US20140305397A1 - Camshaft support structure - Google Patents

Camshaft support structure Download PDF

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Publication number
US20140305397A1
US20140305397A1 US14/349,738 US201114349738A US2014305397A1 US 20140305397 A1 US20140305397 A1 US 20140305397A1 US 201114349738 A US201114349738 A US 201114349738A US 2014305397 A1 US2014305397 A1 US 2014305397A1
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US
United States
Prior art keywords
camshaft
support bases
cylinder head
support
internal combustion
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.)
Abandoned
Application number
US14/349,738
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English (en)
Inventor
Yoshinori Yanase
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.)
Toyota Motor Corp
Original Assignee
Toyota Motor Corp
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 Toyota Motor Corp filed Critical Toyota Motor Corp
Assigned to TOYOTA JIDOSHA KABUSHIKI KAISHA reassignment TOYOTA JIDOSHA KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Yanase, Yoshinori
Publication of US20140305397A1 publication Critical patent/US20140305397A1/en
Abandoned legal-status Critical Current

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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
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • 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
    • F01L1/02—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
    • F01L1/02—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 camshaft support structure that includes support bases, which are mounted on the cylinder head of an internal combustion engine and support camshafts to be freely rotational.
  • the weight of the internal combustion engine is reduced as compared to a structure in which an outer frame for connecting the support bases is provided, as in a ladder-frame camshaft housing, by the weight corresponding to the outer frame.
  • Patent Document 1 Japanese Laid-Open Patent Publication No. 2010-209796
  • the temperature of the cylinder head is increased by receiving heat of exhaust gas, causing the cylinder head to be thermally deformed. Since the support bases are arranged to abut against the cylinder head, the support bases are thermally deformed by receiving heat from the cylinder head. This deteriorates alignment of bearing portions, which are formed in the support bases and support the camshafts. As a result, problems may arise such as an increase in rotational sliding resistance of the camshafts.
  • the amount of heat that the support bases receive from the cylinder head is reduced as compared to the structure with the ladder-frame camshaft housing by the amount corresponding to the outer frame.
  • the thermal deformation amount of the support bases is thus reduced to some extent.
  • the invention is applied to an internal combustion engine in which the exhaust gas temperature is further increased such as an internal combustion engine provided with a forced-induction device, the amount of heat that the support bases receive from the cylinder head is further increased. In this case, there are limitations in favorably reducing deterioration in the alignment of the bearing portions of the support bases.
  • camshaft support structure that favorably reduces deterioration in the alignment of bearing portions of support bases, which support camshafts, due to engine operation.
  • a camshaft support structure mounted on a cylinder head of an internal combustion engine includes support bases for supporting a camshaft to be freely rotational.
  • the support bases are arranged apart from one another in an axial direction of the camshaft.
  • Each support base has a bearing portion, which supports the camshaft, and a through hole, which extends in the axial direction of the camshaft.
  • the through holes receive a rod, which restricts the bearing portions from being displaced from an arrangement position at which the bearing portions are located when the internal combustion engine is stopped and cold.
  • the bearing portions of the support bases mounted on the cylinder head of the internal combustion engine support the camshaft to be freely rotational. Since the support bases are arranged apart from one another in the axial direction of the camshaft, the contact area between the support bases and the cylinder head is reduced as compared to the structure with an outer frame for connecting the support bases, such as a ladder-frame camshaft housing. This reduces the amount of heat received from the cylinder head, thus reducing thermal deformation of the support bases caused by the received heat.
  • the support bases are restricted from being thermally deformed by the heat received from the cylinder head.
  • the rod is assembled to the cylinder head together with the support bases in a state in which the rod is inserted in the through holes.
  • the cylinder head is assembled to the cylinder block with head bolts.
  • the top surface of the cylinder head is slightly distorted from a flat state due to the axial tightening force of the head bolts. The rod is thus maintained in a state pressed by the inner walls of the through holes, and secured to the support bases.
  • the structure thus favorably reduces deterioration in the alignment of the bearing portions of the support bases, which support the camshaft, due to engine operation.
  • the rod is preferably made of material having higher rigidity than the support bases. According to this embodiment, thermal deformation of the support bases is reduced in an appropriate manner.
  • the rod may be made of stainless-steel, which has higher rigidity than the aluminum alloy.
  • each support base preferably includes a receiving member, which is mounted on the cylinder head and receives the camshaft, and a cap member, which is mounted on a top surface of the receiving member and forms the bearing portion together with the receiving member.
  • the through hole is preferably formed in the receiving member.
  • the support bases preferably receive both an exhaust camshaft and an intake camshaft, which each serve as the camshaft, and the through holes are preferably formed closer to the exhaust camshaft than to the intake camshaft.
  • the thermal deformation of the cylinder head is thus greater in the region closer to the exhaust camshaft.
  • the through holes in which the rod is inserted are formed closer to the exhaust camshaft than to the intake camshaft. That is, the rod is arranged close to the region of the receiving members of the support bases where the amount of heat received from the cylinder head is great and the degree of thermal deformation is great. The region of the support bases in the vicinity of the exhaust camshaft where the amount of heat received from the cylinder head is great is thus restricted from being thermally deformed in an appropriate manner.
  • the thermal deformation amount of the support bases caused by heat received from the cylinder head is great. Furthermore, in the internal combustion engine provided with a forced-induction device, since the pressure in the cylinders is higher than that without the forced-induction device, the cylinder head is significantly deformed by fluctuation of the pressure in the cylinders of the internal combustion engine. As a result, the deformation amount of the support bases mounted on the cylinder head is increased.
  • FIG. 1 is a plan view illustrating a planar structure of an internal combustion engine according to a first embodiment of the present invention as viewed from above an exhaust camshaft and an intake camshaft;
  • FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1 , illustrating a cross-sectional structure of the internal combustion engine
  • FIG. 3 is a side view schematically illustrating a side structure of the top surface of the cylinder head and the support bases mounted on the top surface in the longitudinal direction of the cylinder head.
  • a camshaft support structure of a double overhead camshaft (DOHC) inline 4-cylinder internal combustion engine according to one embodiment of the present invention will now be described with reference to FIGS. 1 to 3 .
  • the internal combustion engine of the present embodiment is provided with an exhaust driven forced-induction device.
  • FIG. 1 shows a planar structure of an internal combustion engine as viewed from above an exhaust camshaft and an intake camshaft.
  • FIG. 2 shows a cross-sectional structure of the internal combustion engine taken along line A-A of FIG. 1 .
  • a cylinder head 1 which is provided with a valve mechanism including exhaust valves and intake valves, is provided on the top surface of a cylinder block 2 as shown in FIG. 2 .
  • the cylinder block 2 and the cylinder head 1 are tightened with head bolts 3 in a known manner (see FIGS. 2 and 3 ).
  • An exhaust camshaft 5 provided with exhaust cams 51 for opening and closing the exhaust valves and an intake camshaft 6 provided with intake cams 61 for opening and closing the intake valves are arranged on a top surface 1 a of the cylinder head 1 to be parallel to each other. More specifically, five support bases 4 for supporting the camshafts 5 , 6 to be freely rotational are mounted on the top surface 1 a of the cylinder head 1 . Only one of the support bases 4 is shown in FIG. 2 .
  • the support bases 4 are arranged apart from one another in an axial direction L of the camshafts 5 , 6 as shown in FIG. 1 . More specifically, the support bases 4 are arranged to be perpendicular to the axial direction L of the camshafts 5 , 6 .
  • Each of the support bases 4 includes a receiving member 41 located on the top surface 1 a of the cylinder head 1 , and an exhaust side cap member 42 and an intake side cap member 43 , which are located on the top surface of the receiving member 41 as shown in FIG. 2 .
  • Semi-circular lower recesses 41 b, 41 c are formed on the top surface of each receiving member 41 at positions corresponding to the camshafts 5 , 6 .
  • a semicircular upper recess 42 b is formed on the bottom surface of each exhaust side cap member 42 at a position corresponding to the associated lower recess 41 b.
  • Each lower recess 41 b and the associated upper recess 42 b form a circular bearing portion 45 b, which supports one of cam journals 5 a of the exhaust camshaft 5 (see FIG. 1 ).
  • each intake side cap member 43 is formed on the bottom surface of each intake side cap member 43 at a position corresponding to the associated lower recess 41 c.
  • Each lower recess 41 c and the associated upper recess 43 c form a circular bearing portion 45 c, which supports one of cam journals 6 a of the intake camshaft 6 (see FIG. 1 ).
  • each exhaust side cap member 42 and the associated receiving member 41 are formed in an axial direction C of the cylinders with the exhaust camshaft 5 located in between.
  • the receiving member 41 and the exhaust side cap member 42 are tightened to the cylinder head 1 with bolts 44 L, 44 S inserted in the bolt holes.
  • each intake side cap member 43 and the associated receiving member 41 are coupled to the cylinder head 1 with other bolts 44 L in the same manner as each exhaust side cap member 42 and the associated receiving member 41 .
  • the cylinder head 1 In a state in which the support bases 4 are mounted on the cylinder head 1 with the bolts 44 L, 44 S, the cylinder head 1 is assembled to the cylinder block 2 with the head bolts 3 .
  • the cylinder head 1 , the cylinder block 2 , and the support bases 4 are all made of an aluminum alloy.
  • a through hole 41 d which extends in the axial direction L of the camshafts 5 , 6 , is formed in each receiving member 41 as shown in FIG. 2 .
  • Each through hole 41 d is formed at a position closer to a center position Pex of the exhaust camshaft 5 than to a middle position Pc between the center position Pex of the exhaust camshaft 5 and a center position Pin of the intake camshaft 6 in a direction perpendicular to the axial direction L of the camshafts 5 , 6 .
  • the through holes 41 d are formed closer to the exhaust camshaft 5 than to the intake camshaft 6 .
  • a rod 7 made of stainless-steel is inserted in the through holes 41 d. That is, the rod 7 is made of material having higher rigidity than the support bases 4 .
  • the outer diameter of the rod 7 is slightly smaller than the inner diameter of the through holes 41 d.
  • the bolts 44 S located closer to the rod 7 than to the exhaust camshaft 5 are shorter than the other bolts 44 L so as not to interfere with the rod 7 .
  • the camshafts 5 , 6 are supported to be freely rotational by the bearing portions 45 b, 45 c of the five support bases 4 mounted on the cylinder head 1 . Since the support bases 4 are located separate from one another in the axial direction L of the camshafts 5 , 6 , the contact area between the support bases 4 and the cylinder head 1 is reduced as compared to a case in which an outer frame for connecting the support bases is provided, as in a ladder-frame camshaft housing. The amount of heat received from the cylinder head 1 is thus reduced, which reduces thermal deformation of the support bases 4 caused by receiving heat.
  • the temperature of exhaust gas is increased as compared to the internal combustion engine without a forced-induction device.
  • This increases the thermal deformation amount of the support bases 4 caused by receiving heat from the cylinder head 1 .
  • the cylinder head 1 is deformed significantly as the pressure in the cylinders of the internal combustion engine fluctuates. The deformation amount of the support bases 4 mounted on the cylinder head 1 is consequently increased.
  • the alignment of the bearing portions 45 b, 45 c in the support bases 4 is likely to deteriorate due to engine operation although with the camshaft support structure of the present embodiment that does not include the outer frame for the support bases 4 .
  • the support bases 4 are favorably restricted from being thermally deformed due to heat received from the cylinder head 1 .
  • the through holes 41 d in which the rod 7 is inserted are formed at positions closer to the exhaust camshaft 5 than to the intake camshaft 6 . That is, the rod 7 is arranged in the vicinity of the regions in the receiving members 41 of the support bases 4 where the amount of heat received from the cylinder head 1 is great and the degree of thermal deformation is great. Thermal deformation of the receiving members 41 in the vicinity of the exhaust camshaft 5 is thus reduced in an appropriate manner.
  • the rod 7 is assembled to the cylinder head 1 together with the support bases 4 in a state in which the rod 7 is inserted in the through holes 41 d.
  • the cylinder head 1 is further assembled to the cylinder block 2 with the head bolts 3 in a state in which the support bases 4 and the rod 7 are assembled to the cylinder head 1 .
  • the top surface 1 a of the cylinder head 1 is slightly distorted from a flat state due to the axial tightening force of the head bolts 3 as shown in FIG. 3 .
  • the rod 7 is thus maintained in a state pressed by the inner walls of the through holes 41 d, and secured to the support bases 4 .
  • the distortion of the top surface 1 a of the cylinder head 1 is exaggerated and the rod 7 is omitted in FIG. 3 .
  • the camshaft support structure of the present embodiment as described above has the following advantages.
  • the support bases 4 are arranged apart from one another in the axial direction L of the camshafts 5 , 6 . Furthermore, the bearing portions 45 b, 45 c, which support the camshafts 5 , 6 , and the through holes 41 d, which extend in the axial direction L of the camshafts 5 , 6 , are formed in the support bases 4 .
  • the rod 7 is inserted in the through holes 41 d to restrict the bearing portions 45 b, 45 c from being displaced from the arrangement position at which the bearing portions 45 b, 45 c are located when the internal combustion engine is stopped and cold.
  • the alignment of the bearing portions 45 b, 45 c is favorably restricted from deteriorating due to engine operation.
  • the state in which the internal combustion engine is stopped and cold refers to a state in which operation of the internal combustion engine is stopped and the influence of heat caused by the previous engine operation can be ignored.
  • the rod 7 is made of material having higher rigidity than the support bases 4 . More specifically, the support bases 4 are made of an aluminum alloy, and the rod 7 is made of stainless-steel, which has higher rigidity than the aluminum alloy. With this configuration, thermal deformation of the support bases 4 is reduced in an appropriate manner.
  • the through holes 41 d are formed closer to the exhaust camshaft 5 than to the intake camshaft 6 . This structure appropriately reduces thermal deformation of the receiving members 41 in the vicinity of the exhaust camshaft 5 where the amount of heat received from the cylinder head 1 is great.
  • camshaft support structure of the present invention is not limited to the structure illustrated in the above described embodiment, but may be modified as follows.
  • the present invention is applied to an internal combustion engine provided with an exhaust driven forced-induction device, that is, a turbocharger.
  • the present invention may, however, be applied to an internal combustion engine provided with an engine driven forced-induction device, or a supercharger.
  • the present invention is applied to an internal combustion engine provided with a forced-induction device.
  • the present invention is not only applied to an internal combustion engine provided with a forced-induction device, but may be applied to an internal combustion engine without a forced-induction device.
  • the alignment of the bearing portions of the support bases is favorably restricted from deteriorating due to engine operation in the same manner as the above-described embodiment.
  • the through holes 41 d be formed closer to the exhaust camshaft 5 than to the intake camshaft 6 to prevent thermal deformation of the receiving members 41 in the vicinity of the exhaust camshaft 5 where the amount of heat received from the cylinder head 1 is great.
  • the present invention is not limited to this, but through holes may be formed at, for example, the middle position Pc between the exhaust camshaft 5 and the intake camshaft 6 . In this case also, thermal deformation of the receiving members is restricted to some extent.
  • one through hole 41 d is formed in each of the support bases 4 .
  • two or more through holes may be formed in each of the support bases 4 , and two or more rods may be provided corresponding to the number of the through holes. This further reduces thermal deformation of the support bases.
  • the rod 7 made of stainless-steel is illustrated in the above-described embodiment, but the rod may be made of any material that has higher rigidity than the support bases.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
US14/349,738 2011-10-11 2011-10-11 Camshaft support structure Abandoned US20140305397A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2011/073339 WO2013054395A1 (ja) 2011-10-11 2011-10-11 カムシャフト支持構造

Publications (1)

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US20140305397A1 true US20140305397A1 (en) 2014-10-16

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US14/349,738 Abandoned US20140305397A1 (en) 2011-10-11 2011-10-11 Camshaft support structure

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US (1) US20140305397A1 (ja)
EP (1) EP2767680A4 (ja)
JP (1) JP5742956B2 (ja)
CN (1) CN103874830A (ja)
WO (1) WO2013054395A1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10309339B2 (en) * 2015-05-25 2019-06-04 Nissan Motor Co., Ltd. Internal combustion engine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6631176B2 (ja) * 2015-11-09 2020-01-15 いすゞ自動車株式会社 内燃機関のシリンダヘッド構造及び内燃機関

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090013949A1 (en) * 2006-01-19 2009-01-15 Toyota Jidosha Kabushiki Kaisha Camshaft Support Structure of an Internal Combustion Engine
US20090101096A1 (en) * 2007-10-19 2009-04-23 Honda Motor Co., Ltd. Valve system for overhead-camshaft-type internal combustion engine, and engine incorporating same
JP2010209796A (ja) * 2009-03-10 2010-09-24 Toyota Motor Corp カムシャフト支持構造

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60531B2 (ja) * 1981-10-05 1985-01-08 マツダ株式会社 エンジンのカムシヤフト軸受構造
JPS6127905U (ja) * 1984-07-25 1986-02-19 本田技研工業株式会社 Ｏｈｃ型内燃機関
DE3641129C1 (de) * 1986-12-02 1987-07-30 Daimler Benz Ag Vorrichtung zur Lagerung von zwei Nockenwellen im Zylinderkopf einer mehrzylindrigen Reihenbrennkraftmaschine
JPH11351243A (ja) * 1998-06-05 1999-12-24 Hitachi Ltd スラスト軸受
JP4365373B2 (ja) * 2006-01-19 2009-11-18 トヨタ自動車株式会社 内燃機関のカムシャフト支持構造
JP4144625B2 (ja) * 2006-01-19 2008-09-03 トヨタ自動車株式会社 内燃機関のカムシャフト支持構造
JP4218715B2 (ja) * 2006-08-31 2009-02-04 トヨタ自動車株式会社 シリンダヘッド
JP2008133749A (ja) * 2006-11-27 2008-06-12 Toyota Motor Corp カムシャフトの軸受構造及び軸受方法
JP2008303856A (ja) * 2007-06-11 2008-12-18 Toyota Motor Corp エンジン構造およびエンジンにおける熱変形制御方法

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090013949A1 (en) * 2006-01-19 2009-01-15 Toyota Jidosha Kabushiki Kaisha Camshaft Support Structure of an Internal Combustion Engine
US20090101096A1 (en) * 2007-10-19 2009-04-23 Honda Motor Co., Ltd. Valve system for overhead-camshaft-type internal combustion engine, and engine incorporating same
JP2010209796A (ja) * 2009-03-10 2010-09-24 Toyota Motor Corp カムシャフト支持構造

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Machine Translation of JP 2010209796 A PDF File name: "JP2010209796A_Machine_Translation.pdf" *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10309339B2 (en) * 2015-05-25 2019-06-04 Nissan Motor Co., Ltd. Internal combustion engine

Also Published As

Publication number Publication date
CN103874830A (zh) 2014-06-18
WO2013054395A1 (ja) 2013-04-18
EP2767680A4 (en) 2015-09-30
JPWO2013054395A1 (ja) 2015-03-30
JP5742956B2 (ja) 2015-07-01
EP2767680A1 (en) 2014-08-20

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Effective date: 20140204

STCB Information on status: application discontinuation

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