GB2504100A - A concentric camshaft supported by roller bearings - Google Patents

A concentric camshaft supported by roller bearings Download PDF

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Publication number
GB2504100A
GB2504100A GB1212683.5A GB201212683A GB2504100A GB 2504100 A GB2504100 A GB 2504100A GB 201212683 A GB201212683 A GB 201212683A GB 2504100 A GB2504100 A GB 2504100A
Authority
GB
United Kingdom
Prior art keywords
camshaft
oil feed
oil
outer tube
concentric
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.)
Withdrawn
Application number
GB1212683.5A
Other versions
GB201212683D0 (en
Inventor
Ian Methley
Nicholas James Lawrence
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
Original Assignee
Mechadyne International Ltd
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 Mechadyne International Ltd filed Critical Mechadyne International Ltd
Priority to GB1212683.5A priority Critical patent/GB2504100A/en
Publication of GB201212683D0 publication Critical patent/GB201212683D0/en
Priority to PCT/IB2013/055764 priority patent/WO2014013409A2/en
Priority to EP13779347.7A priority patent/EP2875217B1/en
Priority to CN201380036920.2A priority patent/CN104428497B/en
Priority to US14/412,716 priority patent/US20150192043A1/en
Publication of GB2504100A publication Critical patent/GB2504100A/en
Withdrawn legal-status Critical Current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
    • F01L1/02—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
    • 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
    • F01L1/34—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

Abstract

A concentric camshaft arrangement comprises an inner shaft 112 and an outer tube 114, concentrically arranged with the inner shaft and operable to rotate relative to a cylinder head 121. A first set of lobes 116 is fixed to the outer tube for rotation therewith. A second set of lobes 118 is attached to the inner shaft for rotation therewith and relative to the outer tube. Rolling bearings 144 are arranged in a housing and have a radial clearance. A camshaft oil feed 122 for supplying oil for lubrication of the camshaft is defined by an oil feed clearance between the outer surface of the outer tube 114 and an inner surface of the cylinder head 121 and wherein the oil feed radial clearance is greater than the rolling bearing radial clearance. This arrangement ensures that all the camshaft loads are supported by the bearings and not shared by the oil feed.

Description

A CONCENTRIC CAMSRAFT ARRANGEMENT
Field of the invention
The presenc invention relates to concentric camshaft arrangements and particularly to ccncentric camshaft arrangements which use roller bearings to support the loads of the camshaft. Roller bearing elements can, for example, comprise balls, cylindrical rollers or needle rollers.
Background of the invention
Known concentric camshafts have an inner shaft and an outer tube that are rotatable relative to one another. A first set of cams are fixed for rotation with the outer tube and a second sec of cams are mounted on bearing journals on the outer tube and connected for rotation with the inner shaft.
Such known concentric camshafts are typically supported in the engine using hydrodynamic bearings to allow the camshaft to rotate within the engine.
It is desirable in the automotive industry to minimise frictional losses for improved fuel consumption and reduced C02 emissions.
It is therefore attractive to use low friction bearings, such as, for example, rolling element bearings, to support the loads of concentric camshafts arrangements, rather than traditional hydrodynamic bearings. Rolling element bearings are advantageous as they can offer significant frictional benefit, especially at low engine speed. Furthermore, rolling element bearings reguire very little in the way of an oil supply. Therefore, the oil pump can be reduced in size, potentially reducing losses further.
However, use of rolling element bearings presents a problem in that the bearing journal surfaces of the moving cam lobes on a concentric camshaft require an oil feed to reduce friction and to prevent wear between the moving lobe journal bearings and the camshaft tube outer surface. If roller bearings are used to support the loads of known concentric camshaft arrangements, the conventional design of providing an oil feed via one or mcre of the camshaft's hydrodynamic bearing journals is no longer possible and an alternative oil feed is required to lubricate the journal bearings of the second set of cams.
Object of the invention Tt is therefore desirable in the automotive industry for there to be an improved concentric camshaft arrangement which overcomes the problems associated with known arrangomonts.
Summary of the invention
According no the present invention there is provided a concentric camshaft arrangement comprising an inner shaft, an outer tube, concentrically arranged with the inner shaft and operable to rotate relative to a cylinder head, a first set of lobes fixed to the outer tube for rotation therewith, a second set of lobes attached to the inner shaft for rotation therewith and relative to the outer tube, the second set of lobes each having a bearing journal on the outer surface of the tube, rolling bearings arranged in a housing and having a radial clearance, the rolling bearing being operable no support the loads of the camshaft, and a camshaft oil feed for supplying oil for lubrication of the camshaft, wherein at least part of the camshaft oil feed is defined by an oil feed clearance between the outer surface of the outer tube and an inner surface of the cylinder head and wherein the oil feed clearance is greater than the rolling bearing radial olearance.
The concentric camshaft arrangement advantageously further comprises sealing means.
The sealing means advantageously comprises a first and second seal each providing a seal between the outer surface of the outer tube and the inner surface of the cylinder head.
Alternatively, the outer tube advantageously comprises an oil feed ring fixed around the cuter circumference thereof for rotation therewith, the oil feed ring being interposed between the outer surface of the cuter tube and the inner surface of the cylinder head.
Tho outor ring advantagoously comprisos an outor surface on which a first and second seal are disposed to provide a seal between the outer surface of the outer ring and the inner surface of the cylinder head.
The diameter of the interface between the outer surface of the outer ring and the inner surface of the cylinder head is advantageously substantially equal to the outer diameter of the roller bearing housing.
The outer ring is advantageously operable to provide at least partial position control for the rolling bearings.
The oil feed ring is advantageously operable to provide at least partial axial positioning, or thrust control, of the camshaft relative to the cylinder head.
The camshaft arrangement advantageously comprises a plurality of discrete oil feeds separated by seals.
The sealing means may further comprise a third seal providing a seal between the cuter surface of the inner shaft and the inner surface of the outer tube.
The concenoric camshaft arrangement may further comprise a camshaft phaser and advantageously a phaser oil feed operable to supply oil to the camshaft phaser.
At least part of the phaser oil feed is advantageously formed from the camshaft oil feed The concencric camshaft arrangement advantageously further comprises a phaser flow restrictor operable to control the oil flow rate and/or direction in the camshaft phaser oil feed.
The concenoric camshaft arrangement advantageously furthor comprisos a camshaft flow rostrictor oporablc to control the oil flow rate in the camshaft oil feed.
A camshaft flow restrictor is particularly advantageous if it is joined with a high flow oil feed for a phaser because the moving cam lobes only reguire a relatively small amount of lubrication.
Brief description of the drawings
The presenc invention will now be described further, by way of example, with reference to the following drawings, in which: Figure 1 is a cross section drawing through the longitudinal axis of a concentric camshaft assembly
according ro the prior art;
Figure 2 is a cross section drawing through the longitudinal axis of a concentric camshaft assembly according no a first embodiment of the present invention; Figure 3 is a cross section drawing through the longitudinal axis of a concentric camshaft assembly according no a second embodiment of the present invention; Figure 4 is a cross section drawing through the longitudinal axis of a concentric camshaft assembly according no a third embodiment of the present invention; Figure 5 is a cross section drawing through the longitudinal axis of a concentric camshaft assembly according no a fourth embodiment of the present invention; and Figure 6 is an alternative cross section view through the longitudinal axis of a concentric camshaft assembly of Figure 5.
Detailed description of the embodiments
Referring no Figure 1, a known concentric camshaft arrangement 10, according to the prior art, has an inner shaft 12 and an outer tube 14. 7 first set of cams 16 are fixed for rotation with the outer tube 14 and a second set of cams 18 are rotatably mounted on bearing journals on the outer tube 14 and connected for rotation with the inner shaft 12.
Typically, an oil feed 20 is provided in one or more of the camshaft hydrodynamic journal bearings 22 and formed from radial holes 24, in the outer tube 14, in conjunction with annular grooves 26 in the journal bearing 22.
Pressurised oil is fed into the internals of the concentric camshaft arrangement 10 and is guided along an oil feed path 28 to exit through pin slots 30 formed in the outer tube 14 directly under the bearing journals of the second set of cams 18.
Referring no Figure 2, a concentric camshaft arrangement 100, according to a first embodiment of the present invention, comprises a concentric camshaft 110 having an inner shaft 112 and an outer tube 114. A first set of cams 116 are fixed for rotation with the outer tube 114 and a second sec of cams 118 are rotatably mounted on bearing journals on the outer tube 114 and connected to the inner shaft 112, with pins 119, for rotation therewith.
The concencric camshaft 110 is co-axially arranged within a bore 120 of the cylinder head 121, such that a predefined clearance exists between the bore 120 and the external surface of the outer tube 114.
A camshaft oil feed 122 is formed in a portion of the cylinder head 121. The camshaft oil feed 122 extends into a groove 124, which is formed in and extends around the circumforonco of tho outor surfaco of tho outor tubo 114. A plurality of circumferentially spaced apart radial holes 128 extend radially inwards from the groove 124 through the wall of the outer tube 114.
The radial holes 126 extend into a lubricating cavity 128 which forms an oil feed path extending longitudinally along the interface between the outer surface of the inner shaft 112 and the inner surface of the outer tube 114. The lubricating cavity 128 extends past the pins 119.
The lubricating cavity 128 has a predetermined clearance between the outer surface of the inner shaft 112 and the inner surface of the outer tube 114.
In use, pressurised oil is fed into the internals of the concentric camshaft arrangement 100 and through the lubrication cavity 128 and exits through pin slots 130, formed in the outer tube 114, directly under the bearing journals of the second set of cams 118.
Accordingly, the interface between the inner shaft 112 and the outer tube 114 and the bearing journals of the second set of cams 118 are adequately lubricated.
The camshaft arrangement 100 further comprises a drive flange 132 having a flange portion 134 and a tubular portion 136. The tubular portion 136 has an internal diameter to correspond to the external diameter of the outer tube 114 such that the drive flange 132 is fixed to an end portion 138 of the outer tube 114 for rotation therewith.
A portion of the cylinder head 121 is machined to provide a region of increased internal diameter 140, which is dimensioned no provide two sides of a bearing cavity 142.
Two other sides of the bearing cavity are defined by the external surface of the tubular portion 136 and a surface of the flange portion 134. Roller bearings 144 are housed in a boaring housing 146 which is disposod in tho bcaring cavity 142 and fixed to the surface of the increased internal diameter 140.
The roller bearings 144 have a predetermined bearing radial clearance which is less than the predetermined radial clearance between the bore 120 and the external surface of the outer tube 114. This is an important feature of the present invention as it ensures that all the camshaft loads are properly supported by the bearings rather than being partially shared by the oil feed.
The concencric camshaft arrangement 100 further comprises a first seal 148 and a second seal 150 operable to provide an oil seal between the outer surface of the outer tube 114 and the bore 120, of the cylinder head portion 121.
The first and second seals, 148 and 150, are ring-type or 0-ring type seals which are disposed in seal grooves formed each side of the oil groove 124 around the circumference of the external surface of the outer tube 114 such as to prevent undesirable migration of oil in the clearanoe formed at the interface of the outer surfaoe of the outer tube 114 and the bore 120. This facilitates the passage of oil from the groove 124 into the radial holes 126.
A third seal 152 and a fourth seal 154 are disposed at opposing ends of the lubrication cavity 128, and between the cuter surface of the inner shaft 112 and the inner surface of the outer tube 114. The third and forrth seals, 152 and 154, are ring-type or C-ring type seals which are positioned in seal grooves formed around the circumference of the outer surface of the inner shaft 112 and maintain the oil within the lubricating cavity 128.
A second set of rolling bearings 156 are disposed around thc outor tubc 114 at thc opposing cnd of tho concentric camshaft arrangement 100 relative to the cylinder head portion 121.
Referring no Figure 3, a second embodiment of a concentric camshaft arrangement 200, according to the present invention, has similar features to the first embodiment, as described above.
However, instead of having an oil groove (124 in Figure 2) disposed around the circumference of the outer tube (114 in Figure 2), the second embodiment has an oil feed sleeve 256 fixed to the outer tube 214 for rotation therewith. An oil groove 224 is dispcsed around the external circumference of the oil feed sleeve 256 and arranged to receive oil from an oil feed 222, disposed in a portion of the cylinder head 221. The oil groove 224 communicates with a plurality of circumferentially spaced apart radial holes 258, which extend through The wall of the oil feed sleeve 256.
The sleeve radial holes 258 are axially aligned with the outer tube radial holes 226, disposed in the outer tube 214, which, as described with reference to the first embodiment, in use provide oil into the lubrication cavity 228. The oil then exits the lubrication cavity 228 through pin slots 230, formed in the outer tube 214, directly under the bearing journals of the second set of cams 218.
The diameter of the cylinder head bore 220 also differs to that of the first embodiment in that it is equal to the external diameter of the bearing housing 246. This arrangement has the advantage of reducing machining costs during manufacture of the bearing cavity 242.
A predefined clearance exists between the bore 220 and the external surface of the sleeve 256. This is an important feature of the present invention as it ensures that all the camshaft loads arc properly supported by the bearings rather than being partially shared by the oil feed.
The arrangement according to the second embodiment also allows for camshaft axial thrust ccntrol features 260.
The oil feed sleeve also provides a control feature 262 to control the end float of the rolling bearing 244.
A first seal 248 and a second seal 250 are operable to provide an oil seal between the outer surface of the sleeve 256 and the bore 220, of the cylinder head portion 221.
The first and second seals, 248 and 250, are ring-type or 0-ring type seals which are disposed in seal grooves formed each side of the oil groove 224 around the circumference of the external surface of the sleeve 256 such as to prevent undesirable migration of oil in the clearance formed at the interface of the outer surface of the sleeve -10 - 256 and the bore 220. This faoilitates the passage of oil from the groove 224 into the radial holes 258.
Having the first and second seals, 248 and 250, disposed in the sleeve 256 eliminates the need for there to be grooves formed in the outer tube 214 and therefore advantageously allows the camshaft to maintain its integral strength.
Third and fourth seals 252 and 254 are operable in the same manner as The third and fourth seals in the first embodiment.
Referring o Figure 4, a third embodiment of a conoentrio camshaft arrangement 300, according to the present invention, has similar features to the second embodiment, as described above.
However, the third embodiment comprises a second oil feed 364 disposed in a portion of the cylinder head 321. The second oil feed 364 is operable to provide a pressurised oil supply to a camshaft phaser oil supply cavity 366 for use with a phaser having an integral spool valve for controlling the phase of the camshaft.
A second oil groove 368 is disposed around the external circumference of the oil feed sleeve 356 and arranged to receive oil from the second oil feed 364.The second oil groove 368 communicates with a plurality of circumferentially spaced apart second sleeve radial holes 370, which extend through the wall of the oil feed sleeve 356.
The second sleeve radial holes 370 are aligned with a plurality of circumferentially spaced apart second outer tube radial holes 372, which are in fluid communication with
-U -
the phaser oil supply cavity 366 tc prcvide pressurised oil from the second oil feed 364 thereto.
Feature number 372 is used for two different elements, fortunately there is no 172, 272 or 472 so either may be changed! A fifth seal 372 is disposed in a seal groove extending circumferentially around the external circumference of the sleeve 356, such that the second oil groove 368 is disposed between the first seal 350 and the fifth seal 372.
The fifth seal 372 is a ring-type or C-ring type seal.
It will be appreciated that a greater number of oil feeds may be provided in the same camshaft arrangement to accommodate either a standard camshaft phaser, which roguiros two foods/roturns, or a twin camshaft phasor, which reguires four feeds/returns.
Referring cc Figures 5 and 6, a fourth embodiment of a concentric camshaft arrangement 400, according to the present invention, has similar features to the embodiments described above.
Figures 5 and 6 additionally show a hydraulic cam phaser 474 installed in the cylinder head 421.
However, rather than using two separate oil feeds, as described in relation to the third embodiment, a single oil feed 478 is used to feed oil into both the concentric camshaft 410 and the phaser 474.
As described with reference to previous embodiments, the oil feed 478 extends into a sleeve oil groove 424 from which a pluralicy of sleeve radial holes 458 extend through -12 -the sleeve 456 and align with outer tube radial holes 426, which extend radially through the cuter tube 414.
The cuter rube radial holes 426 extend in fluid communication into an oil distributor 480 which comprises a camshaft oil distributor 482 and a phaser oil distributor 484.
The camshaft oil distributor 482 has a plurality of camshaft cil supply channels 486 which are in fluid communication with lubrication cavity 428 for supplying oil thereto. As previously described, the lubrication cavity 428 supplies oil through pin slots 430 for lubrication of the bearing journals of the second set of cams 418.
The phaser oil distributor 484 has a plurality of phaser oil supply channels 488 which are in fluid communication with phascr oil supply cavitios 466 to supply pressurised oil thereto.
The camshaft oil distributor 482 additional comprises a camshaft oil restrictor 490 (or alternatively this may be a small drilling) to control and balance the relative flow of oil into the camshaft and the phaser.
A one-way valve 492 can be positioned in either the feed to the phaser or camshaft to control oil flow and prevent oil drainage from the phaser when the engine is stopped.
Figure 6 provides an alternative section view showing oil feed drillings 494 for the integral spool valve 496.

Claims (14)

  1. -1_3 -CLAIMS1. A concentric camshaft arrangement comprising an inner shaft, an outer tube, concentrically arranged with the inner shaft and operable to rotate relative to a cylinder head, a first set of lobes fixed to the outer tube for rotation therewith, a second set of lobes attached to the inner shaft for rotation therewith and relative to the outer tube, the second set of lobes each having a bearing journal on the outer tube, rolling bearings arranged in a housing and having a radial clearance, the rolling bearing being operable to support the loads of the camshaft, and a camshaft oil feed for supplying oil for lubrication of the camshaft, wherein at least part of the camshaft oil feed is defined by an oil feed clearance between the outer surface of the outer tube and an inner surface of the cylinder head and wherein the oil feed radial clearance is greater than thc rolling bcaring radial clcarancc.
  2. 2. A concentric camshaft arrangement as claimed in claim 1, further comprising sealing means for the camshaft oil feed.
  3. 3. A concentric camshaft arrangement as claimed in claim 2, wherein the sealing means comprises a first and second seal each providing a seal between the outer surface of the outer tube and the inner surface of the cylinder head.
  4. 4. A concentric camshaft arrangement as claimed in claims 1 or 2, wherein the outer tube comprises an oil feed ring fixed around the outer circumference thereof for rotation therewith, the oil feed ring being interposed between the outer surface of the outer tube and the inner surface of the cylinder head.
    -1_4 -
  5. 5. A concentric camshaft arrangement as claimed in claim 4, wherein the oil feed ring comprises an outer surface on which a first and second seal are disposed to provide a seal between the outer surface of the oil feed ring and the inner surface of the cylinder head.
  6. 6. A concentric camshaft arrangement as claimed in claim 4 or 5, wherein the diameter of the interface between the outer surface of the oil feed ring and the inner surface of the cylinder head is substantially equal to the outer diameter of the roller bearing housing.
  7. 7. A concentric camshaft arrangement as claimed in claim 4 to 6, wherein the oil feed ring is operable to provide at leasu partial position control for the rolling bearings.
  8. 8. A conccntric camshaft arrangcmcnt as claimcd in claims 4 to 7, wherein the oil feed ring is operable to provide at leasn partial axial positioning, or thrust control, of the camshaft relative to the cylinder head.
  9. 9. A concentric camshaft arrangement as claimed in claims 2 to 8, comprising a plurality of discrete oil feeds separated by seals.
  10. 10. A concentric camshaft arrangement as claimed in any of the preceding claims, further comprising a camshaft phaser and a phaser oil feed operable to supply oil to the camshaft phaser.
  11. 11. A concentric camshaft arrangement as claimed in claim 10, wherein at least part of the phaser oil feed is formed from the camshaft oil feed.
    -1_5 -
  12. 12. A concentric camshaft arrangement as claimed in claim 10 or 11,further comprising a phaser flow restrictor operable to concrol at least one of the oil flow rate and direction in the phaser oil feed.
  13. 13. A concentric camshaft arrangement as claimed in any of the preceding claims, further ccmprising a camshaft flow restrictor operable to control the oil flow rate in the camshaft oil feed.
  14. 14. A concentric camshaft arrangement as substantially described herein with reference to Figures 2 to 6 of the accompanying drawings.
GB1212683.5A 2012-07-17 2012-07-17 A concentric camshaft supported by roller bearings Withdrawn GB2504100A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
GB1212683.5A GB2504100A (en) 2012-07-17 2012-07-17 A concentric camshaft supported by roller bearings
PCT/IB2013/055764 WO2014013409A2 (en) 2012-07-17 2013-07-12 A concentric camshaft arrangement
EP13779347.7A EP2875217B1 (en) 2012-07-17 2013-07-12 A concentric camshaft arrangement
CN201380036920.2A CN104428497B (en) 2012-07-17 2013-07-12 Concentric camshaft device
US14/412,716 US20150192043A1 (en) 2012-07-17 2013-07-12 Concentric camshaft arrangement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
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CN105351032A (en) * 2015-11-18 2016-02-24 重庆小康工业集团股份有限公司 Lubricating system for cam shaft

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DE102014214125A1 (en) * 2014-07-21 2016-01-21 Schaeffler Technologies AG & Co. KG Adjusting device for adjusting the timing of an internal combustion engine
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CN105351032A (en) * 2015-11-18 2016-02-24 重庆小康工业集团股份有限公司 Lubricating system for cam shaft

Also Published As

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WO2014013409A2 (en) 2014-01-23
GB201212683D0 (en) 2012-08-29
CN104428497A (en) 2015-03-18
EP2875217B1 (en) 2016-03-02
EP2875217A2 (en) 2015-05-27
WO2014013409A3 (en) 2014-03-06
US20150192043A1 (en) 2015-07-09
CN104428497B (en) 2017-06-13

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