiting unit may cause a passage area of the advance opening or the retard opening to be smaller than a passage area of the lock opening when the slider is set in the lock area.

According to this configuration, the flow rate limiting unit decreases the passage area of the advance opening or the retard opening and relatively increases the passage area of the lock opening. In other words, an increase in the speed of the relative displacement in the advance direction or the retard direction can be suppressed, the fluid can be active from the Locking can be omitted, and a transition of the locking mechanism to the locked state can be reliably obtained.

In another configuration, a boss body formed on an inner surface of at least one of the advance opening and the retard opening may constitute the flow rate restriction unit.

In this configuration, both the advance opening and the retard opening are formed as through holes over the connecting bolt and the sleeve. Accordingly, the protrusion body is formed as the flow rate limiting unit on at least the inner circumference of the through hole formed in the connecting bolt or the inner circumference of the through hole formed in the sleeve. With this configuration, an increase in the flow rate of the fluid supplied to the advance chamber or the retard chamber in a case where the slider is brought into a lock phase can be suppressed, and an increase in the speed of relative rotational phase shift can be suppressed ,

According to another configuration, a bridge body connecting surfaces opposed to each other on an inner surface of at least one of the advance opening and the retard opening may constitute the flow rate limiting unit.

In this configuration, both the advance opening and the retard opening are formed as through holes over the connecting bolt and the sleeve. Accordingly, the bridge body is provided as the flow rate limiting unit on at least the inner circumference of the through hole formed in the connecting bolt or the inner circumference of the through hole formed in the sleeve. With this configuration, an increase in the flow rate of the fluid supplied to the advance chamber or the retard chamber when the slider is brought into the lock phase can be suppressed, and an increase in the speed of the relative rotational phase shift can be suppressed.

In another configuration, a latch outlet flow channel for venting the fluid from the latch opening may differ from a phase control outlet flow channel for venting the fluid from the advance or retard opening.

According to this configuration, the fluid discharged from the lock hole can be discharged without flowing to the phase control outlet flow channel when the slider is set in the lock area. Accordingly, the fluid is rapidly discharged from the lock port without being obstructed by the fluid discharged from the advance opening or the retard opening, and the transition to the locked state is ensured.

In another configuration, the locking portion may be disposed in both end portions of the operating portion of the slider at a position such that the phase control portion is interposed therebetween.

According to this configuration, transition to the locked state can be obtained while shifting the relative rotational phase in the advance direction by adjusting the slider in an end portion of the operation range, and transition to the locked state can be obtained while the relative rotational phase is shifted in the retard direction by the slider is set in the other end. Accordingly, regardless of whether the relative rotational phase on the advance side or the retard side of the intermediate phase in which the lock mechanism transitions to the locked state, a transition to the locked state can be obtained only by an end portion adjustment in the spool operation region.

list of figures

• 1 eine Querschnittsansicht einer Ventilzeitsteuerung;
• 2 eine Querschnittsansicht entlang einer Linie II-II in 1;
• 3 ein Diagramm, das die Beziehung zwischen Bereichen, in denen ein Schieber eingestellt ist, und einer Zufuhr und einem Auslassen eines Arbeitsfluids angibt;
• 4 eine Querschnittsansicht einer Ventileinheit mit dem Schieber in einem ersten Verriegelungsbereich;
• 5 eine Querschnittsansicht der Ventileinheit mit dem Schieber in einem Frühverstellbereich;
• 6 eine Querschnittsansicht der Ventileinheit mit dem Schieber in einem Haltebereich;
• 7 eine Querschnittsansicht der Ventileinheit mit dem Schieber in einem Spätverstellbereich;
• 8 eine Querschnittsansicht der Ventileinheit mit dem Schieber in einem zweiten Verriegelungsbereich;
• 9 eine perspektivische Explosionsansicht der Ventileinheit;
• 10 ein Diagramm, das die Formen einer Frühverstellöffnung und einer Spätverstellöffnung zeigt; und
• 11 ein Diagramm, das die Formen von jeweiligen Öffnungen gemäß anderen Ausführungsformen (a) bis (c) angibt.

The foregoing and additional features and characteristics of this disclosure will become apparent from the following detailed description with reference to the accompanying drawings. Show it:

• 1 a cross-sectional view of a valve timing;
• 2 a cross-sectional view along a line II-II in 1 ;
• 3 a diagram indicating the relationship between areas in which a slider is set, and a supply and a discharge of a working fluid;
• 4 a cross-sectional view of a valve unit with the slider in a first locking portion;
• 5 a cross-sectional view of the valve unit with the slider in a Frühverstellbereich;
• 6 a cross-sectional view of the valve unit with the slider in a holding area;
• 7 a cross-sectional view of the valve unit with the slider in a retard adjustment;
• 8th a cross-sectional view of the valve unit with the slider in a second locking portion;
• 9 an exploded perspective view of the valve unit;
• 10 a diagram showing the shapes of a Frühverstellöffnung and a retard opening; and
• 11 a diagram indicating the shapes of respective openings according to other embodiments (a) to (c).

DETAILED DESCRIPTION

An embodiment disclosed herein will be described below with reference to the accompanying drawings.

[Basic configuration] As in 1 and 2 As shown, a valve timing controller A is configured to include an outer rotor 20 as a drive-side rotary member, an inner rotor 30 as a driven-side rotary member and a solenoid control valve V comprising a working fluid as a fluid.

The valve timing A is coaxial with a rotation axis X an intake camshaft 5 for setting an opening / closing timing of the intake camshaft 5 an internal combustion engine E (an example of an internal combustion engine) of a vehicle (eg car ) intended.

The inner rotor 30 (An example of the driven-side rotary member) is coaxial with the rotation axis X the intake camshaft 5 arranged. The inner rotor 30 rotates integrally with the intake camshaft 5 by passing through a connecting bolt 40 with the intake camshaft 5 connected is. The outer rotor 20 contains the inner rotor 30 , The outer rotor 20 (An example of the drive-side rotary member) is coaxial with the rotation axis X arranged and rotates synchronously with a crankshaft 1 of the internal combustion engine E. Based on this configuration, the outer rotor 20 and the inner rotor 30 rotatable relative to each other.

The valve timing A is with the locking mechanism L provided the relative rotational phase between the outer rotor 20 and the inner rotor 30 in an in 2 shown intermediate locking phase M holds. The interlock phase M is an opening / closing timing, which is suitable for starting the internal combustion engine e , A controller for a transition to the interlock phase M is during a control of a stop of the internal combustion engine e carried out.

A magneto-solenoid Va and a valve unit Vb , which are carried by the internal combustion engine E, form the solenoid control valve V , The valve unit Vb is with the connecting bolt 40 and a slider 55 in an inner room 40R of the connecting bolt 40 is included, provided.

The solenoid solenoid Va is provided with a solenoid portion 50 and a pestle 51 relating to the solenoid section 50 can withdraw. In the valve unit Vb is the slide 55 controlling a supply and a discharge of the working fluid (an example of the fluid) coaxial with the rotation axis X arranged, and respective positional relationships are set such that a projecting end of the plunger 51 against an outer end of the slider 55 encounters.

The solenoid control valve V presses the slide 55 by adjusting the extent to which the plunger 51 protrudes, under the control of electrical power, the solenoid portion 50 is supplied. Based on this operation, the flow of the working fluid is controlled, an opening / closing timing of an intake valve 5V is set, and there is a switching between a transition of the locking mechanism L to a locked state and a release of the locked state. The configuration of the solenoid control valve V and working fluid control modes will be described below.

[Internal combustion engine and valve timing] As in 1 shown, the internal combustion engine E is designed as a four-stroke engine in which a piston 3 in a cylinder bore of a cylinder block 2 is received at an upper position and the piston 3 and the crankshaft 1 through a connecting rod 4 are connected. In the upper section of the internal combustion engine e are the intake camshaft 5 , which is an opening / closing of the inlet valve 5V and an exhaust camshaft (not shown).

A feed flow channel 8th containing a working fluid from a hydraulic pump P , which is driven by the internal combustion engine E, supplies, is in an internal combustion engine component 10 that the intake camshaft 5 rotatably supports, trained. The hydraulic pump P Leads a lubricating oil in an oil pan 9 the internal combustion engine e is stored, the valve unit Vb as the working fluid (an example of the fluid) via the supply flow passage 8th to.

A timing chain 7 is about a starting wheel 6 on the crankshaft 1 the internal combustion engine E is formed, and a steering wheel 21 S of the outer rotor 20 wound. As a result, the outer rotor rotates 20 synchronous with the crankshaft 1 , It should be noted that a gear is also provided at a front end of the exhaust camshaft on the exhaust side and the timing chain 7 is also wrapped around this gear.

As in 2 As shown, the outer rotor rotates 20 by a driving force from the crankshaft 1 in a driving direction S , The direction in which the inner rotor 30 with respect to the outer rotor 20 in the same direction as the driving direction S is referred to as an advance direction Sa, and the direction opposite to the advance direction Sat. is referred to as a retardation direction Sb. In the valve timing A is the relationship between the crankshaft 1 and the intake camshaft 5 is set such that an intake compression ratio increases with an increase in displacement when the relative rotational phase is shifted in the advance direction Sa, and the intake compression ratio is decreased with an increase in displacement when the relative rotational phase is shifted in the retard direction Sb.

It should be noted that the valve timing A in the exhaust camshaft or in both the intake camshaft 5 may also be provided in the exhaust camshaft, although in this embodiment, in the intake camshaft 5 provided valve timing A is described.

[Outer rotor and inner rotor] As in 1 shown, the outer rotor 20 an outer rotor main body 21 , a front panel 22 and a back plate 23 By fastening several fastening bolts 24 are integrated on. The steering wheel 21S is on the outer periphery of the outer rotor main body 21 educated.

As in 2 shown are several protruding sections 21T which protrude radially inwardly integrally in the outer rotor main body 21 educated. The inner rotor 30 has a cylindrical inner rotor main body 31 who is in close contact with the preceding section 21T the outer rotor main body 21 stands, and several blade sections 32 from the outer circumference of the inner rotor main body 31 projecting radially outward and in contact with the inner circumference of the outer rotor main body 21 are on.

The outer rotor 20 takes in this way the inner rotor 30 on, and several fluid pressure chambers C are on the outer peripheral side of the inner rotor main body 31 and at intermediate positions between the projecting portions 21 T , which are adjacent in the direction of rotation formed. An advance chamber Ca and a retardation chamber cb are formed so that they are in the from the blade section 32 subdivided fluid pressure chamber C are separated. Further, the inner rotor main body is 31 with an advance flow channel 33 that with the Frühverstellkammer Ca is in communication, and a retard flow channel 34 , with the retardation chamber cb communicates.

As in 1 and 2 shown, the locking mechanism L each a locking member 25 which is supported so as to be one of two of the protruding portions 21T the outer rotor 20 can retract a locking spring 26 that the locking component 25 for projecting, and a locking recess portion 27 on the outer periphery of the inner rotor main body 31 is trained on. A lock control flow channel 35 that with the locking recess portion 27 is in the inner rotor main body 31 educated.

In the locking mechanism L serve the two locking components 25 for limiting the relative rotational phase to the interlock phase M by passing through the biasing force of the locking spring 26 simultaneously engaged with the corresponding locking recess portions 27 to be brought. By supplying the working fluid to the lock control flow channel 35 in this locked state, the locking member 25 against the biasing force of the locking spring 26 from the locking recess portion 27 be released, and the locked state can be released. In contrast, when the working fluid from the lock control flow channel 35 is omitted, the locking member 25 by means of the biasing force of the locking spring 26 in engagement with the locking recess portion 27 can be brought, and it can be moved to the locked state.

It should be noted that the locking mechanism L may be formed such that a single locking member 25 with a corresponding single locking recess portion 27 is engaged. In addition to this, the locking mechanism L be formed so that the locking member 25 is guided, so that it is along a direction along the axis of rotation X emotional.

[Connecting pin] As in 1 . 4 and 9 are shown in the connecting bolt 40 a bolt main body 41 having a tubular shape and a bolt head portion 42 in an outer end portion (left side in FIG 4 ) integrally formed. The inner space 40R who the connecting bolts 40 in the direction along the axis of rotation X penetrates, is in the connecting bolt 40 formed, and a male threaded portion 41S is on the outer periphery of the inner end portion (right side in FIG 4 ) of the bolt main body 41 educated.

As in 1 shown is the intake camshaft 5 with a wave interior 5R around the axis of rotation X provided, and a female threaded portion 5S is on the inner circumference of the wave interior 5R educated. The wave interior 5R communicates with the supply flow channel 8th in communication, and the working fluid is supplied from the hydraulic pump P.

In this configuration, the bolt main body becomes 41 in the inner rotor 30 introduced, and the male thread section 41S of the bolt main body 41 is with the female thread section 5S the intake camshaft 5 screwed. Then the inner rotor 30 as a result of rotation of the bolt head portion 42 at the intake camshaft 5 attached. As a result, the inner rotor becomes 30 at the intake camshaft 5 attached and fixed, and the wave interior 5R and the inner space 40R (More specifically, the space inside a fluid supply tube 54 ) of the connecting bolt 40 communicate with each other.

A boundary wall 44 pointing in one direction to the axis of rotation X protrudes, is at the inner end side (right side in 4 ) of the inner peripheral surface of the inner space 40R of the connecting bolt 40 in the direction along the axis of rotation X educated. As in 4 and 9 Shown are a plurality of (four) groove-shaped outlet flow channels Da along the axis of rotation X in the region reaching the extreme end from the intermediate position, in the inner circumference of the connecting bolt 40 educated. Several (four) outlet holes Db connecting the connecting bolt 40 penetrate in the radial direction, are on the inner end side of the connecting bolt 40 educated.

[Valve unit] As in 1 . 4 and 9 shown, the valve unit Vb has the connecting bolt 40 , a sleeve 53 in close contact with the inner peripheral surface of the bolt main body 41 is fitted, the fluid supply pipe 54 that in the inner space 40R coaxial with the axis of rotation X is included, and the slider 55 which is arranged so that it is in the direction along the axis of rotation X in a state in which it passes through the inner peripheral surface of the sleeve 53 and the outer peripheral surface of a pipe section 54T the fluid supply pipe 54 is guided, can move on.

The valve unit Vb is with a slider spring 56 that the slider 55 biased in a Vorstehrichtung, a check valve CV , an oil filter F and a fastening ring 61 Provided.

As in 9 shown is the check valve CV with an opening plate 57 and a valve plate 58 provided, which are formed of metal plates with the same outer diameter. In the opening plate 57 are several openings 57a in an annular area around the axis of rotation X drilled. The valve plate 58 is formed so that it has an annular valve portion 58a having the opening during a decrease in pressure 57a the orifice plate 57 blocked.

The valve plate 58 consists of a spring material. When a working fluid is supplied, the valve portion becomes 58a from the opening 57a the orifice plate 57 separated, and thus a working fluid supply is obtained. When the pressure of the working fluid on the upstream side of the check valve CV lower than the pressure on the downstream side of the check valve CV is in a state in which the valve section 58a the valve plate 58 the opening 57a the orifice plate 57 overlaps, blocking is performed, and a reverse flow of the working fluid is then prevented.

The oil filter F is designed to work with a filter body 59 that has the same outside diameter as the orifice plate 57 and the valve plate 58 has, and a support body 60 that the filter body 59 in a state in which a fluid circulation is possible, carries, is provided.

In this configuration, the filter body 59 , the supporting body 60 , the opening plate 57 and the valve plate 58 concerning the inner space 40R of the connecting bolt 40 along with the fluid supply tube 54 , the sleeve 53 , the slider spring 56 and the slider 55 inserted, and the mounting ring 61 is at the outer end part of the connecting bolt 40 fitted and attached. The valve unit Vb is assembled in this way.

In the valve unit assembled in this way Vb are a Frühverstell (passage) opening PA passing through the advance flow channel 33 with the advance chamber Ca communicating, a late adjustment (orifice) opening PB passing over the retard flow channel 34 with the retardation chamber cb communicates, and a locking (through) opening PL via the lock control flow channel 35 with the locking recess portion 27 communicates, formed as through holes, the valve unit Vb over the bolt main body 41 and the sleeve 53 penetrate in the radial direction.

The advance opening PA has a Frühverstellverbindungsbohrung 41a in the bolt main body 41 is formed, and a Frühverstellöffnung 53a that in the sleeve 53 is trained on. The late adjustment opening PB has a late adjustment connecting bore 41b in the bolt main body 41 is formed, and a late adjustment 53b that in the sleeve 53 is trained on. The locking opening PL has a locking connection bore 41c in the bolt main body 41 is formed, and a locking opening 53c that in the sleeve 53 is trained on.

The plurality of (four) groove-shaped outlet flow channels Da that supply the working fluid to the outer end side (left side in FIG 4 ) of the bolt main body 41 are omit in the inner circumference of the bolt main body 41 educated. The plurality of outlet holes Db penetrate the inner end side (right side in FIG 4 ) of the bolt main body 41 ,

It should be noted that the outlet flow passage Da serves as a lock outlet flow passage, which supplies the working fluid in a case where the spool 55 in a first locking area W1 is, from the locking hole PL discharges, and serves as a Phasensteuerungsauslassströmungskanal, the working fluid in a case where the slide 55 in a second locking area W5 is, from the Frühverstellöffnung PA omits. The outlet hole db serves as a Phasensteuerungsauslassströmungskanal, the working fluid in a case where the slide 55 in the first locking area W1 and a Frühverstellbereich W2 is, from the late adjustment PB omits. The working fluid flow is below in conjunction with the areas where the slide 55 is set described.

[Valve unit: sleeve] As in 1 . 4 and 9 shown points the sleeve 53 a tubular shape around the axis of rotation X on, and an end section wall 53W is through the inner end side (right side in 4 ) of the sleeve 53 formed by pulling or the like in a position orthogonal to the axis of rotation X is brought.

The sleeve 53 is with several (four) Frühverstellöffnungen 53a , several (four) retards 53b and a plurality of (four) locking openings 53c Provided. Furthermore, several (four) first outlet openings 53d at the intermediate part of the sleeve 53 formed, and a plurality of (four) second outlet openings 53e are on the inner end side of the sleeve 53 educated.

The early adjustment openings 53a , the retards 53b and the locking holes 53c are in the direction along the axis of rotation X at four locations in the circumferential direction about the axis of rotation X arranged side by side. The multiple (four) first outlet openings 53d and the multiple (four) second outlet openings 53e are in the direction along the axis of rotation X formed with different phases.

As in 9 shown is a pair of engagement protrusions 53T at outer end positions of the sleeve 53 educated. The sleeve 53 is due to the engagement projection 53T with the engagement recessed portion (not shown) of the opening part of the bolt main body 41 is engaged so that they are relative to the bolt main body 41 can not turn.

As described above, the sleeve is 53 through the bolt main body 41 held so that it is not rotatable. As a result, as in 4 shown to maintain a state in which the Frühverstellöffnung 53a , the late adjustment opening 53b and the locking hole 53c each with the Frühverstellverbindungsbohrung 41a , the late adjustment joint hole 41b and the lock connection bore 41c stay in contact. In addition to this are the first outlet opening 53d and the outlet flow passage Da for communicating with each other to form a lock outlet flow passage, and the second outlet port 53e and the outlet hole Db communicate with each other to form a phase control outlet flow channel. As a result, as described above, the advance opening becomes PA , the late adjustment opening PB and the locking hole PL educated. In particular, the exhaust hole Db is provided with an exhaust passage hole 5d that in the intake camshaft 5 is trained, in conjunction.

[Valve Unit: Fluid Supply Pipe] As in 4 and 9 are shown in the fluid supply tube 54 a base end section 54S in the inner room 40R fitted, and the line section 54T having a smaller diameter than the base end portion 54S has, integrally formed. Several first feed openings 54a are at positions near the base end section 54S in the outer periphery of the distal end portion of the pipe section 54T educated. As a result, several second feed openings 54b formed on the outer end side.

The several first feed openings 54a are wide in the circumferential direction and have a slot shape extending in the direction along the axis of rotation X extends. Four intermediate hole sections 55c that in the slider 55 are formed at positions corresponding to these, have a circular shape. With this configuration, a working fluid can reliably from the line section 54T the intermediate hole section 55c be supplied.

The second feed opening 54b has a substantially rectangular shape. Several end section hole sections 55d that in the slider 55 are formed at positions that correspond to it, are circular. With this configuration, a working fluid can reliably from the line section 54T the end portion hole portion 55d be supplied.

[Valve unit: slide and slider spring] As in 4 and 9 shown, points the slider 55 a tubular slider main body 55a on, wherein a contact surface is formed on the outer end side and four web portions 55b are formed on the outer periphery thereof. An inner flow channel is in the slide 55 educated. The multiple intermediate hole sections 55c which communicate with the inner flow channel are at intermediate positions between the pair of land portions 55b on the inner end side in the direction along the rotation axis X educated. The end portion hole portion 55d which communicates with the inner flow passage is at an intermediate position between the pair of land portions 55b on the outer end side in the direction along the rotation axis X educated.

The slider spring 56 is a compression screw slide spring and between the web section 55b on the inner end side and the end portion wall 53W the sleeve 53 arranged.

[Operating modes] For this valve timing control A no pressure force acts on the plunger 51 on the slider 55 when the solenoid section 50 the solenoid solenoid Va no electric power is supplied. As in 4 shown, in this state, the position of the slider 55 by the biasing force of the slider spring 56 maintained at the position where the web section 55b , outside the slider spring 56 is positioned against the mounting ring 61 encounters.

The position of the slider 55 , in the 4 is shown, is the outer end position of the first locking portion W1 , As in 3 can be shown by increasing an electrical power supplied to the solenoid section 50 is fed, in turn, an operation to the Frühverstellbereich W2 , a holding area W3 , a retardation range W4 and the second lock area W5 be carried out, starting from the first locking area W1 as a reference point. In other words, an operation may be performed to one of the five areas by the electric power supplied to the solenoid portion 50 the solenoid solenoid Va is supplied is set.

It should be noted that the slider 55 in a state where the solenoid portion 50 no electric power is supplied to the outer end position of the first locking portion W1 is held as in 4 is shown. In addition, the slider will 55 by maximizing the solenoid portion 50 supplied electrical power as in 8th shown at the outer end of the second locking portion W5 set.

Of the several areas are the Frühverstellbereich W2 and the retardation range W4 Phase control areas, and the first lock area W1 and the second lock area W5 are locking areas.

At the valve unit Vb is a transition of the locking mechanism L to the locked state at a time when the relative rotational phase is the interlock phase M achieved, in a case where the slider 55 either on the first locking area W1 or on the second lock area W5 is set, possible.

[Operation Mode: First Lock Area] As in 4 is shown in a case where the slider 55 in the first locking area W1 is set, the working fluid from the hydraulic pump P the Frühverstellkammer Ca over the intermediate hole section 55c of the slider 55 , the advance opening PA and the advance flow channel 33 fed. At the same time, the working fluid flows in the retard chamber cb to the retard flow channel 34 , the late adjustment opening PB , the second outlet opening 53e and the outlet hole db and is drained to the outside.

In the first locking area W1 the working fluid flows in the locking recess portion 27 to the lock control flow channel 35 , the locking hole PL , the first outlet opening 53d and the outlet flow channel Da and is discharged to the outside.

In other words, in the first lock area W1 is the flow channel through which the working fluid from the locking hole PL over the first outlet opening 53d to the outlet flow channel There flows, a Verriegelungsauslassströmungskanal. The flow channel through which the working fluid from the retard opening PB over the second outlet opening 53e to the outlet hole db flows is a Phasensteuerungsauslassströmungskanal. There the locking outlet flow channel and the Phasensteuerungsauslassströmungskanal are different, the disadvantage that the working fluid from the retard cb is omitted, the flow of working fluid coming out of the Locking recess portion 27 the locking mechanism L is omitted, obstructed, avoided. As a result, the pressure of the locking recess portion decreases 27 quickly, and a transition to the locked state is facilitated.

As a result, the relative rotational phase is shifted in the advance direction Sa, and the lock member 25 is engaged with the locking recess portion 27 and a transition to the locked state occurs at a time when the relative rotational phase is the interlock phase M reached. It should be noted that the relative rotational phase in the interlock phase M is held when the locked state has already been reached.

[Mode: advance range] As in 5 is shown in a case where the slider 55 in the Frühverstellbereich W2 is set, the working fluid from the hydraulic pump P the advance chamber Ca over the intermediate hole section 55c of the slider 55 , the advance opening PA and the advance flow channel 33 as in the case where the slider 55 in the first locking area W1 is set, supplied. At the same time, the working fluid flows in the retard chamber cb to the retard flow channel 34 , the late adjustment opening PB , the second outlet opening 53e and the exhaust hole Db and becomes out of the exhaust passage hole 5d drained to the outside.

In the Frühverstellbereich W2 becomes the working fluid from the hydraulic pump P the locking recess portion 27 over the end portion hole portion 55d of the slider 55 , the locking hole PL and the lock control flow channel 35 fed. As a result, the lock member becomes 25 from the locking recess portion 27 withdrawn, the locking mechanism L is set in the unlocked state, and the relative rotational phase is adjusted in the advance direction Sa.

[Operation Mode: Hold] As in 6 be shown in a case where the slider 55 in the holding area W3 is set, the Frühverstellöffnung PA and the late adjustment opening PB through the bridge section 55b of the slider 55 closed, and it is achieved a state in which no working fluid of the advance chamber Ca and the retardation chamber cb is supplied. In the holding area W3 becomes the hydraulic fluid from the hydraulic pump P the locking recess portion 27 over the end portion hole portion 55d of the slider 55 , the locking hole PL and the lock control flow channel 35 supplied, and the locking member 25 becomes out of the locking recess portion 27 retracted and the unlocked state is maintained.

Accordingly, in the holding area W3 held the relative rotational phase, without the relative rotational phase is shifted.

[Operating mode: retardation range] As in 7 is shown in a case where the slider 55 in the retardation range W4 is set, the working fluid from the hydraulic pump P the retardation chamber cb over the intermediate hole section 55c of the slider 55 , the late adjustment opening PB and the retard flow channel 34 fed. At the same time, the working fluid flows in the advance chamber Ca to the advance flow channel 33 , the Frühverstellöffnung PA , the first outlet opening 53d and the outlet flow channel Da and is discharged to the outside.

In the retardation range W4 The working fluid from the hydraulic pump P becomes the locking recess portion 27 over the end portion hole portion 55d of the slider 55 , the locking hole PL and the lock control flow channel 35 fed. As a result, the lock member becomes 25 from the locking recess portion 27 withdrawn, the locking mechanism L is set in the unlocked state, and the relative rotational phase becomes in the retard direction sb postponed.

[Operating Mode: Second Lock Area] As in 8th is shown in a case where the slider 55 in the second locking area W5 is set, the working fluid from the hydraulic pump P the retardation chamber cb over the intermediate hole section 55c of the slider 55 , the late adjustment opening PB and the retard flow channel 34 fed. At the same time, the working fluid flows in the advance chamber Ca to the advance flow channel 33 , the Frühverstellöffnung PA , the first outlet opening 53d and the outlet flow channel There and is drained to the outside.

In the second locking area W5 the working fluid flows in the locking recess portion 27 from the lock control flow channel 35 and the locking hole PL to the inner space of the sleeve 53 and is discharged to the outside by moving from the outer end (left end portion in FIG 8th ) of the slider 55 through the inner circumference of the mounting ring 61 passes.

In other words, in the second lock area W5 the flow channel through which the working fluid from the locking opening PL to the inner space of the sleeve 53 and to the outer end of the slider 55 flows, a Verriegelungsauslassströmungskanal. The flow channel through which the working fluid from the Frühverstellöffnung PA over the first outlet opening 53d to the outlet flow passage Da is a phase control outlet flow passage. Since the lock outlet flow passage and the phase control outlet flow passage are different, there can be a disadvantage that the working fluid coming out of the advance chamber Ca is omitted, the flow of the working fluid, which from the locking recess portion 27 the locking mechanism L is omitted, obstructed, avoided. As a result, the pressure of the locking recess portion decreases 27 quickly, and a transition to the locked state is facilitated.

As a result, the relative rotational phase is shifted in the retard direction Sb, and the locking member 25 becomes with the locking recess portion 27 is engaged and a transition to the locked state occurs at a time when the relative rotational phase is the interlock phase M reached. It should be noted that the relative rotational phase in a case where the locked state has already been reached, in the interlock phase M is maintained.

[Structures of the advance opening and the retard opening] Even in a case where the slider 55 either in the first locking area W1 or in the second locking area W5 is set, as described above, reaches the locking mechanism L the locked state at a time when the relative rotational phase as a result of the shift, the Zwischenverriegelungsphase M reached.

In the valve timing A is a rectangular projection body 65 at the Öffnungsinnenumfängen the Frühverstellöffnung 53a that the Frühverstelldurchgangsöffnung PA forms, and the late adjustment 53b that the retard passage opening PB is formed as a flow rate limiting unit which suppresses an increase in the displacement speed of the relative rotational phase even when the slider 55 either to the first locking area W1 or to the second locking area W5 is pressed.

As in 9 and 10 are shown, two protrusion bodies 65 each in the Frühverstellöffnung 53a and the late adjustment opening 53b educated. The protrusion bodies 65 are from the opening edges with a predetermined width based on the half positions of the opening edges in the operating direction of the slider 55 (Direction along the axis of rotation X ) in front.

It should be noted that the protrusion body 65 at any of the inner surface of the Frühverstellverbindungsbohrung 41a in the bolt main body 41 as the Frühverstellöffnung PA is formed, and the inner surface of the Spätverstellverbindungsbohrung 41b in the bolt main body 41 as the retard opening PB is formed, may be formed.

With this configuration, in a case where the slider 55 for example, from the Frühverstellbereich W2 to the first locking area W1 is actuated, not only an increase in the flow rate of the working fluid, that of the Frühverstellöffnung PA to the advance chamber Ca flows, be suppressed by an extension of the flow channel cross-section of the Frühverstellöffnung PA is suppressed, but it may also be the flow rate of the working fluid, that of the Frühverstellkammer Ca is reduced by a pressure loss due to the boss body 65 is generated and the flow of the working fluid is disturbed.

Similarly, for example, in a case where the slider 55 from the retardation range W4 to the second lock area W5 is actuated, not only an increase in the flow rate of the working fluid, that of the retardation PB to the retardation chamber cb flows, be suppressed by an extension of the flow channel cross-section of the retard opening PB is suppressed, but it may also be the flow rate of the working fluid, that of the retard cb is supplied reduced by a decrease in pressure due to the boss body 65 is generated and the flow of the working fluid is disturbed.

Accordingly, in a case where the slider 55 either on the first locking area W1 or on the second lock area W5 is set, the displacement speed of the relative rotational phase can be reduced, and it can be a sufficient time for discharging the working fluid from the locking recess portion 27 be guaranteed. As a result, the lock member becomes 25 with the locking recess portion 27 is engaged, and a transition to the locked state becomes reliable at a time when the relative rotational phase is the interlock phase M achieved, performed.

[Effect of the Embodiment] By Using the Simple Configuration in Which the Projecting Body 65 as described above at each of the Frühverstellöffnung PA and the late adjustment opening PB is formed, an increase in the speed at which the relative rotational phase changes, even in a case where the slider 55 either in the first locking area W1 or in the second locking area W5 is set to be suppressed while the only one pusher 55 is used. As a result, a transition of the locking mechanism L to the locked state at a time when the relative rotational phase is the interlock phase M achieved, be carried out reliably.

Even in a case where the slider 55 either on the first locking area W1 or on the second lock area W5 is set, the working fluid from the locking hole PL discharged from the Verriegelungsauslassströmungskanal, and the working fluid from the Frühverstellöffnung PA or the late adjustment opening PB is discharged is discharged from the Phasensteuerungsauslassströmungskanal, which is a different flow channel than the Verriegelungsauslassströmungskanal. Accordingly, the working fluid discharged from the lock outlet flow passage is discharged without hindrance, the pressure of the lock recess portion 27 is reliably reduced, and a transition of the locking mechanism L to the locked state is quickly performed in a short time.

• (a) Wie in Spalte (a) in 11 gezeigt, ist der Vorsprungskörper 65, der als die Strömungsratenbegrenzungseinheit ausgebildet ist, nicht auf ein Rechteck beschränkt, und der Vorsprungskörper 65 kann beispielsweise eine gebogene vorspringende Form oder eine Dreiecksform aufweisen. Wenngleich davon ausgegangen wird, dass die Vorsprungskörper 65 an der Hülse 53 ausgebildet sind, können die Vorsprungskörper 65 an einer oder beiden von der Innenumfangsfläche der Frühverstellverbindungsbohrung 41a der Frühverstellöffnung PA und der Innenumfangsfläche der Spätverstellverbindungsbohrung 41b der Spätverstellöffnung PB ausgebildet sein.
• (b) Wie in Spalte (b) in 11 gezeigt, kann der als die Strömungsratenbegrenzungseinheit ausgebildete Vorsprungskörper 65 ein einziges Stück sein und einen bogenförmigen vorstehenden Teil oder eine Dreiecksform aufweisen. Wenngleich davon ausgegangen wird, dass die Vorsprungskörper 65 an der Hülse 53 ausgebildet sind, können die Vorsprungskörper 65 an einer oder beiden von der Innenumfangsfläche der Frühverstellverbindungsbohrung 41a der Frühverstellöffnung PA und der Innenumfangsfläche der Spätverstellverbindungsbohrung 41b der Spätverstellöffnung PB ausgebildet sein.
• (c) Wie in Spalte (c) in 11 gezeigt, kann ein Brückenkörper 66, der als eine Strömungsratenbegrenzungseinheit ausgebildet ist, so ausgebildet sein, dass er Flächen, die einander entweder bei der Frühverstellöffnung 53a oder bei der Spätverstellöffnung 53b gegenüberliegen, verbindet. Ferner ist der Brückenkörper 66 nicht auf eine konstante Breite beschränkt. Der Brückenkörper 66 kann einen schmalen Mittelteil aufweisen, wie in Spalte (c) gezeigt. Wenngleich davon ausgegangen wird, dass der Brückenkörper 66 an der Hülse 53 ausgebildet ist, kann der Brückenkörper 66 an einer oder beiden von der Innenumfangsfläche der Frühverstellverbindungsbohrung 41a der Frühverstellöffnung PA und der Innenumfangsfläche der Spätverstellverbindungsbohrung 41b der Spätverstellöffnung PB ausgebildet sein.

Other Embodiments The present disclosure may be constructed as follows in addition to the above-described embodiment (the same reference numerals are used as in the embodiment).

• (a) As in column (a) in 11 is shown, the protrusion body 65 formed as the flow rate limiting unit, not limited to a rectangle, and the protrusion body 65 may for example have a curved projecting shape or a triangular shape. Although it is assumed that the protrusion body 65 on the sleeve 53 are formed, the projection body 65 at one or both of the inner peripheral surface of the advance adjusting bore 41a the Frühverstellöffnung PA and the inner peripheral surface of the retard connection bore 41b the retard opening PB be formed.
• (b) As in column (b) in 11 1, the protrusion body formed as the flow rate limiting unit may be shown 65 be a single piece and have an arcuate protruding part or a triangular shape. Although it is assumed that the protrusion body 65 on the sleeve 53 are formed, the projection body 65 at one or both of the inner peripheral surface of the advance adjusting bore 41a the Frühverstellöffnung PA and the inner peripheral surface of the retard connection bore 41b the late adjustment opening PB be educated.
• (c) As in column (c) in 11 shown, can be a bridge body 66 formed as a flow rate limiting unit, be configured to have surfaces facing each other either at the advance opening 53a or at the late adjustment opening 53b opposite, connects. Further, the bridge body 66 not limited to a constant width. The bridge body 66 may have a narrow central part as shown in column (c). Although it is assumed that the bridge body 66 on the sleeve 53 is formed, the bridge body 66 at one or both of the inner peripheral surface of the advance adjusting bore 41a the Frühverstellöffnung PA and the inner peripheral surface of the retard connection bore 41b the late adjustment opening PB be educated.

[Industrial Applicability] The present disclosure may be applied to a valve timing control of the relative rotational phase between a driving-side rotating member and a driven-side rotating member by means of a fluid pressure and holding the relative rotational phase in a predetermined phase by means of a locking mechanism.

The principles, preferred embodiment and operation of the present invention have been described above. However, the invention should not be limited to the particular embodiments described. The embodiments are merely illustrative and not limiting. Variations and changes may be made and equivalents may be used without departing from the scope of the present invention. Accordingly, it is intended that all such variations, changes, and equivalents fall within the scope of the present invention, which is defined by the following claims.

It is explicitly pointed out that all features disclosed in the description and / or the claims are considered separate and independent of each other for the purpose of original disclosure as well as for the purpose of limiting the claimed invention independently of the feature combinations in the embodiments and / or the claims should. It is explicitly stated that all range indications or indications of groups of units disclose every possible intermediate value or subgroup of units for the purpose of the original disclosure as well as for the purpose of restricting the claimed invention, in particular also as the limit of a range indication.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• JP 2015078635A [0002]

Claims (6)

Valve timing control (A) with: a driving-side rotating member (20) that rotates in synchronism with a crankshaft (1) of an internal combustion engine (E); a driven side rotating member (30) coaxial with a rotation axis (X) of the driving side rotating member and integrally rotating with a cam shaft (5) for opening / closing a valve; an advance chamber (Ca) and a retard chamber (Cb) formed between the drive-side rotation member and the output-side rotation member; a lock mechanism (L) capable of making a transition to a locked state in an intermediate phase, which is an intermediate phase of relative rotational phases of the drive-side rotating member and the driven-side rotating member, by having a lock member (25) is provided in one of the drive-side rotary member and the driven-side rotary member and engageable with a lock recess portion (27) formed on the other of the drive-side rotary member and the driven-side rotary member; a connecting bolt (40) disposed coaxially with the rotating shaft, connecting the driven-side rotating member to the camshaft and having an inner space (40R) formed coaxially with the rotating shaft; and a valve unit (Vb) that controls supply and discharge of a fluid with respect to the advance chamber, the retard chamber, and the lock recess section; at the valve unit a sleeve (53) in contact with an inner circumference of the inner space of the connecting bolt, a slider (55) operable along the axis of rotation in the sleeve, a solenoid (Va) that adjusts a position of the slider, and an advance opening (PA) in communication with the advance chamber, a retard opening (PB) in communication with the retard chamber, and a lock opening (PL) in communication with the lock recess portion, each as through holes above the tie bolt and the sleeve are formed, wherein an operating portion of the spool includes a phase control portion that supplies the fluid to the advance or retard opening in a state of supply of the fluid to the lock opening, and a lock portion (W1, W5) that supplies the advance or retard opening fluid in a state of Extracting the fluid from the locking opening feeds, at a position adjacent to the phase control region and wherein the advance opening and the retard opening comprise a flow rate limiting unit that limits fluid flow in an opening of the advance opening and the retard opening to which fluid is supplied when the slider is set in the lock area. Valve timing control to Claim 1 wherein the flow rate limiting unit causes a passage area of the advance or retard opening to be smaller than a passage area of the lock opening when the slider is set in the lock area. Valve timing control to Claim 1 or 2 in which a projection body (65) formed on an inner surface of at least one of the advance opening and the retard opening forms the flow rate limiting unit. Valve timing control to Claim 1 or 2 in which a bridge body (66) connecting surfaces opposed to each other on an inner surface of at least one of the advance opening and the retard opening forms the flow rate restriction unit. Valve timing according to one of Claims 1 to 4 wherein a lock outlet flow passage for discharging the fluid from the lock opening is different from a phase control outlet flow passage for discharging the fluid from the advance opening or the retard opening. Valve timing according to one of Claims 1 to 5 in which the lock portion is disposed in both end portions of the operation range of the slider so that the phase control portion is interposed therebetween.

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