CN104428497A - A concentric camshaft arrangement - Google Patents

A concentric camshaft arrangement Download PDF

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Publication number
CN104428497A
CN104428497A CN201380036920.2A CN201380036920A CN104428497A CN 104428497 A CN104428497 A CN 104428497A CN 201380036920 A CN201380036920 A CN 201380036920A CN 104428497 A CN104428497 A CN 104428497A
Authority
CN
China
Prior art keywords
outer tube
camshaft
oil supply
concentric
cylinder head
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
CN201380036920.2A
Other languages
Chinese (zh)
Other versions
CN104428497B (en
Inventor
I·梅思利
N·J·劳伦斯
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.)
Mechadyne International Ltd
Mechadyne PLC
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Mechadyne PLC
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Filing date
Publication date
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Publication of CN104428497A publication Critical patent/CN104428497A/en
Application granted granted Critical
Publication of CN104428497B publication Critical patent/CN104428497B/en
Active 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
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F01M9/102—Lubrication of valve gear or auxiliaries of camshaft bearings
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • 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
    • 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
    • F01L1/34413—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 composite camshafts, e.g. with cams being able to move relative to the camshaft
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0476—Camshaft bearings
    • 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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • 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
    • F01L2810/00—Arrangements solving specific problems in relation with valve gears
    • F01L2810/02—Lubrication
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

A concentric camshaft arrangement comprises an inner shaft ('12), an outer tube('14) concentrically arranged around the inner shaft ('12) and rotatably supported in a cylinder head ('21). A first set of lobes ('16) is fixed for rotation with the outer tube ('14) and a second set of lobes ('18) is rotatably supported by bearing journals on the outer tube ('14) and connected for rotation with the inner shaft ('12). The outer tube ('14) is supported in the cylinder head ('21) by means of a roller bearing ('42) and an oil feed ('22, '28) is provided for supplying oil for lubricating the bearing journals of the second set of cam lobes ('18). At least part of the oil feed is defined by a radial clearance between the outer surface ('20) of the outer tube ('14) and an inner surface of the cylinder head ('21) that is sealed ('48, '50) at its axial ends, the radial clearance being larger than any radial clearance at the roller bearing ('42) so that loads on the camshaft are supported at least predominantly by the roller bearing ('42).

Description

Concentric camshaft device
Invention field
The present invention relates to concentric camshaft device and in particular to use rolling bearing to support the concentric camshaft device of the load of this camshaft.Herein use term " rolling bearing " to refer to antifriction bearing, it adopts any type of roll piece, such as ball, cylindricality is rolled or pin rolls.
background of invention
Known concentric camshaft has relative to each other rotating interior axle and outer tube.Install first group of cam to this outer tube to rotate with this outer tube, and second group of cam to be arranged on the bearing journal on this outer tube and to be connected to rotate with interior axle by means of the interior axle of pin and this, described pin extends through the circumferential elongated slot in this outer tube.
Known concentric camshaft like this uses hydrokinetics bearing to be supported in motor to allow described camshaft to rotate within this motor usually.JP2010196488 describes the example of the concentric camshaft be supported on by this way in cylinder head.
In order to improve fuel consumption and reduce CO2 emission, expect to minimize frictional loss in the automotive industry.Therefore use rolling bearing to be attractive, it demonstrates friction less compared with traditional hydrodynamic bearing, to bear the load of concentric camshaft.WO2012/014069 discloses and bears camshaft load with rolling bearing.
Rolling bearing not only provides remarkable benefit in the lower friction particularly under lower engine speed, and considerably less in oily supply side demand.Therefore, oil pump size can be reduced, likely reduce the wastage further.
But use rolling bearing existing problems, the bearing journal namely supporting described second group of moveable cam lobe on concentric camshaft outer tube needs oil supply to reduce friction and to prevent the wearing and tearing between the cam lobe and camshaft tube of movement.If use rolling bearing to bear the load of known concentric camshaft, so no longer can by the one or more fluid dynamic bearing journal of this concentric camshaft for oil supply, and need the oil supply substituted to lubricate the shaft bearing of second group of cam lobe.
goal of the invention
Therefore expect the concentric camshaft device providing improvement in the automotive industry, it overcomes the problem relevant to known devices.
Summary of the invention
According to the present invention, a kind of concentric camshaft device is provided, it comprises interior axle, around this interior axle arranged concentric and the outer tube be supported on rotationally in cylinder head, be mounted to outer tube with rotate with this outer tube first group of salient angle, being rotatably supported on this outer tube and with this interior axle by bearing journal is connected with second group of salient angle of rotating with this interior axle, be arranged on the rolling bearing between this outer tube and this cylinder head, and for supplying oil to lubricate the oil supply mechanism of the bearing journal of second group of salient angle, wherein at least partly oil supply mechanism by between the outer surface and cylinder head internal surface of this outer tube and axial end portion limited by the radial internal clearance sealed, this radial internal clearance is than all large at any radial internal clearance at this rolling bearing place, thus the load on this camshaft is at least born primarily of this rolling bearing.
Sealing mechanism preferably includes the first and second seal rings, and each seal ring is provided in the sealing between the outer surface of this outer tube and the internal surface of this cylinder head.
In one embodiment, this outer tube comprises the oil supply lasso formed separately, its outer surface being fixedly installed to this outer tube to rotate with this outer tube, the outer surface of this oil supply lasso be radial internal clearance because forming this oil supply mechanism and with this isolated surface of cylinder head internal surface.
The diameter of the outer surface of this outside can equal the external diameter of this rolling bearing substantially.
Accompanying drawing explanation
To further describe the present invention by example with reference to following accompanying drawing now, wherein:
Fig. 1 is along the sectional view according to the concentric camshaft device longitudinal axes of prior art;
Fig. 2 is the sectional view along concentric camshaft device longitudinal axes according to a first embodiment of the present invention;
Fig. 3 is the sectional view along concentric camshaft device longitudinal axes according to a second embodiment of the present invention;
Fig. 4 is the sectional view along concentric camshaft device longitudinal axes according to a third embodiment of the present invention;
Fig. 5 is the sectional view along concentric camshaft device longitudinal axes according to a fourth embodiment of the present invention; And
Fig. 6 is another cross sectional view of the concentric camshaft device longitudinal axes along Fig. 5.
Embodiment
With reference to figure 1, known concentric camshaft 10 has interior axle 12 and outer tube 14.First group of cam 16 is mounted to this outer tube 14 to rotate with outer tube 14, and second group of cam 18 to be installed in rotation on the bearing journal on outer tube 14 and to be connected to rotate with interior axle by means of pin 19 with interior axle 12, described pin is through the circumferential elongated slot 30 in outer tube 14.
Oil supply mechanism 20 to be located in the hydrokinetics shaft bearing 22 of one or more camshaft and to be communicated with the radial hole 24 in outer tube 14 by the annular groove 26 in this shaft bearing 22.
Pressure oil is injected into concentric camshaft device 10 and then flows along the feeding gallery 28 be limited between interior axle 12 and outer tube 14, leaves with the groove 30 by being formed in outer tube 14, immediately below the bearing journal of second group of cam 18.
In the present ensuing specific embodiment of the invention, identical parts are assigned with the reference character with identical rudimentary number of significant digit, but are divided into 100,200,300 or 400 series according to embodiment.In the appended claims, relate to the reference character of each parts of several embodiment most significant bit (msb) number apostrophe (') substitute.
With reference to figure 2, according to a first embodiment of the present invention, concentric camshaft device 100 comprises the concentric camshaft 110 with interior axle 112 and outer tube 114.First group of cam 116 to outer tube 114 is installed to rotate with outer tube 114, and second group of cam 118 is installed in rotation on the bearing journal on outer tube 114 and is connected to interior axle 112 to rotate with interior axle by pin 19.
This concentric camshaft 110 is disposed coaxially in the perforate 122 of cylinder head 121, thus, there is pre-qualified play between the outer surface of perforate 120 and outer tube 114.
In the part that camshaft oil supply mechanism 120 is formed in cylinder head 121 or bearing support.Camshaft oil supply mechanism 120 extends to groove 126, and it is formed and extends around this periphery in the outer surface periphery of outer tube 114.The wall that the isolated radial hole 124 of multiple circumference passes outer tube 114 from groove 126 extends radially inwardly.
Radial hole 124 extends into tubulose lubricating cavity 128, and it is formed in axially extended feeding gallery between the outer surface of interior axle 112 and the internal surface of outer tube 114.This lubricating cavity 128 extends past pin 119.
Lubricating cavity 128 is formed by the pre-qualified play between the outer surface and the internal surface of outer tube 114 of interior axle 112.
In use, pressure oil is injected into concentric camshaft 110 and flows through lubricating cavity 128 to leave through cotter way 130, and described cotter way is formed immediately below the bearing journal of second group of cam 118, in outer tube 114.
Therefore, the interface between interior axle 112 and outer tube 114 and the bearing journal of second group of cam 118 are all by sufficient lubrication.
Camshaft device 100 also comprises the driving flange 132 with flange part 134 and tubular portion 136.Tubular portion 136 has the internal diameter corresponding to outer tube 114 external diameter, thus drives flange 132 to be mounted to the end portion 138 of outer tube 114 to rotate with this outer tube.
A part for cylinder head 121 is machined as the region of the internal diameter 140 with increase, and it is used for limiting the both sides in chamber holding rolling bearing 142.The other both sides of described bearing bore are limited by the outer surface of tubular portion 136 and the radial surface of flange part 134.The rolling bearing 142 comprising the rolling bearing component 144 remained within bearing housing 146 is pressed into bearing bore and is assembled to the surface of the internal diameter 140 of this increase.
Rolling bearing component 144 has radial internal clearance, and it is less than the pre-qualified radial internal clearance between perforate 120 and the outer surface of outer tube 144.Which ensure that whole camshaft load is at least born primarily of described bearing, instead of partly shared by described oil supply mechanism.
Concentric camshaft device 100 also comprises the first sealing 148 and the second sealing 150, and it is used as the sealing between the outer surface and the perforate 120 of cylinder head portion 121 of outer tube 114.
Described first and second sealings 148 and 150 are ring-like or the sealing of O ring, it is arranged in seal groove, outer surface periphery around outer tube 114, the every side at oil groove 126 form a seal groove, to prevent the less desirable oil of institute from overflowing from the play of the interface formation of the outer surface of outer tube 114 and perforate 120.Which ensure that oil enters radial hole 124 from groove 126.
Third and fourth sealing 152,154 is arranged on the relative two ends of lubricating cavity 128, and between the outer surface and the internal surface of outer tube 114 of interior axle 112.Third and fourth sealing 152,154 is ring-like or the sealing of O ring, and it is in place in seal groove, and described seal groove is formed around the outer surface periphery of interior axle 112 and oil is remained within lubricating cavity 128.
Second group of rolling bearing 156 is arranged around outer tube 114 at the opposite end place away from cylinder head portion 121 of concentric camshaft 110.
Embodiment shown in Figure 3 is from the different of the embodiment in Fig. 2, second embodiment has the independent oil supply lasso 256 formed, but not the oil groove (126 in Fig. 2) arranged around outer tube (114 in Fig. 2) periphery, this oil supply lasso is mounted to outer tube 214 to rotate with this outer tube and in fact to form a part for this outer tube.Oil groove 226 is arranged around the periphery of oil supply lasso 256, and is arranged to the oil received from oil supply mechanism 220, and described oil supply mechanism is arranged in a part for cylinder head 221.Oil groove 226 communicates with the isolated radial hole 258 of multiple circumference, and described radial hole extends through the wall of oil supply lasso 256.
The radial hole 258 of described lasso 256 is aimed at radial hole 224 radial direction be arranged in outer tube 214, and oil is supplied to lubricating cavity 228 by radial hole in described outer tube as previously mentioned.Then described oil leaves lubricating cavity 228 by cotter way 230, and described cotter way is formed immediately below the bearing journal of second group of cam 218, in outer tube 214.
In addition, in the diameter of cylinder head perforate 220 and the first embodiment, difference is that it equals the external diameter of bearing housing 246.This device has by avoiding the needs of machining bearing bore and between processing period, has the advantage reduced costs.
Pre-qualified play is present between the outer surface of perforate 220 and lasso 256.Which ensure that whole camshaft load is suitably born by described bearing, instead of partly shared by described oil supply mechanism.
Camshaft axial thrust is also allowed to control according to this device of the second embodiment.The flange part 260 stretched out from the axial end portion of oil supply lasso 256 abuts the axial surface of cylinder head 221, to limit the axial displacement of this camshaft.
Described oil supply lasso also has control piece 262, to control the end float of rolling bearing 242.
First and second sealings 248,250 seal between the outer surface and the perforate 220 of cylinder head portion 221 of lasso 256.
Described first and second sealings 248,250 are ring-like or the sealing of O ring, it is arranged in seal groove, outer surface periphery around lasso 256, the every side at oil groove 226 form described seal groove, so as to prevent less desirable oil overflow from the play that the interface of lasso 256 outer surface and perforate 220 is formed.Which ensure that oil passes into radial hole 258 from groove 226.
Described first and second sealings 248,250 are arranged on the needs eliminating in lasso 256 and form groove in outer tube 214, and therefore advantageously allow described camshaft to maintain its bulk strength.
Third and fourth sealing 252,254 is for the object identical with 154 with sealing 152 in a first embodiment.
The third embodiment of the present invention, as shown in Figure 4, comprises the second oil supply mechanism 364 in the part being arranged on cylinder head 321.This second oil supply mechanism 364 is used for camshaft phaser fuel supply chamber 366 supply pressure oil, and to be used in conjunction with phase discriminator, this phase discriminator has the guiding valve of the one for controlling this camshaft phase.
Second oil groove 368 is arranged around the periphery of oil supply lasso 356, and is arranged to the oil received from the second oil supply mechanism 364.Second oil groove 368 communicates with isolated second radial hole 370 of multiple circumference, and described radial hole extends through the wall of oil supply lasso 356.
Second lasso radial hole 370 is aimed at the isolated second outer tube radial hole 373 of multiple circumference, and described second outer tube radial hole is communicated with phase discriminator fuel supply chamber 366 fluid, to provide the pressure oil from the second oil supply mechanism 364 to this chamber.
5th sealing 372 is arranged in the seal groove extended around the periphery of lasso 356 circumference, thus the second oil groove 368 is arranged between the first sealing 350 and the 5th sealing 372.Again, the 5th sealing 372 is ring-like or the sealing of O ring.
Should understand, many oil supply mechanisms can be arranged in same camshaft device needs the standard cams axle phase discriminator in two supply/loops or the twin cam shaft phase discriminator in needs four supply/loops with adaptation.
Fig. 5 and Fig. 6 illustrates the 4th embodiment of concentric camshaft device 400, and this concentric camshaft device has feature similar to the aforementioned embodiment.In addition, Fig. 5 and Fig. 6 shows the hydraulic cam phase discriminator 474 be arranged in cylinder head 421.Be different from and use two independently oil supply mechanisms described by the 3rd embodiment, use single oil supply mechanism 420 in this embodiment, oil to be injected both concentric camshaft 410 and phase discriminator 474.
Described by about previous embodiment, oil supply mechanism 420 extends into lasso oil groove 426, and multiple radial hole 458 extends through lasso 456 from this oil groove and aims at the radial hole 424 extending diametrically through outer tube 414.
Outer tube radial hole 424 fluid flow communication extends into oil dispenser 480, and this oil dispenser 480 comprises camshaft oil dispenser 482 and phase discriminator oil dispenser 484.
Camshaft oil dispenser 482 has multiple camshaft fuel feeding path 486, and they are communicated with to its fuel feeding with lubricating cavity 428 fluid.As mentioned above, lubricating cavity 428 feed oil passes through cotter way 430, to lubricate the bearing journal of second group of cam 418.
Phase discriminator oil dispenser 484 has multiple phase discriminator fuel feeding path 488, and they are communicated with to supply pressure oil to it with phase discriminator fuel supply chamber 466 fluid.
Camshaft oil dispenser 482 also comprises cam shafting oil current-limiting mechanism 490 (or alternatively this can be small bore), to control and to balance the relative oily flow entering described camshaft and phase discriminator.
One-way valve 492 can be sentenced the oily flow of control and prevents oil extraction from phase discriminator when an engine is stopped by the feed mechanism at phase discriminator or camshaft in place.
Fig. 6 provides the alternative cross sectional view of the oil supply boring 494 illustrated for overall guiding valve 496.

Claims (11)

1. a concentric camshaft device, it comprises interior axle (' 12), around this interior axle (' 12) arranged concentric and the outer tube (' 14) be supported on rotationally in cylinder head (' 21), be mounted to outer tube with first group of salient angle (' 16) of rotating with this outer tube (' 14), be supported on this outer tube (' 14) rotationally by bearing journal to go up and the second group of salient angle (' 18) be connected with this interior axle (' 12) to rotate with this interior axle, be arranged on the rolling bearing (' 42) between this outer tube (' 14) and this cylinder head, and for supplying oil to lubricate oil supply mechanism (' 22 of the described bearing journal of this second group of camshaft lobe (' 18), ' 28), wherein at least partly oil supply mechanism by between the outer surface (' 20) and the internal surface of cylinder head (' 21) of this outer tube (' 14) and axial end portion is sealed (' 48, ' 50) radial internal clearance limit, thus the load of this camshaft on all larger than any radial internal clearance at this rolling bearing (' 42) place of this radial internal clearance is at least born primarily of this rolling bearing (' 42).
2. concentric camshaft device according to claim 1, the described radial internal clearance wherein between described outer tube and described cylinder head is by means of the first seal ring (' 48) and the second seal ring (' 50) sealing.
3. concentric camshaft device according to claim 1 and 2, wherein this outer tube (214) comprises the oil supply lasso (256) formed separately, its outer surface being fixedly installed to this outer tube (214) to rotate with it, the outer surface of this oil supply lasso (256) be radial internal clearance because forming this oil supply mechanism and with the isolated surface of internal surface of this cylinder head (' 21).
4. concentric camshaft device according to claim 3, wherein the diameter of the outer surface of this oil supply lasso (256) equals the external diameter of this rolling bearing (' 42) substantially.
5. the concentric camshaft device according to claim 3 or 4, wherein this oil supply lasso (256) is used for limiting the axial displacement of this rolling bearing (' 42).
6. the concentric camshaft device according to any one of claim 3 to 5, wherein this oil supply lasso (256) is also used for limiting the displacement of outer tube relative to this cylinder head of this camshaft.
7. concentric camshaft device according to any one of claim 1 to 6, it comprises multiple independently oil supply mechanism, and they are limited by the play between this camshaft tube and this cylinder head, and these oil supply mechanisms are by sealing spaced (Fig. 4).
8. concentric camshaft device according to any one of claim 1 to 7, it also comprises camshaft phaser and can operate with the phase discriminator oil supply mechanism (' 66) to this camshaft phaser fuel feeding.
9. concentric camshaft device according to claim 8, wherein this phase discriminator oil supply mechanism is configured to by this camshaft oil feeder at least partly.
10. concentric camshaft device according to claim 8 or claim 9, it also comprises phase discriminator current-limiting mechanism, its can operate to control oily flow in this phase discriminator oil supply mechanism and direction at least one of them.
11. concentric camshaft devices according to any one of claim 1 to 10, it also comprises camshaft current-limiting mechanism, and it can operate to control the oily flow in this camshaft oil supply mechanism.
CN201380036920.2A 2012-07-17 2013-07-12 Concentric camshaft device Active CN104428497B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB1212683.5A GB2504100A (en) 2012-07-17 2012-07-17 A concentric camshaft supported by roller bearings
GB1212683.5 2012-07-17
PCT/IB2013/055764 WO2014013409A2 (en) 2012-07-17 2013-07-12 A concentric camshaft arrangement

Publications (2)

Publication Number Publication Date
CN104428497A true CN104428497A (en) 2015-03-18
CN104428497B CN104428497B (en) 2017-06-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN201380036920.2A Active CN104428497B (en) 2012-07-17 2013-07-12 Concentric camshaft device

Country Status (5)

Country Link
US (1) US20150192043A1 (en)
EP (1) EP2875217B1 (en)
CN (1) CN104428497B (en)
GB (1) GB2504100A (en)
WO (1) WO2014013409A2 (en)

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CN109312636A (en) * 2016-05-23 2019-02-05 蒂森克虏伯普利斯坦技术中心股份公司 The system being made of camshaft and camshaft sleeve

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CN104428497B (en) 2017-06-13
EP2875217B1 (en) 2016-03-02

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