CN104812996A - Hydraulic camshaft adjuster with centre locking and adjustable locking play - Google Patents

Hydraulic camshaft adjuster with centre locking and adjustable locking play Download PDF

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Publication number
CN104812996A
CN104812996A CN201380036098.XA CN201380036098A CN104812996A CN 104812996 A CN104812996 A CN 104812996A CN 201380036098 A CN201380036098 A CN 201380036098A CN 104812996 A CN104812996 A CN 104812996A
Authority
CN
China
Prior art keywords
rotor
stator
locking
camshaft adjuster
locking nail
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201380036098.XA
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Chinese (zh)
Inventor
米夏埃尔·布塞
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of CN104812996A publication Critical patent/CN104812996A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34459—Locking in multiple positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34463—Locking position intermediate between most retarded and most advanced positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34466—Locking means between driving and driven members with multiple locking devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34469—Lock movement parallel to camshaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34476—Restrict range locking means

Abstract

The invention relates to a hydraulic camshaft adjuster (1), for an internal combustion engine of a motor vehicle, such as a passenger car or a lorry, having a stator (2) which can be driven by the internal combustion engine, for instance via a traction mechanism drive, and having a rotor (3) which can be connected to a camshaft, wherein the rotor (3) is fixed releasably to the stator (2) via at least one first pin-like locking pin (12) in a rotationally fixed manner in a centre position counter to a first rotational direction, wherein the locking pin (12) is designed for moving into and moving out of a first slotted guide (11) in a first axial direction which is defined by the rotational axis (13) of the stator (2) and/or of the rotor (3), wherein a second locking pin (16) can be moved in a second axial direction, which is parallel to the first axial direction but in a different direction, into a second slotted guide (28), so as to secure the rotor (3) relative to the stator (2) in a centre position counter to a second rotational direction which is in a different direction to the first rotational direction, and can be moved out of the second slotted guide (28). The invention also relates to an internal combustion engine with a camshaft and a camshaft adjuster of this type.

Description

With the hydraulic camshaft adjuster of center lock locking mechanism with the locking gap that can adjust
Technical field
The present invention relates to a kind of hydraulic camshaft adjuster of the internal-combustion engine for Motor Vehicle such as private car or lorry, this camshaft adjuster with stators and rotators, wherein, stator can such as by towing gear by internal combustion engine drive; Rotor can be connected with camshaft, wherein, rotor by least one pin-shaped locking nail in central position in anti-relative rotation (drehfest) can releasably be fixed on stator against the first sense of rotation, wherein, locking nail be designed for along the spin axis by stator and/or rotor limits first axial direction immigration or shift out the first chute.
Background technique
There is various system in principle to adjust the angle of the camshaft of internal-combustion engine.A kind of certified system based on blade chamber principle, wherein, with the blade extended diametrically rotor arrangements in the stator and the chamber existed in the stator utilizes blade to be divided into each two opposed active chambers.Active chamber can load with pressure medium by hydraulic system, and wherein, when active chamber is loaded pressure, pressure medium is extruded from opposed active chamber.The pressure-loaded ground relative stator that then rotor depends on active chamber in rotational direction adjusts.Because rotor is connected with bent axle with camshaft and stator, so have also been changed the rotation angle of the relative bent axle of camshaft at this.In order to adjust the rotation angle of camshaft, or the alternation moment be applied on camshaft can be utilized, wherein, the pressure medium coming from an active chamber is squeezed into another active chamber corresponding by the alternation moment be applied on camshaft, this process is also referred to as CTA (Camshaft TorqueActuated camshaft torque actuation), active chamber can be loaded by the conveying of outside pressure medium with pressure and pressure medium exports to pressure medium reservoir from opposed active chamber, this process is also referred to as OPA (Oil Pressure Actuated oil pressure activated).The advantage of CTA is, in order to adjust the pressure medium flow from outside conveying that camshaft only needs one minimum, the pressure medium flow of being carried from outside by pressure medium pump that OPA then requires one larger.When pressing the adjustment of CTA principle, only need the leakage loss for compensated regulator from little a lot of pressure medium flow of outside conveying, this is because the volume in order to expand or reduce active chamber, pressure medium is squeezed into another active chamber corresponding from an active chamber.In addition, can by the adjustment according to CTA principle, be issued to than with high a lot the regulating the speed of regulating the speed adjusted by OPA principle in the situation being applied to the very large alternation moment on camshaft.Usually be all be devoted to little pressure medium flow, this is because therefore hydraulic system can be implemented less generally.
By the known this camshaft adjuster of DE 10 2,006 045 005 A1, the Angle Position of the relative bent axle of camshaft can be adjusted by it.The camshaft adjuster described in the literature has hydraulic system, this hydraulic system is with the multiple-way valve for the multiple active chamber of pressure-loaded, in this hydraulic system, according to the position of valve body in multiple-way valve, active chamber is loaded differently with pressure and therefore adjusts camshaft towards the relative bent axle of different sense of rotation.In addition, be provided with the safety check of two-sided action in the valve body of multiple-way valve, it is with the closure of two load on spring, provides the flowing between active chamber to be communicated with by this safety check in the specific position of valve body.Based on set safety check again in conjunction with multiple-way valve, the pressure-loaded that can realize the outside of active chamber in the special position of valve body also can realize the pressure balance between active chamber.But the defect of this solution is, safety check itself requires the installation process that expends and itself is formed by the valve body of load on spring, and valve body may cause vibration under adverse conditions.
By DE 10 2,010 022 896 A1 known a kind of for internal-combustion engine by hydraulically controlled camshaft adjuster, it is with the active chamber of at least two adverse effects of pressure medium pump, pressure medium reservoir and the housing comprising multiple-way valve, this housing is with multiple active chamber, the opening of attaching troops to a unit in pressure medium pump and pressure medium reservoir, inflow and/or the outflow of pressure medium can be realized by these openings, wherein, use following valve body, this valve body utilizes the control seamed edge abutted on housing to realize or the opening of occluding pressure medium percolation in housing according to position, and this valve body is also provided with check vavle device, it can realize pressure medium and enter another active chamber corresponding and attaching troops to a unit in the flowing of valve body conversely from an active chamber.At this, the document should be mentioned that, valve body has at least two pressure medium conduit, and they can be connected with one of them in active chamber respectively in flow technique, and check vavle device is formed by the latch plate of confining pressure medium pipeline.
In DE 10 2,010 024 026 A1, also known another kind is used for the equipment that can switch of supply pressure.Disclose a kind of at least one expendable part supply pressure for combustion motor in the publication in particular for the equipment that can switch to camshaft adjuster supply pressure.This equipment comprises the accumulator of the movable component of layout especially piston in the cavities and the especially spring element with movable component mating reaction, wherein, the power that movable component can overcome accumulator by carrying out pressure-loaded with pressure medium to apotheca moves to the second end position from first end position.Even if when little oil pressure or little engine speed, trouble-free operation for the equipment that can switch of supply pressure is also guaranteed, its method is, accumulator is arranged in interior room, in this interior room, at least when movable component moves to the second end position from first end position by vacuum pump to adjust negative pressure.
But it is known that such problem may be there is when internal combustion engine start, that is, in the oil return line of motor, do not have enough oil pressure to be remained in specific position by camshaft adjuster.Result is exactly, and camshaft adjuster starts to vibrate uncontrollably.In addition, because blade backstop causes noise on the stator that also can be called as external rotor.
It is known that solve the problem mentioned as follows, that is, carry out the axial locking between internal rotor in camshaft adjuster and the locking lid of lateral arrangement.At this, carry out locking in an end stop position " delayed " or " shifting to an earlier date " at least wherein.At this, locking gap can be adjusted relative to the corresponding location of external rotor by internal rotor before camshaft adjuster is installed relatively without problems.This gap on the one hand should be not excessive, because otherwise just there will be less desirable noise, on the other hand should be not too small yet, and because the lock pin that also can be called as locking nail or lockup piston otherwise can be made no longer can reliably to lock or unlock.
But locking " shifts to an earlier date " or also defectiveness in " delayed " to end position, thus expect to carry out locking in the central position between " shifting to an earlier date " and " delayed ".The difference of the center locking and end stop locking that can realize this point is, camshaft adjuster " shifts to an earlier date " by locking in the Angle Position of the restriction between " delayed " at two end positions, and this is especially favourable when engine start.This center locking is such as known by EP 2 132 417 B1.
Usually a kind of locking chute of V-arrangement is utilized, locking gap can be adjusted by moving radially lid.But in this solution, although locking gap can be adjusted, the position of lock position, center itself is determined by this adjustment equally thereupon.The movement of this radial direction of lid causes the additional imbalance on camshaft adjuster, but this imbalance should be avoided.Although just locking gap should can be adjusted, also negative impact should be avoided.Compare current, locking gap also should be adjusted more simply.
Summary of the invention
Therefore, technical problem to be solved by this invention is to provide the evolutionary approach for hydraulic camshaft adjuster, but also improves such internal-combustion engine.
This technical problem solves as follows according to the present invention in the hydraulic camshaft adjuster of generic, namely, second locking nail can towards from the first axial direction parallel but the second axial direction that direction is different move into make rotor relative stator against in the second sense of rotation centre-lock different with the first sense of rotation direction in the second chute, and second locking nail can shift out from the second chute.
Favourable form of implementation also provides in the dependent claims and next explains in detail.
Therefore advantageously, when the first locking nail is not in positive with chute, the mode that rotor rotates with energy relative stator supports.Also advantageously, when the second locking nail is not in positive with the second chute, rotor energy relative stator is rotated along direction in contrast.
In addition advantageously, the first locking nail and the second locking nail are bearing in rotor in the mode that can shift out from rotor.Can set up between the first locking nail with the first chute by this way simply or the second locking follows closely positive between the second chute.So can effectively guarantee to stop rotor relative stator along the first sense of rotation or the rotational motion along the second sense of rotation.
The feature of favourable embodiment is also, the first locking nail can shift out from the first end face of rotor and the second locking nail can shift out from second end face be positioned at rotor opposite side of rotor.Certainly, locking nail also can be moved into the chute of rotor from stator in principle, but shifts out advantageously from rotor.
When in the first lid that the first chute is configured in energy rotation inhibiting on stator and/or when the second chute is configured in the second lid of energy rotation inhibiting on stator, determine that middle lock position can be separated from each other with being separated of function in adjustment locking gap.When locking nail to be bearing in the mode that can move into and shift out cover in or in stator time, in principle also it is possible that chute place in the rotor.When locking nail to be bearing in the mode that can move into and shift out in rotor or in covering time, chute also can be located in the stator.
When between stator is in the first lid in the axial direction and second covers, installs and become easy.
When the first or second locking nail in axial direction separate with sleeve by spring and preferred sleeve, spring and locking follow closely be in axial direction orientation at least in part hole such as by the blind hole of drilling kind or through hole time, operating Security also can be optimized thus according to demand in hydraulic camshaft adjuster.
In order to can mounting cover and advantageously simply, first lid and/or the second lid can be fixed on stator by least one screw, a threaded sections had for set screw preferably in two lids, wherein, further preferably threaded sections is such as configured as the constituent element of the integration that can be arranged on the first or second threaded cap covered or the first or second lid in anti-relative rotation according to the type of ring.Also particularly advantageously, use multiple screw distributed identically in relation to each other, especially those are at one end gone up with screw head and at least one region of the other end, are threaded the screw of section.The screw rod, rivet and/or the bolt that do not have screw head can certainly be used.
When screw through the kidney shape in the first or second lid or fan-shaped recess such as elongated hole stretch out time, the mobility covered to each other can be guaranteed when screw inserts.
The present invention also relates to a kind of with the internal-combustion engine of camshaft with the camshaft adjuster of this camshaft of manipulation, camshaft adjuster designs according to the present invention.
Can realize a kind of solution of the alternative for lock position, center by this way, this lock position, center and locking gap have nothing to do and do not represent additional imbalance.Locking chute is placed in two lids at this, and wherein, these lids can rotate relative to each other when mounted and guarantee independently of one another the adjustment of lock position, center and the adjustment to locking gap.
Therefore, center locking is realized by the locking chute of two in lid in hydraulic camshaft adjuster, wherein, first locking chute is included in protecgulum, and the second locking chute is included in bonnet, wherein, be mounted with two locking units in the rotor, described two locking units comprise locking nail, locking spring and sleeve.Locking unit loads on opposed orientation ground in the rotor.First locking nail embeds in stress-free first locking chute also by pushing back again in rotor from the oil pressure of the first oil boring or the first oil groove.Second locking nail embeds in stress-free second locking chute also by pushing back again in rotor from the oil pressure of the second oil boring or the second oil groove.To the oil supply of two locking chutes by independent, be that the oil pipe separated realizes with the oil supply for oil pocket.
Camshaft adjuster therefore can intactly pre-installation, wherein, lid screw is not yet tightened, and protecgulum is bearing in the mode that can rotate in the elongated hole in stator also can rotate the position entering into expectation, until adjust locking gap, now, this position is just fixed by from exterior mechanical.Lock position, center is determined in blocked part in first locking chute, this is because that is the friction torque of camshaft presses rotor or the first locking nail in the current situation widdershins towards delayed direction all the time.Bonnet can be configured in the elongated hole inner rotation in bonnet.First bonnet rotates at this, thus the blocked part in the second locking chute and locking nail joint are touched.Locking gap can be 0 °.But gap width is preferably adjusted to 0.6 ° to 1.2 °, the best is 0.8 °.
Bonnet rotates, until adjust to total locking gap of expectation towards other direction subsequently.Bonnet is equally mechanically fixed at this.Last just by lid screw-driving.Threaded cap to be assemblied on regulator and to be clamped with stator by two lids.
Accompanying drawing explanation
Next the present invention is explained in detail by accompanying drawing.The first embodiment is shown in detail in accompanying drawing.Wherein:
Fig. 1 illustrates the stereogram of the assembling according to hydraulic camshaft adjuster of the present invention;
Fig. 2 illustrates the camshaft adjuster of Fig. 1 from front, but it is with the first protecgulum shown in perspective;
Fig. 3 illustrates the camshaft adjuster of Fig. 1 and 2 from rear, it is with the second bonnet shown in perspective;
Fig. 4 illustrates rotor separately, and it is with two place's Locking Devices that can shift out along different directions within it; And
Fig. 5 illustrates this camshaft adjuster of Fig. 1 to Fig. 3 from rear, that is illustrates as shown in Figure 3, but is different from Fig. 3, and it is with mounted threaded cap now.
Accompanying drawing is only schematically also only for understanding the present invention.The identical reference character of identical element marks.
Embodiment
Figure 1 illustrates the first form of implementation of hydraulic camshaft adjuster 1.This camshaft adjuster 1 utilizes the pressure provided by fluid.This fluid can be oil and be directed in the different pressure chamber between stator 2 from rotor 3.
Pressure chamber reference character 4 marks in fig. 2.Pressure chamber 4 passes through the blade 5 be in rotor 3 regularly and is divided into the first pressure chamber and the second pressure chamber 7.In two width Fig. 1 and 2 it is seen that, it is inner that rotor 3 is in stator 2 diametrically.First protecgulum 9 passes through preferably five screws 8 that also can be called as lid screw to be fixed on the stator 2 in the side of rotor 3.
Rotor 3 can be connected with camshaft or be connected with camshaft.Stator 2 has tooth 10 on the outside, and these teeth guarantee the connection with the bent axle of internal-combustion engine by towing gear.
In fig. 2 it is seen that, first lid 9 in there is the first chute 11.This first chute 11 also can be called as locking chute and position for rotor 3 relative stator 2 is determined, this is because the first lid 9 is connected with stator 2 in anti-relative rotation by screw 8.
The first pin-shaped locking nail 12 that also can be called as lock pin or lockup piston is bearing in rotor 3 in the mode that can shift out along the first axial direction, thus the first locking nail when shifting out and the first chute 11 in side snugly positive.First axial direction is parallel to spin axis 13 ground orientation.
First locking nail 12 is parts of the first Locking Device, first Locking Device also additionally has the first locking spring 14 and the first sleeve 15, wherein, locking spring 14 is configured to helical spring and arranges contiguously with both between the first locking nail 12 and the first sleeve 15.This is such as shown in Figure 4.
Therefore also it is seen that, exist second locking nail 16, it is all the parts of the second Locking Device together with the second locking spring 17 and the second sleeve 18.Two Locking Devices continuously structure construct in the same manner, but direction is differently arranged in rotor 3, thus the first locking nail 14 can shift out from the first side 19 of rotor 3 and the second locking nail 16 can shift out from the second side 20 of rotor 3.First side 19 also can be called as the first end face, just as the second side 20 also can be called as the second end face.It is inner that first sleeve 15 and the second sleeve 18 are in rotor 3, just as the first locking spring 14 and the second locking spring 17.
Two Locking Devices are in two different through holes 21 in principle.But, two Locking Devices also can be in unique through hole 21.Be provided with two Locking Devices at this, but do not oppose to there is multiple Locking Device, such as four or six Locking Devices.But advantageously, two Locking Devices are restricted to.
Also be noted that in fig. 2, hydraulic fluid such as oil can be imported to also can be called as the first chute 11 of locking chute by the first oil boring 22 and the first oil groove 23 from innermost radial zone, to be pushed back in rotor 3 by the first locking nail 12.
In order to ensure degassing function, through hole 21 is provided with the air vent 24 extended radially inwardly.
Also advantageously, screw 8 through stretching out in stator 2 with being configured to the through hole of elongated hole 25.In the second lid 26, be provided with elongated hole equally, but these elongated hole reference characters 27 mark.Screw 8 stretches out through these elongated hole 27 ground equally.Also or elongated hole 25 can be used, or use other elongated hole 27.
Second chute 28 is in the second lid 26, and the second locking nail 16 embeds in this second chute.With similar when following closely 12 at the first locking, also by the second oil boring 29 and the second oil groove 30, oil can be flowed to the second locking nail 16.
When the first locking nail 12 and the first chute 11 are in lock position, the center of arrival during positive, with the second chute 28 positive while of the second locking nail 16, wherein, the face or the blocked part that reach positive are opposite each other.Positive between the first locking nail 12 and the first chute 11 prevents rotor relative stator along the rotation of a sense of rotation, and the positive between the second locking nail 16 and the second chute 28 then prevents the rotation along another sense of rotation.Two sense of rotation are contrary, that is the direction that the direction of an edge " delayed " and an edge " shift to an earlier date ".
When screw has screw head 31 as such as seen in FIG on side, so they just only have threaded portion 32 on another side, and the threaded sections 33 that this threaded portion and second covers 26 is in bolt-lock and closes (Zapfschluss).
In the 5 embodiment of figure 5, threaded sections 33 is configured to cover 26 components separated with second, that is is configured to independently threaded cap 34.Threaded cap 34 has the shape of ring.
Threaded cap 34 and second covers 26 and is connected un-rotatably.
Reference numerals list
1 camshaft adjuster
2 stators
3 rotors
4 pressure chambers
5 blades
6 first pressure chambers
7 second pressure chambers
8 screws
9 first lids
10 teeth
11 first chutes
12 first locking nails
13 spin axiss
14 first locking springs
15 first sleeves
16 second locking nails
17 second locking springs
18 second sleeves
19 first sides
20 second sides
21 through holes
22 first oil borings
23 first oil grooves
24 air vents
25 elongated holes
26 second lids
27 elongated holes
28 second chutes
29 second oil borings
30 second oil grooves
31 screw head
32 threaded portions
33 threaded sections
34 threaded caps

Claims (9)

1. a hydraulic camshaft adjuster (1), it is with stator (2) and rotor (3), described rotor can be connected with camshaft, wherein, described rotor (3) can releasably be fixed on stator (2) against the first sense of rotation by least one first pin-shaped locking nail (12) in anti-relative rotation in central position, wherein, described locking nail (12) is designed for the first axial direction limited along the spin axis (13) by stator (2) and/or rotor (3) and moves into and/or shift out the first chute (11), it is characterized in that, second locking nail (16) can towards parallel with the first axial direction, but different the second axial direction in direction moves in the second chute (28) to make the relatively described stator of described rotor (3) (2) against in the second sense of rotation centre-lock different from the first sense of rotation direction, and described second locking nail can shift out from described second chute (28).
2. by camshaft adjuster according to claim 1 (1), it is characterized in that, when described first locking nail (12) is not in positive with described first chute (11), described rotor (3) supports in the mode can rotated along at least the first sense of rotation relative to described stator (2), and/or when described second locking nail (16) is not in positive with described second chute (28), described rotor (3) supports in the mode can rotated along at least the second sense of rotation relative to described stator (2).
3. by the camshaft adjuster (1) described in claim 1 or 2, it is characterized in that, described first locking nail (12) and described second locking nail (16) are bearing in rotor in the mode that can shift out from described rotor (3).
4. by the camshaft adjuster (1) described in any one of claims 1 to 3, it is characterized in that, described first locking nail (12) can shift out from first end face (19) of described rotor (3) and described second locking nail (16) can shift out from the second end face (20) the opposite side being in described rotor (3) of described rotor (3).
5. by the camshaft adjuster (1) described in any one of Claims 1-4, it is characterized in that, described first chute (11) be configured in can in the first lid (9) of the upper rotation inhibiting of described stator (2) and/or described second chute (28) be configured in and can cover in (26) second of the upper rotation inhibiting of described stator (2).
6. by camshaft adjuster according to claim 5 (1), it is characterized in that, described stator (2) is in described first lid (9) and described second in the axial direction and covers between (26).
7. by the camshaft adjuster (1) described in any one of claim 1 to 6, it is characterized in that, the first or second locking nail (12,16) is separated by spring (14,17) and sleeve (15,18) and preferred described sleeve (15,18), described spring (14,17) and described locking follow closely hole that (12,16) be in axial direction orientation at least in part such as by the blind hole of drilling kind or through hole (21).
8. by the camshaft adjuster (1) described in any one of claim 5 to 7, it is characterized in that, described first lid (9) and/or described second lid (26) can be fixed on stator (2) by least one screw (8), wherein, preferably two lids (9, 26) one of them in has the threaded sections (33) for fixing described screw (8), wherein, further preferably, described threaded sections (33) is configured as and can be arranged on the first or second lid (9 in anti-relative rotation, 26) on such as according to the type of ring threaded cap (34) or first or second lid (9, 26) constituent element of integration.
9. by camshaft adjuster according to claim 8 (1), it is characterized in that, described screw (8) stretches out through the elongated hole (27) in kidney shape or fan-shaped groove such as first or second lid (9,26).
CN201380036098.XA 2012-07-06 2013-04-24 Hydraulic camshaft adjuster with centre locking and adjustable locking play Pending CN104812996A (en)

Applications Claiming Priority (3)

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DE102012211870.5 2012-07-06
DE102012211870.5A DE102012211870A1 (en) 2012-07-06 2012-07-06 Hydraulic camshaft adjuster with central locking and adjustable locking clearance
PCT/EP2013/058418 WO2014005739A1 (en) 2012-07-06 2013-04-24 Hydraulic camshaft adjuster with centre locking and adjustable locking play

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US (1) US20150322825A1 (en)
CN (1) CN104812996A (en)
DE (1) DE102012211870A1 (en)
WO (1) WO2014005739A1 (en)

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WO2014005739A1 (en) 2014-01-09
US20150322825A1 (en) 2015-11-12

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