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CN102812214A - Camshaft Arrangement - Google Patents

Camshaft Arrangement Download PDF

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Publication number
CN102812214A
CN102812214A CN2010800447759A CN201080044775A CN102812214A CN 102812214 A CN102812214 A CN 102812214A CN 2010800447759 A CN2010800447759 A CN 2010800447759A CN 201080044775 A CN201080044775 A CN 201080044775A CN 102812214 A CN102812214 A CN 102812214A
Authority
CN
China
Prior art keywords
axle
face
rotor
cam shaft
cam
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.)
Granted
Application number
CN2010800447759A
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Chinese (zh)
Other versions
CN102812214B (en
Inventor
马蒂亚斯·卡普
克雷格·杜普伊斯
因赫瓦·钟
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.)
Fifth Schaeffler Investment Management & CoKg GmbH
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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Filing date
Publication date
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Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of CN102812214A publication Critical patent/CN102812214A/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02Valve drive
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02Valve drive
    • F01L1/04Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02Valve drive
    • F01L1/04Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047Camshafts
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20Valve-gear or valve arrangements actuated non-mechanically by electric means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D13/00Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02Valve drive
    • F01L1/04Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047Camshafts
    • F01L2001/0471Assembled camshafts
    • F01L2001/0473Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D13/00Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0203Variable control of intake and exhaust valves
    • F02D13/0215Variable control of intake and exhaust valves changing the valve timing only

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

The invention relates to a camshaft arrangement (1) for changing the relative angle of at least one first cam of a camshaft (2) relative to a second cam of the camshaft (2), wherein the arrangement comprises an angle adjusting device (3) having a stator (4) and a rotor (5) rotatably disposed relative to said stator, wherein the rotor (5) is rotationally fixed to a shaft (6), wherein the stator (4) is rotationally fixed to a hollow shaft (7), wherein the shaft (6) and the hollow shaft (7) are disposed concentric to each other, wherein the at least one first cam is rotationally fixed to the shaft (6), wherein the at least one second cam is rotationally fixed to the hollow shaft (7), and wherein the rotationally fixed connection between the rotor (5) and the shaft (6) is produced by at least one screw (8). In order to establish a fixed connection between the rotor and the shaft, taking up little space, according to the invention, the shaft (6) having an end face (9) contacts a contact surface (10) of the rotor (5) and is pulled against the contact surface (10) by means of the at least one screw (8), wherein the shaft (6) comprises a cross-sectional area (A1) along the axial extent thereof present in the area of the rotor (5), said cross-sectional area expanding to a greater value (A2) out to the end face (9) thereof.

Description

Cam shaft system
Technical field
The present invention relates to a kind of cam shaft system of at least one first cam of camshaft with respect to the relative angle position of second cam of camshaft that be used to change, wherein, this system comprises angular adjustment apparatus; This angular adjustment apparatus has stator and with respect to this stator rotor arranged rotationally, wherein, rotor is connected with axle antitorquely; Wherein, stator is connected with hollow shaft antitorquely, wherein; Axle and hollow shaft arrange concentrically that each other wherein, at least one first cam is connected with axle antitorquely; And wherein; At least one second cam is connected with hollow shaft antitorquely, and wherein, sets up with antitorque being connected through at least one bolt between the axle at rotor.
Background technique
Such cam shaft system is known as " Cam in Cam (cam be nested cam) " system.At least two cams of camshaft (being mostly several corresponding cams) can rely on this system on camshaft, to be reversed relative to one another, so that change the port timing of Gas Exchange Process of Internal Combustion Engine valve.This type cam shaft system is for example in EP 1 945 918 B1, introduce in GB 2 423 565 A and in WO 2009/098497 A1 to some extent.
Be well known that, twist component with antitorque being connected between the axle by means of bolt in the part of rotor or rotor and set up that wherein, use at least one centre bolt, this centre bolt is arranged with respect to the axis of axle and hollow shaft concentrically.In mentioned publication document, partly pointed out such solution.
What shown is that this connection shows as weak part to a certain extent.Only in the scheme of centre bolt, can guarantee enough pretensions, thereby make connection firmly lasting by the EXPANSION ANCHOR BOLTS structure.Yet it possibly loosened with antitorque being connected between the rotor at axle under the situation of stronger load.Correspondingly, show as weak part under the situation of axle and the regulating device that is connected the type of rotor, this weak part causes the functional failure of cam shaft system under failure condition.
Summary of the invention
The present invention is based on following task, that is: improve like this cam shaft system of previous mentioned type: rotor with spool between be connected and improve.At this, lasting firm connection should be guaranteed under the situation that need not enlarge operational structure space.
This task is characterised in that through solution of the present invention; The axle with end face by be placed on rotor by putting on the face; And be pulled to by putting face by means of at least one bolt; Wherein, axle is in extending axially in the zone of rotor along it, has the cross sectional area that expands bigger value until end face to.
The expansion section of cross sectional area preferably is limited on the zone near the next-door neighbour of end face.Especially do following understanding, that is, the expansion section of cross sectional area is limited to as on the lower area, promptly; Its end face maximum from axle is extended 10mm, particularly preferably does following the setting, promptly; The expansion section of cross sectional area is limited to as on the lower area, that is, and and between the end face extension 3mm and 8mm of axle.
Axle can along its be in the zone of rotor and also extending axially beyond the expansion section of cross section, have constant cross section.
The outer diameter of axle on its end face preferably be equivalent at least bolt bolt head outer diameter 80%,, particularly preferably be equivalent at least bolt head outer diameter 90%.
At this, the outer diameter of axle is preferably carried out by zone to the transition in the zone of the cross sectional area that enlarges of small cross section area continuously.Especially do following setting, that is, and this transition rounding ground structure.
Preferably, have unique bolt, this bolt is arranged with its axis and axle as centre bolt concentrically; At this, bolt advantageously is configured to EXPANSION ANCHOR BOLTS.
Axle can be in extending axially and be configured to hollow shaft in the zone of rotor along it, and has constant inner diameter until end face.In addition, axle can be in extending axially until the expansion section of its cross sectional area in the zone of rotor along it and have following outer diameter, and this outer diameter is up to 90% of the outer diameter of axle on its end face.Particularly preferably do following the setting, that is, axle until the outer diameter of the expansion section of its cross section be in axle the outer diameter on its end face 80% and 90% between.
Angular adjustment apparatus preferably is configured to the regulating device of hydraulic pressure.
Utilize this design proposal feasible be between rotor and axle, to set up very firm being connected of less space that occupy.The expansion of the end regions of the end face through axle significantly improved the area of contact with rotor, thereby obtained that axle improves at the rotor place and more firm in putting.
Description of drawings
One embodiment of the present of invention shown in the drawings.Wherein:
Fig. 1 a shows the radial cross section of the cam shaft system with the camshaft that is made up of two concentric axles of internal-combustion engine, and wherein, this system has angular adjustment apparatus,
Fig. 1 b shows the thin portion " X " according to Fig. 1 a,
Fig. 2 schematically shows the suction valve of internal-combustion engine and the change curve in time that outlet valve is accordinged to first kind of feasible mode of operation opening and closing,
Fig. 3 schematically show said valve according to second kind of feasible mode of operation opening and closing change curve in time,
Fig. 4 schematically shows in time the change curve of said valve according to the third feasible mode of operation opening and closing, and
Fig. 5 schematically shows in time the change curve of said valve according to the 4th kind of feasible mode of operation opening and closing.
Embodiment
In Fig. 1 a and Fig. 1 b, cam shaft system 1 has been shown, it comprises the camshaft 2 of the cam with (unshowned), and the cam that is somebody's turn to do (unshowned) concurs with scavenging air valve in known manner, so that be controlled at the gas exchange in the internal-combustion engine.
Such device is used to change the valve timing of internal-combustion engine.Use hydraulic operation formula regulator mostly.
According to first kind of strategy that goes, the controlling schemes of suction valve with respect to outlet valve is changed, perhaps conversely also can, this can be used in the motor of the structure type that is SOHC (Single Over Head Camshaft) or OHV (Overhead valve) mostly.This allows air inlet phase or exhaust phase place to utilize unique camshaft change.
Second kind of strategy that goes done following the setting, that is, one group of suction valve with respect to the port timing of another group valve with separately admission cam shaft change.This point when each cylinder be provided with two or maybe three suction valves and expectation be when changing one of them suction valve at the cylinder place, can be used with respect to the port timing of another suction valve.
According to the third strategy that goes, one group of outlet valve changes with separately exhaust cam shaft with respect to the port timing of another group valve.This point is provided with two or maybe three outlet valves when each cylinder, wherein, expectation be when changing an outlet valve at the cylinder place, can be used with respect to the port timing of other outlet valves.
Herein, cam shaft system 1 has angular adjustment apparatus 3, and angular adjustment apparatus 3 is connected with camshaft 2.On camshaft, be furnished with the suction valve that for example is used for internal-combustion engine and the cam of outlet valve.Can realize as follows that by means of angular adjustment apparatus 3 promptly, the part of cam is reversed with respect to another part of cam.For this reason, camshaft 2 is made up of two shaft elements of arranging coaxially (promptly by axle 6 and the hollow shaft 7 in the disposed axle 6 coaxially).Be in the cam on the camshaft 2 or be connected antitorquely, or be connected antitorquely with hollow shaft 7 with axle 6.Details to this is known by EP 1 945 918 B1.
Angular adjustment apparatus 3 has stator 4 and rotor 5, and stator 4 and rotor 5 operation piece of hydraulic pressure (in this embodiment by means of) relative to one another can be reversed the angle that limits.This generation of reversing function is known in the prior art, wherein, and reference DE 10344816A1 exemplarily.In the device that this place is described, there is impeller, blade forming is in impeller, or vane collocation is in impeller.Blade is in the hydraulic chamber that is machined in the rotor.Side through to hydraulic chamber loads with hydraulic fluid accordingly, can realize the adjustment of rotor with respect to stator.
Rotor 5 is connected with axle 6 antitorquely, wherein, uses centre bolt 8 for this reason.Guarantee in rotor 5 and firm radially be connected and axially be connected of axle between 6 through centre bolt 8.
Should connect in order to constitute especially securely, the present invention does following setting, that is, axle 6 with one of its end face 9 by be placed on rotor 5 by putting on the face 10, and be pulled to by putting face 10 by means of centre bolt 8.For reach axial end by put improvement on the face by putting, do to be provided with as follows, that is, axle 6 is in extending axially in the zone of rotor 5 along it, has cross sectional area A 1, cross sectional area A 1When reaching end face 9, expand bigger value A to 2Area A 1And A 2In Fig. 1 b, show; What here, relate to is the face that is ring.
The preferred sizes of the those widened sections of the end face of axle 6 is set scheme and is drawn by given geometric data equally.Axle 6 is implemented as hollow shaft in the axial zone of rotor 5, and correspondingly has inner diameter D IThe outer diameter of axle 6 is with D A0Express.Axle 6 is widened towards the end face end of axle 6, that is to say the outer diameter value of being increased to D AExpress with x in the axial zone that cross sectional area enlarges within it.
At this, the outer diameter D in the end regions of the end face of axle 6 APreferably approximately and the outer diameter D of the bolt head 11 of centre bolt 8 ASOnesize, perhaps outer diameter D ASmaller.
As further visible, construct to the transition part 12 of bigger cross sectional area by the small cross section area, so that avoid stress to concentrate roundedly.
In addition, stator 4 has covering element 13, and covering element 13 is connected with stator 4 by means of bolt 14.Hollow shaft 7 is connected with covering element 13 antitorquely.At this, carry out as follows with the antitorque covering element 13 that is connected through being connected between the hollow shaft 7 at stator 4 with stator 4, that is: covering element 13 has the hole, in order to hold columniform section of hollow shaft 7.Do following the setting at this, that is, in the columniform surface of contact 15 between covering element 13 and the hollow shaft 7, exist the power cooperation and/or material fit is connected.
On the side of putting relatively with covering element 13, angular adjustment apparatus 3 is sealed with another covering element 16.Angle regulating device 3 and then the driving that also has camshaft 2 are undertaken by (unshowned) chain by the crank-driven of internal-combustion engine through small gear 17 in known manner.Small gear 17 constitutes independent member here.Yet small gear 17 can be constructed with the mode that is integrated in the stator 4 equally.
Thus, feasible is, to exerting one's influence with the phase place between the cam that coaxial 6 are connected antitorquely at the cam that is connected with hollow shaft 7 antitorquely, just adjusts.At this, be connected according to the present invention structure so securely at rotor 5 and axle between 6, that is, can transmit enough torques, so that realize operation to cam against the spring force of scavenging air valve.Identical situation is applicable to being connected between stator 4 and the hollow shaft 7 naturally.
The feasible method of operation by cam shaft system of internal-combustion engine illustrates in Fig. 2 to 5.These figure correspondingly show cam and are applied to the opening travel change curve in time on the valve.
In the motor that has single camshaft (SOHC structure type-Single Over Head Camshaft) or in the motor of OHV structure type (Overhead valve), axle 6 operations platoon's air valves, wherein, outlet valve can be adjusted with respect to the controlling schemes of the bent axle of motor.At this, visible among half figure to the left side of operation scheme in Fig. 2 of outlet valve, and visible among half figure on the right be operation scheme to suction valve.Explained corresponding to the curvilinear motion process that is shown in dotted line of outlet valve and along the mobile of double-head arrow direction: the adjustment feasibility of angle regulating device 3 is used for this reason.
Under the situation of Fig. 2, this makes the controlling schemes (that is to say opening and closing) of optimization that outlet valve is depended on rotating speed and the load condition of internal-combustion engine become possibility.This causes higher fuel efficiency in an advantageous manner and produces the discharging that reduces.
For motor with for structure type identical among Fig. 2, visible in Fig. 3, when axle 6 operation suction valves, what kind of change curve looks like.Also in half figure in left side, and visible in half figure on right side to the operation scheme of outlet valve to the operation scheme of suction valve.Here, at this moment again for the curvilinear motion process that is shown in dotted line and double-head arrow and find out that suction valve can be changed with respect to the phase place of bent axle.
Under the situation of Fig. 3, this controlling schemes (that is to say opening and closing) of optimization that makes suction valve depend on rotating speed and the load condition of internal-combustion engine becomes possibility.Volumetric efficiency can be enhanced, and this torque that has produced the improvement of motor generates and higher fuel efficiency, and has produced the roadability preferably of motor.
In the motor that has two camshafts (DOHC (Dual Over Head Camshaft) structure type) that are in top, can do following setting; Promptly; Axle 6 utilizes the cam that is fixed on the axle 6 to operate one or more outlet valves of each cylinder antitorquely, and remaining outlet valve is operated through hollow shaft 7 and the cam that is arranged on the hollow shaft 7 antitorquely.Fig. 4 shows such solution.In this case, can realize that for each cylinder the one or more operation schemes with respect to remaining outlet valve in the outlet valve adjust.Visible among half figure in the left side in Fig. 4 promptly, at least one outlet valve (referring to solid line) is loaded with fixing port timing as follows, and another outlet valve (referring to dotted line and double-head arrow) can be adjusted aspect port timing at least.Here, suction valve can not be by adjustment (referring to half figure on right side) aspect port timing.
Thus, can change the duration of the unlatching of outlet valve, thereby make that the opening time of outlet valve can be optimised.The unlatching that outlet valve is done sth. in advance at lower dead centre (UT) before makes internal-combustion engine heat up faster becomes possibility, and this has reduced cold start-up-discharging.
Letter illustrates the similar solution with Fig. 4 in Fig. 5.Likewise here, the motor of DOHC (Dual Over Head Camshaft) structure type obtains using.Axle 6 is operated one or more suction valves of each cylinder here, and remaining suction valve is operated by hollow shaft 7.
Thus, can realize control again as follows, that is, the valve opening time of inlet can be changed.Solid line in half figure on the right side of Fig. 5 shows the controlling schemes of the one or more suction valves that possess immutable port timing again; And the explanation of dotted line and double-head arrow is, remaining suction valve with regard to regard to its controlling schemes by means of angular adjustment apparatus 3 change in time.
Therefore, be similar to Fig. 4 ground here, can change the duration of inlet open.In addition, can optimize the shut-in time of suction valve equally.This can be used to carry out the strategy (the retarded admission valve cuts out (LIVC-Late Intake Value Closing)) of suction valve late release.
Suction valve cuts out afterwards at lower dead centre (UT) and makes and to become possibility as follows, that is, the part of gas is pushed back to be drawn in the section, and this has reduced the length of compression section.This causes the reduction of the pumping loss of motor, and therefore causes the fuel efficiency of improvement.The closing of suction valve can depend on rotating speed and engine load is optimized.
Reference numerals list
1 cam shaft system
2 camshafts
3 angular adjustment apparatus
4 stators
5 rotors
6
7 hollow shafts
8 bolts (centre bolt)
9 end faces
10 by putting face
11 bolt heads
12 transition parts
13 covering elements
14 bolts
15 columniform surface of contact
16 covering elements
17 small gears
A 1Cross sectional area
A 2Cross sectional area
X zone (extending axially)
D AOuter diameter
D ASThe outer diameter of bolt head
D IInner diameter
D A0Outer diameter

Claims (15)

1. be used to change the cam shaft system (1) of at least one first cam of camshaft (2) with respect to the relative angle position of second cam of said camshaft (2), wherein, said system comprises angular adjustment apparatus (3); Said angular adjustment apparatus (3) have stator (4) and with respect to this stator (4) with rotating mode rotor arranged (5), wherein, said rotor (5) is connected with axle (6) antitorquely; Wherein, Said stator (4) is connected with hollow shaft (7) antitorquely, and wherein, said axle (6) and said hollow shaft (7) are arranged each other concentrically; Wherein, Said at least one first cam is connected with said axle (6) antitorquely, and wherein, at least one second cam is connected with said hollow shaft (7) antitorquely; And wherein; Setting up antitorque the connection through at least one bolt (8) between said rotor (5) and said axle (6) is characterized in that, said axle (6) with end face (9) by be placed on said rotor (5) by putting on the face (10) and being pulled to said by means of at least one bolt (8) by putting face (10); Wherein, said axle (6) has cross sectional area (A along the longitudinal extension in the zone that is in said rotor (5) of said axle (6) 1), said cross sectional area (A 1) when reaching said end face (9), expand bigger value (A to 2).
2. cam shaft system according to claim 1 is characterized in that, said cross sectional area (A 2) the expansion section be limited to zone near the next-door neighbour of said end face (9).
3. cam shaft system according to claim 2 is characterized in that, said cross sectional area (A 2) the expansion section be limited to the zone (x) of extending 10mm from end face (9) maximum of said axle (6).
4. cam shaft system according to claim 3 is characterized in that, said cross sectional area (A 2) the expansion section be limited to from the end face (9) of said axle (6) and extend the zone (x) between 3mm and the 8mm.
5. cam shaft system according to claim 1 is characterized in that, said axle (6) extending axially in the zone that is in said rotor (5) of said axle (6) and beyond the expansion section of said cross sectional area has constant cross section.
6. cam shaft system according to claim 1 is characterized in that, the outer diameter (D that said axle (6) is located at the end face (9) of said axle (6) A) be equivalent to the outer diameter (D of the bolt head (11) of said bolt (8) at least AS) 80%.
7. cam shaft system according to claim 6 is characterized in that, the outer diameter (D that said axle (6) is located at the end face (9) of said axle (6) A) be equivalent to the outer diameter (D of the bolt head (11) of said bolt (8) at least AS) 90%.
8. cam shaft system according to claim 1 is characterized in that, the outer diameter of said axle (6) is from small cross section area (A 1) the zone to the cross sectional area (A that enlarges 2) the transition part (12) in zone realize continuously.
9. cam shaft system according to claim 8 is characterized in that, transition part (12) the rounding ground structure of the outer diameter of said axle (6).
10. cam shaft system according to claim 1 is characterized in that, has unique bolt (8), and said bolt (8) is arranged with the axis and the said axle (6) of said bolt (8) as centre bolt concentrically.
11. cam shaft system according to claim 10 is characterized in that, said bolt (8) is configured to EXPANSION ANCHOR BOLTS.
12. cam shaft system according to claim 1; It is characterized in that; Said axle (6) extending axially in the zone that is in said rotor (5) of said axle (6) is configured to hollow shaft, and has constant inner diameter (D until said end face (9) I).
13. cam shaft system according to claim 1 is characterized in that, extending axially in the zone that is in said rotor (5) of said axle (6), and until the expansion section of the cross sectional area of said axle (6), said axle (6) has outer diameter (D A0), this outer diameter (D A0) be up to the outer diameter (D that said axle (6) is located at the end face (9) of said axle (6) A) 90%.
14. cam shaft system according to claim 13 is characterized in that, until the expansion section of the cross sectional area of said axle (6), the outer diameter (D of said axle (6) A0) be in the outer diameter (D that said axle (6) is located at the end face (9) of said axle (6) A) 80% and 90% between.
15. cam shaft system according to claim 1 is characterized in that, said angular adjustment apparatus (3) is configured to the regulating device of hydraulic pressure.
CN201080044775.9A 2009-10-05 2010-10-04 Cam shaft system Active CN102812214B (en)

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US24863409P 2009-10-05 2009-10-05
US61/248,634 2009-10-05
PCT/EP2010/064752 WO2011042392A1 (en) 2009-10-05 2010-10-04 Camshaft arrangement

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111485969A (en) * 2019-01-28 2020-08-04 舍弗勒技术股份两合公司 Camshaft phase adjuster

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011052822A1 (en) 2011-08-18 2013-02-21 Thyssenkrupp Presta Teccenter Ag Camshaft, in particular for motor vehicle engines
CN107313821B (en) * 2017-08-30 2023-06-16 上海汽车集团股份有限公司 Connecting structure of camshaft end piece

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4771742A (en) * 1986-02-19 1988-09-20 Clemson University Method for continuous camlobe phasing
US5417186A (en) * 1993-06-28 1995-05-23 Clemson University Dual-acting apparatus for variable valve timing and the like
US6820578B2 (en) * 2002-09-26 2004-11-23 Aisin Seiki Kabushiki Kaisha Valve timing control device
DE102007017514A1 (en) * 2007-04-13 2008-10-16 Mahle International Gmbh camshaft
US7469670B2 (en) * 2006-05-27 2008-12-30 Mahle International Gmbh Adjustable camshaft

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2822147C3 (en) 1978-05-20 1982-02-11 Volkswagenwerk Ag, 3180 Wolfsburg Camshaft arrangement, in particular for an internal combustion engine
JPH07224617A (en) * 1994-02-09 1995-08-22 Unisia Jecs Corp Valve timing control device for internal combustion engine
GB2369175A (en) 2000-11-18 2002-05-22 Mechadyne Plc Variable phase coupling
GB2423565A (en) 2005-02-23 2006-08-30 Mechadyne Plc Inner camshaft of SCP assembly receives drive via sleeve on outer tube
GB2431977A (en) 2005-11-02 2007-05-09 Mechadyne Plc Camshaft assembly
DE102005061187A1 (en) * 2005-12-21 2007-06-28 Mahle International Gmbh camshaft
GB2457228A (en) 2008-02-05 2009-08-12 Mechadyne Plc Lubricating oil feed arrangement for a single cam phaser (SCP) camshaft
DE102008019747A1 (en) * 2008-04-19 2009-10-22 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102008019746A1 (en) * 2008-04-19 2009-10-22 Schaeffler Kg Device for variable adjustment of valve timings of charge-cycle valves of internal combustion engine, has two drive elements and side cap, where former drive element is brought in drive connection with crankshaft
EP2334913B1 (en) 2008-09-19 2014-01-01 Borgwarner Inc. Cam torque actuated phaser using band check valves built into a camshaft or concentric camshafts

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4771742A (en) * 1986-02-19 1988-09-20 Clemson University Method for continuous camlobe phasing
US5417186A (en) * 1993-06-28 1995-05-23 Clemson University Dual-acting apparatus for variable valve timing and the like
US6820578B2 (en) * 2002-09-26 2004-11-23 Aisin Seiki Kabushiki Kaisha Valve timing control device
US7469670B2 (en) * 2006-05-27 2008-12-30 Mahle International Gmbh Adjustable camshaft
DE102007017514A1 (en) * 2007-04-13 2008-10-16 Mahle International Gmbh camshaft

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111485969A (en) * 2019-01-28 2020-08-04 舍弗勒技术股份两合公司 Camshaft phase adjuster
CN111485969B (en) * 2019-01-28 2024-09-06 舍弗勒投资(中国)有限公司 Camshaft phase adjuster

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KR101675613B1 (en) 2016-11-11
US20120199085A1 (en) 2012-08-09
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EP2486249A1 (en) 2012-08-15
EP2486249B1 (en) 2017-04-19
KR20120089281A (en) 2012-08-09
WO2011042392A1 (en) 2011-04-14

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