EP1728976B1 - Brennkraftmaschine - Google Patents

Brennkraftmaschine Download PDF

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Publication number
EP1728976B1
EP1728976B1 EP06011297.6A EP06011297A EP1728976B1 EP 1728976 B1 EP1728976 B1 EP 1728976B1 EP 06011297 A EP06011297 A EP 06011297A EP 1728976 B1 EP1728976 B1 EP 1728976B1
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EP
European Patent Office
Prior art keywords
cam
rocker
shaft
cam carrier
combustion engine
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.)
Active
Application number
EP06011297.6A
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English (en)
French (fr)
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EP1728976A1 (de
Inventor
Tsunero Hamada
Yasuo Okamato
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Yamaha Motor Co Ltd
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Yamaha Motor Co Ltd
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Publication date
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Publication of EP1728976A1 publication Critical patent/EP1728976A1/de
Application granted granted Critical
Publication of EP1728976B1 publication Critical patent/EP1728976B1/de
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    • 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
    • F01L1/053—Camshafts overhead type
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/185—Overhead end-pivot rocking arms
    • 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
    • F01L1/053—Camshafts overhead type
    • F01L2001/0537—Double overhead camshafts [DOHC]

Definitions

  • the present invention relates to a multi-cylinder internal combustion engine according to the preamble of independent claim 1.
  • a multi-cylinder internal combustion engine can be taken from the prior art document US 4,793,297 .
  • Prior art document DE 195 04 636 A1 teaches a multi-cylinder internal combustion engine having a cylinder head with a camshaft casing being detachably mounted on the cylinder head.
  • Said camshaft casing is assembled as a one-piece element and supports the camshaft, which is provided as a one-piece element and controls the cam of each cylinder.
  • Said camshaft casing is provided with a plurality of bores arranged in the lower casing part.
  • One group of bores is arranged to coincide with one rocker shaft axis, while the other group of bores is arranged to coincide with the axis of a further rocker shaft.
  • Said two groups of bores receive two rocker shafts that extend through the entire cam carrier as a one-piece element, respectively.
  • the camshafts as well as the rocker shafts are provided as a one-piece element substantially extending along the entire cylinder head.
  • valve opening/closing of valves in a multi-cylinder internal combustion engine has been carried out by rotating a cam shaft having the same number of cams as the valves corresponding to cylinders such that cam noses of the cams depress rocker arms supported on the rocker shaft and further valve stems depressed by the rocker arms move up and down.
  • Inventions related to the multi-cylinder internal combustion engine provided with such a valve opening/closing mechanism include ones described in JP-A-2000-170506 and JP-B-2537205 .
  • JP-A-2000-170506 an intake side cam shaft and an exhaust side cam shaft are held by underlying lower cam holders and overlying upper cam holders therebetween and the lower cam holders in this condition are fastened to the cylinder head with first fastening members.
  • the upper cam holder and lower cam holder are fastened to each other at a position further inward than the first fastening members, with second fastening members each having a smaller diameter than the first fastening member.
  • a rocker arm holder is formed with a spark plug insert mouth, a rocker shaft is divided such that sub-divided rocker shafts are disposed overlapping each other in the axial direction of the cam shaft, and the rocker shaft is supported at its end on the rocker holder.
  • rocker shafts are configured such that they are supported on a plurality of holders (cam carriers) between adjacent holders (cam carriers). Therefore, when the holders (cam carriers) are assembled to the cylinder head, they need to be assembled in succession while rocker arms are fitted on the rocker shafts, causing complicated assembly work.
  • the support section for supporting the rocker shaft needs to be machined for each holder (cam carrier), the positional accuracy is difficult to secure.
  • the object of this invention is to provide a multi-cylinder internal combustion engine provided with cam carriers in which centering of rocker shafts requires less time, assembly to a cylinder head is easy, weight saving and size reduction of the rocker shaft are effected, and further, small-scale machining facilities can be used satisfactory for machining rocker shaft support sections of the cam carriers, and accuracy of the position, at which the rocker arm is supported, is easily secured.
  • an internal combustion engine in particular multi-cylinder internal combustion engine, comprising a cam shaft having at least one cam for depressing a rocker arm, and at least one cam carrier, said cam carrier being detachably mounted on a cylinder head, and being formed integrally with a cam shaft bearing portion and with a rocker shaft support section, said rocker shaft support section independently supporting a rocker shaft inserted in the rocker shaft support section.
  • the rocker shaft which is supported independently for each cam carrier, is inserted in the rocker shaft support section of the cam carrier and extends on both sides of or on one side of the cam shaft bearing section so as to be disposed parallel to the cam shaft, and wherein the rocker arm is supported for rotation by the rocker shaft on both sides of or on one side of the cam bearing section of the cam carrier.
  • the rocker shaft support section is provided extending on both sides of or on one side of the cam shaft bearing section in the same direction as the cam shaft and is formed with a slot for supporting the rocker arm, and wherein the rocker shaft support section is formed with a through-hole passing therethrough across the slot, and the rocker shaft is inserted in the through-hole.
  • cam carrier is mounted approximately directly above each cylinder, and all of the rocker arm supported on both sides of the cam shaft bearing section of the cam carrier, correspond to one cylinder.
  • the internal combustion engine is a multi-cylinder internal combustion engine, which includes cam shafts having a plurality of cams for depressing rocker arms formed thereon, a cam carrier for supporting the cam shafts, rocker shafts passing through a cam shaft bearing section formed in the cam carrier and extending on both sides thereof to be disposed parallel to the cam shafts, wherein the rocker arms are supported for rotation by the rocker shafts on both sides of the cam shaft bearing section of the cam shafts.
  • the cam carrier is mounted between adjacent cylinders, the rocker arm supported on one side of the cam shaft bearing section with respect to the cam shaft bearing section of the cam carrier is used for one of the adjacent cylinders, and the rocker arm supported on the other side of the cam shaft bearing section is used for the other of the adjacent cylinders.
  • the internal combustion engine further comprises a slipping-off prevention member mounted to the cam carrier for preventing the rocker shaft from slipping off the cam carrier.
  • the slipping-off prevention member is a collar inserted in a hole of an ignition plug insert section formed in the cam carrier, wherein a notch, with which part of the collar is engaged, is formed in the rocker shaft for the prevention of slipping-off of the rocker shaft.
  • the slipping-off prevention member is a collar inserted in a hole for a fastening member with the cylinder head formed in the cam carrier, wherein a notch, with which part of the collar is engaged, is formed in the rocker shaft for the prevention of slipping-off of the rocker shaft.
  • a linear expansion coefficient of the collar is different from a linear expansion coefficient of the cam carrier.
  • the cam carrier, the rocker shaft and the rocker arm have an oil passage supplied from the cylinder head, the rocker shaft is formed hollow inside and closed at both ends, and the notch is covered with the slipping-off prevention member.
  • the oil passage is constituted by first, second and third oil passages
  • the cam carrier is provided with the first oil passage
  • the rocker shaft is provided with the second oil passage
  • the rocker arm is provided with the third oil passage
  • an oil delivery port of the third oil passage is directed toward the contact face of the rocker arm with the cam
  • the rocker shaft is supported by the cam carrier without rotation
  • a communication area between the second oil passage and the third oil passage changes to be increased or decreased, with the cam depressing the rocker arm.
  • Embodiment 1 is shown in FIG. 1 through FIG. 6 .
  • a cylinder head 9 is disposed on a cylinder block (not shown), and a plurality of cam carriers 15 are provided on the cylinder head 9.
  • the cam carrier 15 supports an intake side cam shaft 11 and an exhaust side cam shaft 12 disposed parallel to each other, for rotation, as shown in FIG. 1 , and is provided with a cam shaft bearing section 15m formed with cam shaft bearing holes 15c, 15d for supporting these cam shafts 11, 12, as shown in FIG. 3 .
  • the intake side cam shaft 11 is formed with a plurality of cams 13a through 13h, and the exhaust side cam shaft 12 with a plurality of cams 14a through 14h. These pluralities of cams 13a through 13h, 14a through 14h are each adapted to depress their respective rocker arms 21, 22.
  • the cam carrier 15, as shown in FIG. 3 includes an upper holder 15a and a lower holder 15b, and the upper holder 15a is formed with upper recesses 15x, 15y and the lower holder 15b with lower recesses 15v, 15w so that the cam shafts 11, 12 can be held from above and below.
  • the upper recesses 15x, 15y, 15v, 15w the upper recess 15x and lower recess 15v are combined to form an intake side cam shaft bearing hole 15c, and the upper recess 15y and lower recess 15w are combined to form an exhaust side cam shaft bearing hole 15d.
  • the intake side cam shaft 11 is fitted in the intake side cam shaft bearing hole 15c formed in this way for rotation, and the exhaust side cam shaft 12 is fitted in the exhaust side cam shaft bearing hole 15d for rotation.
  • the cam shafts 11, 12 are supported by a cam shaft bearing section 15m having the cam shaft bearing holes 15c, 15d, as shown in FIG. 1 .
  • the lower holder 15b of the cam carrier 15 is formed with an intake side rocker shaft through-hole 15e and an exhaust side rocker shaft through-hole 15f in a rocker shaft support section 15n between the intake side cam shaft bearing section 15c and the exhaust side cam shaft bearing section 15d, as shown in FIG. 3 .
  • Rocker shafts 23, 24 are supported by the rocker shaft support section 15n, as shown in FIG. 1 , FIG. 2 and FIG. 4 .
  • the rocker shaft support section 15n is provided on both sides of the cam shaft bearing section 15m, extending in the same direction as the cam shafts 11, 12 (see FIG. 1 ).
  • the rocker shaft through-holes 15e, 15f is formed in the cam carrier 15 as through-holes passing through the rocker shaft support section 15n, and the rocker shafts 23, 24 are inserted in these rocker shaft through-holes 15e, 15f.
  • the lower holder 15b of the cam carrier 15 is formed with a hole 15g for an ignition plug insert section between the intake side rocker shaft through-hole 15e and the exhaust side rocker shaft through-hole 15f in the direction perpendicular to the axial direction of these shaft receiving sections 15e, 15f, as shown in FIG. 2 and FIG. 4 .
  • a cylindrical collar 16 is fitted In the hole 15g for the ignition plug insert section formed in the cam carrier 15, as shown in FIG. 1 , and an ignition plug 17 is disposed toward the cylinder head 9 through the collar 16.
  • the collar 16 is a member mounted to the cam carrier 15 and having the function of preventing the rocker shafts 23, 24 from slipping off the cam carrier 15.
  • the rocker shafts 23, 24 are formed with notches 23a, 24a with which parts of the collar 16 are engaged, for the prevention of their slipping-off.
  • the linear expansion coefficient of the collar 16 is different from that of the cam carrier 15 and it is larger than the linear expansion coefficient of the cam carrier 15 or smaller. This is because it is ensured that the collar 16 can be attached to and detached from the cam carrier 15 in a cold or a hot environment and the collar 16 is prevented from slipping off the cam carrier 15 at room temperature.
  • Such an arrangement improves handling properties of the cam carrier 15, as well as its assembling properties, and a slipping-off prevention condition can be realized of a small amount of play compared with slipping-off prevention devices such as bolts.
  • the cam carrier 15 is formed with slots 15h, as shown in FIG. 2 and FIG. 4 , and intake side rocker arms 21 and exhaust side rocker arms, 22 are inserted in these slots 15h.
  • the rocker arms 21, 22 are formed with shaft insert holes 21 a, 22a, respectively.
  • the intake side rocker shaft 23 With the intake side rocker arm 21 fitted in the slot 15h of the cam carrier 15, the intake side rocker shaft 23 is inserted in the intake side rocker shaft through-hole 15e and shaft insert hole 21 a.
  • the exhaust side rocker shaft 24 is inserted in the exhaust side rocker shaft through-hole 15f and shaft insert hole 22a.
  • the rocker shafts 23, 24 are supported independently for each cam carrier 15, pass through the rocker shaft support section 15n of the cam carrier 15 and extend on both sides of the cam shaft bearing section 15m so as to be disposed parallel to the cam shafts 11, 12.
  • the rocker arms 21, 22 are supported for rotation by the rocker shafts 23, 24 on both sides of the cam shaft bearing section 15m of the cam carrier 15.
  • each of the intake side cams 13a through 13h and exhaust side cams 14a through 14h depresses each of the intake side rocker arms 21 and exhaust side rocker arms 22 or releases the depression.
  • the cam carrier 15 is mounted approximately directly above each cylinder and configured such that all of the plurality of rocker arms 21, 22 supported on both sides of the cam shaft bearing section 15m of the cam carrier 15, correspond to one cylinder. That is, all valve faces 32 (see FIG. 3 ) corresponding to one cylinder are adapted to be opened/closed by the movement of the four rocker arms 21, 22 supported on the two rocker shafts 23, 24 of one cam carrier 15.
  • the upper holder 15a is formed with bolt holes 15j and the lower holder 15b with bolt holes 15k (seed FIG. 2 and FIG. 4 ).
  • bolts 25 are inserted in the bolt holes 15j of the upper holder 15a and bolt holes 15k of the lower holder 15b from above, as shown in FIG. 2 , so that the upper holder 15a and lower holder 15b are fastened.
  • Bolts 26 are inserted in bolt holes 15t of the lower holder 15b so that the cam carrier 15 is fixed to the cylinder head 9.
  • cam carrier 15 is formed with an oil passage 15p, shown in FIG. 2 and FIG. 3
  • the intake side rocker shaft 23 and exhaust side rocker shaft 24 are formed with oil passages 23p, 24p, respectively
  • the rocker arms 21, 22 are formed with oil passages 21 p, 22p, respectively.
  • the cam carrier 15, rocker shafts 23, 24 and rocker arms 21, 22 have oil passages 15p, 23p, 24p, 21 p, 22p for oil supplied from the cylinder head 9.
  • the rocker shafts 23, 24 are each formed hollow inside and closed at both ends. Further, the rocker shafts 23, 24 have notches 23a, 24a (see FIG. 4 ) covered with the collar 16 as a slipping-off prevention member, respectively.
  • the cam carrier 15 is provided with the first oil passage 15p, the rocker shafts 23, 24 with the second oil passages 23p, 24p, 23p-1, 23p-2, 24p-1, 24p-2 and the rocker arms 21, 22 with the third oil passages 21p, 22p.
  • Oil delivery ports 21q, 22q of the third oil passages 21 p, 22p are directed toward the contact faces of the rocker arms 21, 22 with the arms 13a through 13h, 14a through 14h, and the rocker shafts 23, 24 are supported on the cam carrier 15 without rotation.
  • the second oil passages in the rocker shafts 23, 24 are constituted by the oil passages 23p, 24p formed in the axial direction of the rocker shafts 23, 24; the oil passages 23p-1, 24p-1 formed in the direction perpendicular to the axial direction from the oil passages 23p, 24p and allowing oil in-flow from the first oil passage 15p; and the oil passages 23p-2, 24p-2 formed in the direction perpendicular to the axial direction from the oil passages 23p, 24p and allowing oil passage into the third oil passages 21 p, 22p.
  • the cylinder head 9 is provided below of the carriers 15 and a valve mechanism 31 is provided inside the cylinder head 9, as shown in FIG. 3 .
  • the valve mechanism 31 the top of a valve stem 33 having a valve face 32 is fixed with an upper retainer 34 and the top of a valve spring 33 is fixed to the upper retainer 34.
  • the valve spring 35 is disposed between the upper retainer 34 and a spring seat 36, and when the cams 13a through 13h, 14a through 14h depress the rocker arms 21, 22, the valve stems 33 are depressed by the rocker arms 21, 22 to be lowered so that the valve springs 35 are compressed. On the contrary, when the cams 13a through 13h, 14a through 14h release the depression of the rocker arms 21, 22, the contracted valve springs 35 expand so that the rocker arms 21, 22 are raised, as well as the rocker stems 33. As such, raising and lowering the valve stems 33 causes up and down movements of the valve faces 32.
  • valve stems 33 are raised and the valve faces 32 are also raised inside the unillustrated cylinder, so that no air will be taken in on the intake side and no exhaust gas will be exhausted on the exhaust side.
  • lubricating oil flows in from the first oil passage 15p in the cam carrier 15, and the lubricating oil flows through the second oil passages 23p, 24p in the rocker shafts 23, 24 and further through the third oil passages 21 p, 22p in the rocker arms 21, 22 to be delivered from delivery ports 21q, 22q.
  • the delivered lubricating oil is splashed on the contact faces of the cams 13a through 13h, 14a through 14h with the rocker arms 21, 22.
  • cam shafts 11, 12 having a plurality of cams 13a through 13h, 14a through 14h for depressing rocker arms 21, 22, formed thereon; a plurality of cam carriers 15 each formed integrally with cam shaft bearing section 15m for supporting the cam shafts 11, 12 and a rocker shaft support section 15n for supporting rocker shafts 23, 24; the rocker shafts 23, 24 being supported independently for each cam carrier 15, inserted in the rocker shaft support section 15n of the cam carrier 15 and extending on both sides of the cam shaft bearing section 15m so as to be disposed parallel to the cam shafts 11, 12; and the rocker arms 21, 22 being supported for rotation on the rocker shafts 23, 24 on both sides of the cam bearing section 15m of the cam carrier 15.
  • the positional accuracy of the holes for supporting rocker shafts 23, 24 to the cam shaft bearing section 15m can be secured easily, so that improvement in reliability due to improvement in the behavior of the valve drive system can be realized.
  • the scale of the mounting work of the rocker shafts 23, 24 to the arm carrier 15 can be decreased.
  • the rocker shaft support section 15n is provided extending on both sides of the cam shaft bearing section 15m in the same direction as the cam shafts 11, 12 and is formed with slots 15h for supporting the rocker arms 21, 22, the rocker shaft support section 15n is formed with through-holes 15e, 15f passing therethrough across the slots 15h, and the rocker shafts 23, 24 are inserted in the through-holes 15e, 15f. Therefore, since the rocker arms 21, 22 are held by the slots 15h on both sides in the vicinity of the shaft insert holes 21a, 22a, supporting rigidity of the rocker arms 21, 22 can be secured, as well as accurate movements of the rocker arms 21, 22, effecting higher rotation and improvement in reliability.
  • cam carrier 15 is mounted approximately directly above each cylinder, and all of the plurality of rocker arms 21, 22 supported on both sides of the cam shaft bearing section 15m of the cam carrier 15, correspond to one cylinder. If the cam carriers 15 are each provided between cylinders, additional cam carriers 15 need to be provided to support rocker arms 21, 22 disposed at both ends of the cam shafts 11, 12. On the contrary, such cam carriers 15 are dispensed with in this case, so that the number of parts can be decreased, as well as the number of types of parts.
  • a collar 16 is mounted to the cam carrier 15 to prevent the rocker shafts 23, 24 from slipping off the cam carrier 15. Therefore, the rocker shafts 23, 24 are fixed to the cam carrier 15 with the collar 16. Thus, the rocker arms 21, 22 can be prevented from slipping off during their rocking movement.
  • the collar 16 is a collar inserted in a hole 15g of an ignition plug insert section formed in the cam carrier 15, and notches 23a, 24a with which parts of the collar 16 are engaged, are formed in the rocker shaft 23, 24 for the prevention of slipping-off of the rocker shafts 23, 24. Therefore, by using the collar 16 in the hole 15g of the ignition plug insert section, the rocker shafts 23, 24 can be prevented from slipping off the cam carrier 15 within a narrow space.
  • the cam carrier 15, the rocker shafts 23, 24 and the rocker arms 21, 22 have passages 15p, 23p, 24p, 21p, 22p for oil supplied from the cylinder head 9, the rocker shaft 23, 24 are each formed hollow inside and closed at both ends, and the notches 23a, 24a are covered with the collar 16. Therefore, leakage of oil passing through the rocker shafts 23, 24 from the notches 23a, 24a can be suppressed.
  • This structure allows the hollow portions inside the rocker shaft 23, 24 to be increased in size, effecting weight saving of the rocker shafts 23, 24.
  • the cam carrier 15 is provided with the first oil passage 15p, the rocker shafts 23, 24 with the second oil passages 23p, 24p and the rocker arms 21, 22 with the third oil passages 21 p, 22p, oil delivery ports 21 q, 22q of the third oil passages 21 p, 22p are directed toward the contact faces of the rocker arms 21, 22 with the cams 13, 14, the rocker shafts 23, 24 are supported by the cam carrier without rotation, and communication areas between the second oil passages 23p, 24p and the third oil passages 21p, 22p change to be increased or decreased, with the cams 13, 14 depressing the rocker arms 21, 22.
  • rocker shafts 23, 24 also pass through the rocker shaft support section 15n
  • teaching of the invention is not limited to the foregoing embodiment if the rocker shafts 23, 24 can be supported. That is, it is possible that the rocker shafts 23, 24 are configured such that they pass at one ends through the rocker shaft support section 15n and don't pass at the other ends through the rocker shaft support section 15n, and both of the rocker shafts 23, 24 need not necessarily pass each at both ends through the rocker shaft support section 15n at both ends.
  • the rocker shafts 23, 24 are provided extending on both sides of the cam shaft bearing section 15m to be disposed parallel to the cam shafts 11, 12, the teaching of the invention is not limited to the foregoing embodiment. That is, the rocker shafts 23, 24 can be configured such that they extend only on one side of the cam shaft bearing section 15m.
  • the cam carrier 15 is configured so as to be provided with the cam shaft bearing section 15m extending only on one side thereof in plan view.
  • a cam carrier 215 is shown in FIG. 11 and FIG. 12 illustrating embodiment 3.
  • FIG. 6 and FIG. 7 show the embodiment 2.
  • same parts as in the embodiment 1 are designated by same reference numerals and description will not be repeated.
  • a cam carrier 115 in the embodiment 2 is different from the cam carrier 15 of the embodiment 1 in that as shown in FIG. 7 , rocker shaft through-holes 115e, 115f are formed in a rocker shaft support section 115n outside the cam shaft bearing section 115m to be disposed parallel to the cam shafts 11, 12, respectively, and as shown in FIG. 6 , the rocker arms 21, 22 rotate for up and down movement at the sides of an ignition plug insert hole 115g, respectively.
  • the cam carrier 115 includes a cam shaft bearing section 115m having cam shaft bearing holes 115c, 115d, and a rocker shaft support section 115n extending on both sides of the cam shaft bearing section 115m, and the rocker shaft support section 115n formed with shaft through-holes 115e, 115f for the rocker shafts 11, 12 to be inserted therein.
  • FIG. 8 through FIG. 11 show the embodiment 3.
  • same parts as in the embodiment 1 are designated by same reference numerals and description will be omitted.
  • a multi-cylinder internal combustion engine 200 in the embodiment 3 is different from the multi-cylinder internal combustion engine 10 of the embodiment 1 in the following aspects.
  • cam carriers 215 are each disposed between adjacent cylinders, rocker arms 21, 22 supported on a cam shaft bearing section 215m at one side with respect to the cam shaft bearing section 215m (see FIG. 10 ) having cam shaft bearing holes 215c, 215d of the cam carrier 215, are held by the inside walls of slots 215h formed in a rocker shaft support section 215n of the cam carrier 215 and used for one of the adjacent cylinders, and rocker arms 21, 22 supported on the cam shaft bearing section 215m at the other side are held by the slots 215h formed in the rocker shaft support section 215n of the cam carrier 215 and used for the other of the adjacent cylinders.
  • a collar 216 as a slipping-off prevention member is inserted in a hole 215s for a fastening member with the cylinder head 9 formed in the cam carrier 215.
  • rocker shafts 223, 224 are formed with notches 223a, 224a with which parts of the collars 216 are engaged, for the prevention of slipping-off of the rocker shafts 223, 224.
  • a cam carrier 220a (see FIG. 12(b) and FIG. 13(b) ) and a cam carrier 220b (see FIG. 12(a) and FIG. 13(a) ) are provided to support the rocker arms 21, 22 for cylinders provided at the left and right ends of the cylinder head 9.
  • These cam carriers 220a, 220b are each formed in the same shape as part of the cam carrier 215, but they have shapes each lacking the other part of the cam carrier 215. This is because when four valve mechanisms 31 are provided for each cylinder in a four-cylinder engine as shown in FIG.
  • rocker shafts 323, 324 are smaller in length than the rocker shafts 23, 24.
  • rocker shafts 423, 424 are smaller in length than the rocker shafts 23, 24, and each formed with the hole 215s for a fastening member in which the collar 216 is inserted.
  • the rocker shafts 423, 424 are also formed with notches 423a, 424a.
  • the cam carrier 215 are each mounted between adjacent cylinders, the rocker arms 21, 22 supported on one side of the cam shafts bearing section 215m with respect to the cam shaft bearing section 215m, are used for one of the adjacent cylinders, and the rocker arms 21, 22 supported on the other side of the cam shaft bearing section 215m are used for the other of the adjacent cylinders. Therefore, even in the multi-cylinder internal combustion engine 200 having an ignition plug 17 dispose above each cylinder, the cam carriers 215 can be configured such that they don't obstruct the disposition of ignition plugs 17. Thus, the degree of freedom in designing can be increased for the disposition of cam carriers 215 in the multi-cylinder internal combustion engine 200.
  • the collar 216 is inserted in the hole 215s formed in the cam carrier 215 for a fastening member with the cylinder head 9, the rocker shafts 223, 224 are formed with the notches 223a, 224a with which parts of the collars 216 are engaged, for the prevention of the slipping-off of the rocker shafts 223, 224. Therefore, by using the collar 216 inserted in the hole 215s for a fastening member with the cylinder head 9, the rocker shafts 223, 224 can be prevented from slipping off the cam carrier 215 within a narrow space.
  • an embodiment (first aspect) of a multi-cylinder internal combustion engine including: a cam shaft having at least one cam for depressing a rocker arm, formed thereon; at least one cam carrier formed integrally with a cam shaft bearing section for supporting the cam shaft and a rocker shaft support section for supporting a rocker shaft and mounted detachably on a cylinder head; the rocker shaft being supported independently for each cam carrier, inserted in the rocker shaft support section of the cam carrier and extending on both sides or on one side of the cam shaft bearing section so as to be disposed parallel to the cam shaft; and the rocker arm being supported for rotation by the rocker shaft on both sides or on one side of the cam bearing section of the cam carrier.
  • a further embodiment is directed to the arrangement of the first aspect, in which the rocker shaft support section is provided extending on both sides or on one side of the cam shaft bearing section in the same direction as the cam shaft and is formed with a slot for supporting the rocker arm, the rocker shaft support section is formed with a through-hole passing therethrough across the slot, and the rocker shaft is inserted in the through-hole.
  • a further embodiment is directed to the arrangement of the first or second aspect, in which the cam carrier is mounted approximately directly above each cylinder, and all of the rocker arm supported on both sides of the cam shaft bearing section of the cam carrier, correspond to one cylinder.
  • a further embodiment is directed to the arrangement of the first or second aspect, in which the cam carrier is mounted between adjacent cylinders, the rocker arm supported on one side of the cam shaft bearing section with respect to the cam shaft bearing section of the cam carrier is used for one of the adjacent cylinders, and the rocker arm supported on the other side of the cam shaft bearing section is used for the other of the adjacent cylinders.
  • a further embodiment is directed to the arrangement of one of the first to fourth aspects, further including a slipping-off prevention member mounted to the cam carrier for preventing the rocker shaft from slipping off the cam carrier.
  • a further embodiment is directed to the arrangement of the fifth aspect, in which the slipping-off prevention member is a collar inserted in a hole of an ignition plug insert section formed in the cam carrier, and a notch with which part of the collar is engaged, is formed in the rocker shaft for the prevention of slipping-off of the rocker shaft.
  • the slipping-off prevention member is a collar inserted in a hole of an ignition plug insert section formed in the cam carrier, and a notch with which part of the collar is engaged, is formed in the rocker shaft for the prevention of slipping-off of the rocker shaft.
  • a further embodiment is directed to the arrangement of the fifth aspect, in which the slipping-off prevention member is a collar inserted in a hole for a fastening member with the cylinder head formed in the cam carrier, and a notch with which part of the collar is engaged, is formed in the rocker shaft for the prevention of slipping-off of the rocker shaft.
  • the slipping-off prevention member is a collar inserted in a hole for a fastening member with the cylinder head formed in the cam carrier, and a notch with which part of the collar is engaged, is formed in the rocker shaft for the prevention of slipping-off of the rocker shaft.
  • a further embodiment is directed to the arrangement of the sixth or seventh aspect, in which the linear expansion coefficient of the collar is different from that of the cam carrier.
  • a further embodiment is directed to the arrangement of the sixth or seventh aspect, in which the cam carrier, the rocker shaft and the rocker arm have passages for oil supplied from the cylinder head, the rocker shaft is formed hollow inside and closed at both ends, and the notch is covered with the slipping-off prevention member.
  • a further embodiment is directed to the arrangement of the ninth aspect, in which the oil passage is constituted by a first through a third oil passages, the cam carrier is provided with the first oil passage, the rocker shaft is provided with the second oil passage, the rocker arm is provided with the third oil passage, an oil delivery port of the third oil passage is directed toward the contact face of the rocker arm with the cam, the rocker shaft is supported by the cam carrier without rotation, and communication area between the second oil passage and the third oil passage changes to be increased or decreased, with the cam depressing the rocker arm.
  • the oil passage is constituted by a first through a third oil passages
  • the cam carrier is provided with the first oil passage
  • the rocker shaft is provided with the second oil passage
  • the rocker arm is provided with the third oil passage
  • an oil delivery port of the third oil passage is directed toward the contact face of the rocker arm with the cam
  • the rocker shaft is supported by the cam carrier without rotation
  • communication area between the second oil passage and the third oil passage changes to be increased or decreased, with
  • a cam shaft having at least one cam for depressing a rocker arm, formed thereon; at least one cam carrier formed integrally with a cam shaft bearing section for supporting the cam shaft and a rocker shaft support section for supporting a rocker shaft and mounted detachably on a cylinder head; the rocker shaft being supported independently for each cam carrier, inserted in the rocker shaft support section of the cam carrier and extending on both sides or on one side of the cam shaft bearing section so as to be disposed parallel to the cam shaft; and the rocker arm being supported for rotation by the rocker shaft on both sides or on one side of the cam bearing section of the cam carrier.
  • the rocker shaft support section is provided extending on both sides or on one side of the cam shaft bearing section in the same direction as the cam shaft and is formed with a slot for supporting the rocker arm, the rocker shaft support section is formed with a through-hole passing therethrough across the slot, and the rocker shaft is inserted in the through-hole. Therefore, since the rocker arm is held by the slot 15h on both sides, supporting rigidity of the rocker arm can be secured, as well as accurate movements of the rocker arm, effecting higher rotation and improvement in reliability.
  • the cam carrier is mounted approximately directly above each cylinder, and all of the rocker arm supported on both sides of the cam shaft bearing section of the cam carrier, correspond to one cylinder. If cam carriers are each provided between cylinders, additional cam carriers need to be provided to support rocker arms disposed at both ends of the cam shaft. On the contrary, such cam carriers are dispensed with in this case, so that the number of parts can be decreased, as well as the number of types of parts.
  • the cam carrier is mounted between adjacent cylinders, the rocker arm supported on one side of the cam shaft bearing section with respect to the cam shaft bearing section of the cam carrier is used for one of the adjacent cylinders, and the rocker arm supported on the other side of the cam shaft bearing section is used for the other of the adjacent cylinders. Therefore, in the case of a multi-cylinder internal combustion engine having an ignition plug disposed above each cylinder, cam carriers can be configured such that they doesn't obstruct proper disposition of the ignition plugs. Thus, the degree of freedom in designing can be increased for the disposition of cam carriers in the multi-cylinder internal combustion engine.
  • a slipping-off prevention member is mounted to the cam carrier to prevent the rocker shaft from slipping off the cam carrier. Therefore, the rocker shaft is fixed to the cam carrier with the slipping-off prevention member. Thus, the rocker arm can be prevented from slipping off during its rocking movement.
  • the slipping-off prevention member is a collar inserted in a hole of an ignition plug insert section formed in the cam carrier, and a notch with which part of the collar is engaged, is formed in the rocker shaft for the prevention of slipping-off of the rocker shaft. Therefore, by using the collar in the hole of the ignition plug insert section, the rocker shaft can be prevented from slipping off the cam carrier within a narrow space.
  • the slipping-off prevention member is a collar inserted in a hole for a fastening member with the cylinder head formed in the cam carrier, and a notch with which part of the collar is engaged, is formed in the rocker shaft for the prevention of slipping-off of the rocker shaft. Therefore, by using the collar inserted in the hole for a fastening member with the cylinder head, the rocker shaft can be prevented from slipping off the cam carrier within a narrow space.
  • the linear expansion coefficient of the collar is different from that of the cam carrier. That is, the linear expansion coefficient of the collar is larger than that of the cam carrier or smaller. Therefore, the collar can be attached to and detached from the cam carrier in a cold or hot environment and it doesn't slip off the cam carrier at room temperature. Thus, handling properties of the cam carrier can be improved, as well as its assembling properties, and a slipping-off prevention condition can be realized of a small amount of play compared with slipping-off devices such as bolts.
  • the cam carrier, the rocker shaft and the rocker arm have a passage for oil supplied from the cylinder head, the rocker shaft is formed hollow inside and closed at both ends, and the notch is covered with the slipping-off prevention member. Therefore, leakage of oil passing through the rocker shaft from the notch can be suppressed.
  • This structure allows the hollow section inside the rocker shaft to be increased in size, effecting weight saving of the rocker shaft.
  • the cam carrier is provided with the first oil passage
  • the rocker shaft is provided with the second oil passage
  • the rocker arm is provided with the third oil passage
  • an oil delivery port of the third oil passage is directed toward the contact face of the rocker arm with the cam
  • the rocker shaft is supported by the cam carrier without rotation
  • communication area between the second oil passage and the third oil passage changes to be increased or decreased, with the cam depressing the rocker arm. Since, rotation of the rocker shaft is restricted at this time by the slipping-off prevention action of a small amount of play, change in the communication area can be set accurately. This causes oil to be delivered accurately and intermittently, allowing restriction of the oil flow. Therefore, a stirring loss due to delivered oil can be decreased, as well as the oil pump capacity, effecting reduction in the driving loss horsepower of the oil pump.
  • a multi-cylinder internal combustion engine 10 includes cam shafts 11, 12 having a plurality of cams 13a through 13h, 14a through 14h for depressing rocker arms 21, 22 formed thereon; a cam carrier 15 for supporting the cam shafts 11, 12; rocker shafts 23, 24 passing through a cam shaft bearing section 15m formed in the cam carrier 15 and extending on both sides thereof to be disposed parallel to the cam shafts 11, 12; and the rocker arms 21, 22 being supported for rotation by the rocker shafts 23, 24 on both sides of the cam shaft bearing section 15m of the cam shafts 11, 12.
  • a multi-cylinder internal combustion engine comprising: a cam shaft having at least one cam for depressing a rocker arm, formed thereon; at least one cam carrier formed integrally with a cam shaft bearing section for supporting the cam shaft and a rocker shaft support section for supporting a rocker shaft and mounted detachably on a cylinder head; the rocker shaft being supported independently for each cam carrier, inserted in the rocker shaft support section of the cam carrier and extending on both sides or on one side of the cam shaft bearing section so as to be disposed parallel to the cam shaft; and the rocker arm being supported for rotation by the rocker shaft on both sides or on one side of the cam bearing section of the cam carrier.
  • the rocker shaft support section is provided extending on both sides or on one side of the cam shaft bearing section in the same direction as the cam shaft and is formed with a slot for supporting the rocker arm, the rocker shaft support section is formed with a through-hole passing therethrough across the slot, and the rocker shaft is inserted in the through-hole.
  • the cam carrier is mounted between adjacent cylinders, the rocker arm supported on one side of the cam shaft bearing section with respect to the cam shaft bearing section of the cam carrier is used for one of the adjacent cylinders, and the rocker arm supported on the other side of the cam shaft bearing section is used for the other of the adjacent cylinders.
  • an embodiment of the multi-cylinder internal combustion engine further comprising a slipping-off prevention member mounted to the cam carrier for preventing the rocker shaft from slipping off the cam carrier.
  • the slipping-off prevention member is a collar inserted in a hole of an ignition plug insert section formed in the cam carrier, and a notch with which part of the collar is engaged, is formed in the rocker shaft for the prevention of slipping-off of the rocker shaft.
  • the slipping-off prevention member is a collar inserted in a hole for a fastening member with the cylinder head formed in the cam carrier, and a notch with which part of the collar is engaged, is formed in the rocker shaft for the prevention of slipping-off of the rocker shaft.
  • the cam carrier, the rocker shaft and the rocker arm have a passage for oil supplied from the cylinder head, the rocker shaft is formed hollow inside and closed at both ends, and the notch is covered with the slipping-off prevention member.
  • the oil passage is constituted by a first through a third oil passages
  • the cam carrier is provided with the first oil passage
  • the rocker shaft is provided with the second oil passage
  • the rocker arm is provided with the third oil passage
  • an oil delivery port of the third oil passage is directed toward the contact face of the rocker arm with the cam
  • the rocker shaft is supported by the cam carrier without rotation
  • communication area between the second oil passage and the third oil passage changes to be increased or decreased, with the cam depressing the rocker arm.

Claims (12)

  1. Mehrzylinder- Brennkraftmaschine, aufweisend eine Nockenwelle (11, 12), die Nocken zum Niederpressen eines Kipphebels (21, 22) hat, und eine Nockentrageinrichtung (15, 115, 215), die lösbar an einem Zylinderkopf (9) montiert ist, und die einstückig mit einem Nockenwellen- Lagerabschnitt (15m, 115m, 215m) und mit einem Kippwellen- Stützabschnitt (15n, 115n, 215n) gebildet ist, wobei der Kippwellen- Lagerabschnitt (15n, 115n, 215n) eine Kipphebelwelle (23, 24), eingesetzt in den Kippwellen- Lagerabschnitt (15n, 115n, 215n), lagert, wobei die Nockentrageinrichtung durch eine Mehrzahl von Nockenträgern (15, 115, 215), die lösbar und voneinander unabhängig an dem Zylinderkopf (9) montiert sind, gebildet ist,
    dadurch gekennzeichnet, dass jeder Nockenträger (15, 115, 215) die Kipphebelwelle (23, 24) unabhängig von den Kipphebelwellen (23, 24) von weiteren Nockenträgern (15, 115, 215) lagert.
  2. Mehrzylinder- Brennkraftmaschine nach Anspruch 1, dadurch gekennzeichnet, dass die Kipphebelwelle (23, 24), die unabhängig für jeden Nockenträger (15, 115, 215) gelagert ist, in den Kippwellen- Lagerabschnitt (15n, 115n, 215n) des Nockenträgers (15, 115, 215) eingesetzt ist und sich auf beiden Seiten von oder auf einer Seite des Nockenwellen- Lagerabschnittes (15m, 115m, 215m) erstreckt, um parallel zu der Nockenwelle (11, 12) angeordnet zu sein, und wobei der Kipphebel (21, 22) zum Drehen durch die Kipphebelwelle (23, 24) auf beiden Seiten von oder auf einer Seite des Nockenlagerabschnitt des Nockenträger (15, 115, 215) gelagert ist.
  3. Mehrzylinder- Brennkraftmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Kippwellen- Lagerabschnitt (15n, 115n, 215n) sich auf beiden Seiten von oder auf einer Seite des Nockenwellen- Lagerabschnitt (15m, 115m, 215m) in derselben Richtung wie die Nockenwelle (11, 12) erstreckend vorgesehen ist und mit einem Schlitz (15h, 215h) zum Lagern des Kipphebels (21, 22) gebildet ist und wobei der Kippwellen- Lagerabschnitt (15n, 115n, 215n) mit einer Durchgangsbohrung (15e, 115e, 215e), die quer durch den Schlitz (15h, 215h) hindurchgeht, gebildet ist und wobei die Kipphebelwelle (23, 24) in die Durchgangsbohrung (15e, 115e, 215e) eingesetzt ist.
  4. Mehrzylinder- Brennkraftmaschine nach einem der Ansprüche 1 oder 3, dadurch gekennzeichnet, dass der Nockenträger (15, 115, 215) annähernd direkt oberhalb jedes Zylinders montiert ist und alle der Kipphebel (21, 22), gelagert auf beiden Seiten des Nockenwellen- Lagerabschnittes (15m, 115m, 215m) des Nockenträgers (15, 115, 215), einem Zylinder angeordnet sind.
  5. Mehrzylinder- Brennkraftmaschine nach einem der Ansprüche 1 bis 4, gekennzeichnet durch Nockenwellen (11, 12) mit einer daran gebildeten Mehrzahl von Nocken (13a bis 13h und 14a bis 14h) zum Niederdrücken der Kipphebel (21, 22), einem Nockenträger (15, 115, 215) zum Lagern der Nockenwellen (11, 12), Kipphebelwellen (23, 24), die durch einen Nockenwellen- Lagerabschnitt (15m, 115m, 215m), gebildet in dem Nockenträger (15, 115, 215) hindurchgehen und sich auf beiden Seiten desselben erstrecken, um zu den Nockenwellen (11, 12) parallel angeordnet zu sein, wobei die Kipphebel (21, 22) zum Drehen durch die Kipphebelwellen (23, 24) auf beiden Seiten des Nockenwellen- Lagerabschnittes (15m, 115m, 215m) der Nockenwellen (11, 12) abgestützt werden.
  6. Mehrzylinder- Brennkraftmaschine nach einem der Ansprüche 1 oder 3, dadurch gekennzeichnet, dass der Nockenträger (15, 115, 215) zwischen benachbarten Zylindern montiert ist, der Kipphebel (21, 22), gelagert auf einer Seite des Nockenwellen- Lagerabschnittes (15m, 115m, 215m) in Bezug auf den Nockenwellen- Lagerabschnitt (15m, 115m, 215m) des Nockenträgers (15, 115, 215) für einen der benachbarten Zylinder verwendet wird und der Kipphebel (21, 22), gelagert auf der anderen Seite des Nockenwellen- Lagerabschnittes (15m, 115m, 215m), für den anderen der benachbarten Zylinder verwendet wird.
  7. Mehrzylinder- Brennkraftmaschine nach einem der Ansprüche 1 bis 6, gekennzeichnet durch ein Wegrutschverhinderungsteil (16, 216), montiert an dem Nockenträger (15, 215), um die Kipphebelwelle (23, 24) am Wegrutschen von dem Nockenträger (15, 215) zu hindern.
  8. Mehrzylinder- Brennkraftmaschine nach Anspruch 7, dadurch gekennzeichnet, dass das Wegrutschverhinderungsteil ein Kragen (16, 216) ist, eingesetzt in eine Bohrung eines Zündkerzen- Einsetzabschnittes, gebildet in dem Nockenträger (15, 215), wobei eine Kerbe (23a, 24a, 223a, 224a), mit der ein Teil des Kragens (16, 216) im Eingriff ist, in der Kipphebelwelle (23, 24) gebildet ist, um das Wegrutschen der Kipphebelwelle (23, 24) zu verhindern.
  9. Mehrzylinder- Brennkraftmaschine nach Anspruch 7, dadurch gekennzeichnet, dass das Wegrutschverhinderungsteil ein Kragen (16, 216) ist, eingesetzt in eine Bohrung für ein Befestigungsteil bei dem Zylinderkopf (9), gebildet in dem Nockenträger (15, 215), wobei eine Kerbe, mit der ein Teil des Kragens im Eingriff ist, in der Kipphebelwelle (23, 24) gebildet ist, um ein Wegrutschen der Kipphebeiwelle (23, 24) zu verhindern.
  10. Mehrzylinder- Brennkraftmaschine nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass ein linearer Ausdehnungskoeffizient des Kragens (16, 216) von einem linearen Ausdehnungskoeffizient des Nockenträgers (15, 215) verschieden ist.
  11. Mehrzylinder- Brennkraftmaschine nach einem der Ansprüche 8 bis 10, dadurch gekennzeichnet, dass der Nockenträger (15, 215), die Kipphebelwelle (23, 24) und der Kipphebel (21, 22) einen von dem Zylinderkopf (9) versorgten Ölkanal haben, die Kipphebelwelle (23, 24) im Inneren hohl ausgebildet und an beiden Enden geschlossen ist und die Kerbe (23a, 24a, 223a, 224a) mit dem Wegrutschverhinderungsteil abgedeckt ist.
  12. Mehrzylinder- Brennkraftmaschine nach Anspruch 11, dadurch gekennzeichnet, dass der Ölkanal durch erste, zweite und dritte Ölkanäle gebildet ist, wobei der Nockenträger (15, 115, 215) mit dem ersten Ölkanal versehen ist, die Kipphebelwelle (23, 24) mit dem zweiten Ölkanal versehen ist, der Kipphebel (21, 22) mit dem dritten Ölkanal versehen ist, wobei eine Ölzulieferöffnung des dritten Ölkanals in Richtung zu der Kontaktfläche des Kipphebels (21, 22) mit dem Nocken gerichtet ist, die Kipphebelwelle (23, 24) durch den Nockenträger (15, 215) ohne Drehung gelagert ist und sich ein Verbindungsbereich zwischen dem zweiten Ölkanal und dem dritten Ölkanal verändert, um vergrößert oder vermindert zu sein, wenn der Nocken den Kipphebel (11, 22) niederdrückt.
EP06011297.6A 2005-05-31 2006-05-31 Brennkraftmaschine Active EP1728976B1 (de)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11692503B2 (en) 2020-12-07 2023-07-04 Ford Global Technologies, Llc Methods and systems for an engine with removable camshaft carrier

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5139112B2 (ja) * 2008-02-19 2013-02-06 ヤマハ発動機株式会社 エンジン
US20130019472A1 (en) * 2011-07-20 2013-01-24 GM Global Technology Operations LLC Method of manufacturing a cam carrier with cam carrier bore machined apart from cylinder head and apparatus for same
EP3306065A4 (de) * 2015-05-25 2018-06-06 Nissan Motor Co., Ltd. Verbrennungsmotor
DE102015224440A1 (de) * 2015-12-07 2017-06-08 Mahle International Gmbh Zylinderkopfhaube
JP6839576B2 (ja) * 2017-03-21 2021-03-10 本田技研工業株式会社 Ｄｏｈｃ型内燃機関

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6127905U (ja) * 1984-07-25 1986-02-19 本田技研工業株式会社 Ｏｈｃ型内燃機関
DE3515348A1 (de) * 1985-04-27 1986-11-06 Klöckner-Humboldt-Deutz AG, 5000 Köln Hydraulische umsteuereinrichtung fuer einen ventiltrieb
JPS6318109A (ja) * 1986-07-09 1988-01-26 Honda Motor Co Ltd 内燃機関の動弁機構
JP2537205B2 (ja) 1986-07-09 1996-09-25 本田技研工業株式会社 内燃機関の動弁装置
US5070824A (en) * 1988-05-30 1991-12-10 Yamaha Hatsudoki Kabushiki Kaisha Combustion chamber and valve operating mechanism for multi-valve engine
EP0458341A1 (de) * 1990-05-24 1991-11-27 Mazda Motor Corporation Zylinderkopf eines Doppelnockenwellenmotors
DE19504637C2 (de) * 1995-02-13 2000-06-08 Daimler Chrysler Ag Anordnung zur Lagerung einer Nockenwelle und mehrerer Steuerelemente zur Gaswechselsteuerung an einer Brennkraftmaschine
DE19504636A1 (de) 1995-02-13 1996-08-22 Daimler Benz Ag Anordnung zur Lagerung der Steuerelemente zur Gaswechselsteuerung einer Brennkraftmaschine
JP2000170506A (ja) 1998-12-09 2000-06-20 Honda Motor Co Ltd 内燃機関の動弁系支持構造
KR20010037508A (ko) * 1999-10-18 2001-05-07 이계안 디오에치시 디젤 엔진

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11692503B2 (en) 2020-12-07 2023-07-04 Ford Global Technologies, Llc Methods and systems for an engine with removable camshaft carrier

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