JPH04116209A - Valve system four-cycle - Google Patents
Valve system four-cycleInfo
- Publication number
- JPH04116209A JPH04116209A JP23526890A JP23526890A JPH04116209A JP H04116209 A JPH04116209 A JP H04116209A JP 23526890 A JP23526890 A JP 23526890A JP 23526890 A JP23526890 A JP 23526890A JP H04116209 A JPH04116209 A JP H04116209A
- Authority
- JP
- Japan
- Prior art keywords
- exhaust
- intake
- valve
- lifter
- spring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000001816 cooling Methods 0.000 abstract description 13
- 238000002485 combustion reaction Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 239000000498 cooling water Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000000881 depressing effect Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
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
-
- 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
- F01L1/022—Chain drive
-
- 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
- F01L1/024—Belt drive
-
- 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
- F01L1/026—Gear drive
-
- 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
-
- 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
- F01L1/14—Tappets; Push rods
- F01L1/143—Tappets; Push rods for use with overhead 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
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
- F01L1/265—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder peculiar to machines or engines with three or more intake valves per cylinder
-
- 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
- F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
- F01L3/10—Connecting springs to valve members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
- F02F1/4221—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder particularly for three or more inlet valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F7/0002—Cylinder arrangements
- F02F7/0012—Crankcases of V-engines
-
- 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]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B1/00—Engines characterised by fuel-air mixture compression
- F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
- F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/18—DOHC [Double overhead camshaft]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F2001/244—Arrangement of valve stems in cylinder heads
- F02F2001/245—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F2200/00—Manufacturing
- F02F2200/06—Casting
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は4サイクルエンジンの動弁構造に関し、特に気
筒あたり3本の吸気弁及び2本の排気弁を備えた場合に
、エンジン全高を抑えながら排気側の冷却ジャケットを
大きくできるように、又はバルブリフト量を増大できる
ようにした各弁用付勢ばね、及びリフタの配置構造の改
善に関する。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a valve train structure for a four-stroke engine, and in particular, when each cylinder is provided with three intake valves and two exhaust valves, the overall height of the engine can be suppressed. The present invention also relates to improvements in the arrangement structure of valve biasing springs and lifters that can increase the size of the cooling jacket on the exhaust side or increase the amount of valve lift.
エンジンの充填効率を向上させるために吸気弁を3本、
排気弁を2本備えた5バルブエンジンが提案されている
。この種のエンジンの動弁機構は、リフタを答弁の上端
面に当接するように装着するとともに、答弁の上部に固
着されたリテーナと弁座との間に付勢ばねを介設し、上
記りフタをカム軸で押圧するように構成されている。Three intake valves to improve engine filling efficiency.
A five-valve engine with two exhaust valves has been proposed. In this type of engine valve mechanism, a lifter is mounted so as to come into contact with the upper end surface of the valve, and a biasing spring is interposed between the retainer fixed to the top of the valve and the valve seat. The lid is configured to be pressed by a camshaft.
ところで上記5バルブエンジンでは、排気弁は本数が少
ないため吸気弁に比較して大径で、従って比較的重量の
大きいものを採用する場合が多く、またバルブリフト量
も大きく設定される。そのため排気弁用付勢ばねとして
は、比較的重い排気弁を確実に付勢できるようにばね定
数の大きい大径のものが必要であり、かつリフト量を増
大できるようにばね長の長いものが必要となり、それだ
けエンジン全高が高くなり易い、一方、エンジン全高を
抑えようとすると、上記ばね座を下方に位置させること
となり、それだけ排気側の冷却ジャケットが小さくなり
、冷却性が低下したり、又は十分なバルブリフト量が確
保できない懸念がある。Incidentally, in the above-mentioned five-valve engine, since the number of exhaust valves is small, the exhaust valves have a larger diameter than the intake valves, and therefore are often relatively heavy, and the valve lift amount is also set to be large. Therefore, the biasing spring for the exhaust valve needs to have a large diameter with a large spring constant so that it can reliably bias the relatively heavy exhaust valve, and a spring with a long length to increase the amount of lift. On the other hand, if you try to reduce the overall height of the engine, you will have to position the spring seat lower, which will make the cooling jacket on the exhaust side smaller and reduce the cooling performance. There is a concern that sufficient valve lift cannot be secured.
また、吸気弁については、3本と本数が多いため各吸気
弁同士の間隔が狭くなり、1気リフタの配置スペースの
確保が困難である。Furthermore, since there are a large number of intake valves (three), the intervals between the intake valves become narrow, making it difficult to secure a space for arranging the one-stroke lifter.
本発明は上記従来の実情に鑑みてなされたもので、エン
ジン全高を抑え、吸気リフタを無理なく配置しながら排
気側の冷却ジャケットを大きくして冷却性を改善でき、
又は十分なバルブリフト量を確保できるようにした4サ
イクルエンジンの動弁装置を提供することを目的として
いる。The present invention has been made in view of the above-mentioned conventional circumstances, and it is possible to improve cooling performance by reducing the overall height of the engine, arranging the intake lifter without difficulty, and enlarging the cooling jacket on the exhaust side.
Another object of the present invention is to provide a valve operating system for a four-stroke engine that can ensure a sufficient amount of valve lift.
本願請求項fl)の発明は、気筒あたり3本の吸気弁及
び該吸気弁より大径の2本の排気弁を配設するとともに
、該各吸気弁、排気弁の上端部とシリンダヘッドに形成
された吸気、排気ばね座との間に該答弁を閉方向に付勢
する吸気、排気付勢ばねを配設し、上記答弁の上端面に
当接するように吸気、排気リフタを装着し、該各リフタ
を介して上記吸気弁、排気弁をそれぞれ吸気カム軸、排
気カム軸で開閉駆動するようにした4サイクルエンジン
の動弁装置において、上記吸気付勢ばねの外径と吸気リ
フタの外径とを略同一に設定して、該吸気付勢ばねの上
端をリフタの下端付近に位置させるとともに、上記排気
付勢ばねの外径を排気リフタの内径より小さく設定して
、該排気付勢ばねの上部を排気リフタ内に挿入したこと
を特徴としており、請求項(2)の発明は、上記排気カ
ム軸の軸芯からばね座までの寸法を吸気カム軸の軸芯か
らばね座までの寸法より小さく設定したことを特徴とし
ている。また、請求項(3)の発明は、上記排気カム軸
の軸芯からばね座までの寸法を吸気カム軸の軸芯からば
ね座までの寸法と同一に設定したことを特徴としている
。The invention of claim fl) is provided with three intake valves and two exhaust valves having a larger diameter than the intake valves per cylinder, and the upper ends of each intake valve and exhaust valve are formed on the cylinder head. An intake/exhaust biasing spring for biasing the answering valve in the closing direction is disposed between the intake/exhaust spring seats, and an intake/exhaust lifter is attached so as to come into contact with the upper end surface of the answering valve. In a valve operating system for a four-cycle engine in which the intake valve and the exhaust valve are driven to open and close by an intake camshaft and an exhaust camshaft, respectively, via each lifter, the outer diameter of the intake bias spring and the outer diameter of the intake lifter are provided. are set to be substantially the same, and the upper end of the intake biasing spring is located near the lower end of the lifter, and the outer diameter of the exhaust biasing spring is set to be smaller than the inner diameter of the exhaust lifter, so that the exhaust biasing spring is located near the lower end of the lifter. The upper part of the exhaust camshaft is inserted into the exhaust lifter, and the invention of claim (2) is characterized in that the dimension from the axis of the exhaust camshaft to the spring seat is the dimension from the axis of the intake camshaft to the spring seat. It is characterized by being set smaller. Further, the invention according to claim (3) is characterized in that the dimension from the axis of the exhaust camshaft to the spring seat is set to be the same as the dimension from the axis of the intake camshaft to the spring seat.
ここで吸気付勢ばねの外径と吸気リフタの外径とを略同
一に設定するとは、両者が干渉する程度の大きさに設定
する場合、及び付勢ばねを吸気リフタ内に挿入可能の場
合で、両者の相対移動に十分な隙間がない大きさに設定
する場合の両方を含む。Here, setting the outer diameter of the intake biasing spring and the outer diameter of the intake lifter to be approximately the same means that they are set to such a size that they interfere with each other, and when the biasing spring can be inserted into the intake lifter. This includes both cases where the size is set so that there is not enough clearance for relative movement between the two.
本願請求項(1ンの発明に係る動弁装置によれば、吸気
弁側については、付勢ばねの上端をリフタの下端付近に
位置させるいわゆる2段重ね構造とし、排気弁側につい
ては、付勢ばねの上部をリフタ内に挿入するいわゆるパ
ケット構造としたので、エンジンの全高を抑えることが
できるとともに、3つの吸気リフタを無理なく配設でき
る。According to the valve train according to the invention of claim 1, the intake valve side has a so-called two-stage structure in which the upper end of the biasing spring is located near the lower end of the lifter, and the exhaust valve side has an attached structure. Since it has a so-called packet structure in which the upper part of the spring is inserted into the lifter, the overall height of the engine can be suppressed and three intake lifters can be arranged without difficulty.
また、請求項(2)の発明によれば排気弁例のカム軸〜
ばね座間寸法を吸気弁側の寸法より小さく設定したので
、排気弁側のばね座を高くして排気開口〜ばね座間寸法
を増大でき、エンジン全高を抑えながら排気弁側の冷却
ジャケットを大きくでき、それだけ冷却性を改善できる
。Further, according to the invention of claim (2), the camshaft of the exhaust valve example ~
Since the spring seat dimension is set smaller than that on the intake valve side, the spring seat on the exhaust valve side can be raised to increase the dimension between the exhaust opening and the spring seat.The cooling jacket on the exhaust valve side can be enlarged while keeping the overall height of the engine down. Cooling performance can be improved accordingly.
また請求項(3)の発明によれば、上記2段重ね構造と
パケット構造とを採用し、かつ排気弁側のカム軸〜ばね
座間寸法を吸気弁側と同一に設定したので、排気付勢ば
ねを相対的に長くすることができ、それだけエンジン全
高を抑えながらリフト量を増大でき、排気弁本数が少な
いにも関わらず排気効率を向上できる。Further, according to the invention of claim (3), the two-stage structure and the packet structure are adopted, and the dimension between the camshaft and the spring seat on the exhaust valve side is set to be the same as that on the intake valve side, so that the exhaust bias is Since the spring can be made relatively long, the lift amount can be increased while suppressing the overall height of the engine, and the exhaust efficiency can be improved despite the small number of exhaust valves.
以下、本発明の実施例を図について説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
第1図ないし第3図は請求項(1)、及び(2)の発明
の一実施例による4サイクルエンジンの動弁装置を説明
するための図であり、第1図は該エンジンの車両搭載状
態におけるシリンダヘッド部分の断面正面図、第2図は
上部ヘッドの平面図、第3図は該実施例エンジンの正面
図である。1 to 3 are diagrams for explaining a valve train for a four-stroke engine according to an embodiment of the invention of claims (1) and (2), and FIG. FIG. 2 is a plan view of the upper head, and FIG. 3 is a front view of the engine of this embodiment.
図において、1は本実施例装置が採用された水冷式4サ
イクル■型エンジンであり、これはシリンダブロック2
の下面にクランクケース3を装着するとともに、上面に
左、右一対のシリンダヘッド4.ヘッド力バー5を積層
締結した構造のものである。上記シリンダブロック2に
は複数の気筒(シリンダボア)6がクランク軸方向に見
て7字状をなすように形成されており、該各気筒6内に
挿入されたピストン7はコンロフト8でクランク軸9に
連結されている。In the figure, 1 is a water-cooled 4-cycle ■ type engine in which the device of this embodiment is adopted, and this is a cylinder block 2.
The crankcase 3 is mounted on the lower surface of the , and a pair of left and right cylinder heads 4 are mounted on the upper surface. It has a structure in which head force bars 5 are stacked and fastened together. A plurality of cylinders (cylinder bores) 6 are formed in the cylinder block 2 so as to form a 7-shape when viewed in the direction of the crankshaft, and a piston 7 inserted into each cylinder 6 has a convex loft 8 and a crankshaft 9. is connected to.
上記シリンダヘッド4は下部ヘッド10と上部ヘッド1
)とからなる上下2分割構造のものであり、下部ヘッド
10の下面には上記ピストン7の上面とで燃焼室を構成
する燃焼凹部12が凹設されている。この燃焼凹部12
には、3つの吸気開口12a 〜12C,及び2つの排
気開口12d。The cylinder head 4 has a lower head 10 and an upper head 1.
), and a combustion recess 12 is formed in the lower surface of the lower head 10 and forms a combustion chamber with the upper surface of the piston 7. This combustion recess 12
There are three intake openings 12a to 12C and two exhaust openings 12d.
128が該燃焼凹部12の周縁に沿って形成されており
、中央には点火プラグ挿入孔12iが形成されている。128 is formed along the periphery of the combustion recess 12, and a spark plug insertion hole 12i is formed in the center.
上記排気開口12d、12eは排気通路13d、13g
によってシリンダへフド4のVバンク外側壁10bに導
出されている。また上記吸気開口122〜12Cは吸気
通路13a〜13cによってシリンダヘッド4のVバン
ク内側壁10aに導出され、上部へソド1)の上方に延
びる延長部1)c部分で合流しており、該合流部13f
はクランク軸方向に横長の楕円状に形成されている。上
記中央の吸気通路13b部分に形成された取付穴lid
には燃料噴射弁30が装着されており、また上記延長部
lieには上記合流部13fを開閉するスライドバルブ
39が配設され、さらにエアホーン40が接続されてい
る。なお41は上記エアホーン41にゴミ等が侵入する
のを防止するカバーである。The exhaust openings 12d and 12e are exhaust passages 13d and 13g.
is led out to the V-bank outer wall 10b of the cylinder hood 4. Further, the intake openings 122 to 12C are led out to the V-bank inner wall 10a of the cylinder head 4 by the intake passages 13a to 13c, and are merged at an extension portion 1)c extending upward to the upper portion of the cylinder head 1). Part 13f
is formed into a horizontally long ellipse in the direction of the crankshaft. Mounting hole lid formed in the center intake passage 13b part
A fuel injection valve 30 is attached to the extension portion lie, and a slide valve 39 for opening and closing the merging portion 13f is provided on the extension portion lie, and an air horn 40 is further connected to the extension portion lie. Note that 41 is a cover that prevents dirt and the like from entering the air horn 41.
また、上記下部へッドlO内には、上記燃焼凹部12の
上方を覆うように水冷ジャケットが形成されている。こ
の水冷ジャケットは、上記吸気通路13a〜13c部分
から該下部ヘッド10の内側壁10a側にかけて位置す
る吸気側ジャケット31aと、上記排気通路13d、1
3e部分から外側壁10b側にかけて位置する排気側ジ
ャケット31bと、上記吸気通路、排気通路間部分に位
置する中央ジャケット31cとから構成されている。ま
た中央ジャケット31cと吸気側ジャケット31aとの
上端同士を結ぶ位置で、かつ左、右の吸気通路13a、
13eを挟む位置には、ドリル加工により連通孔31e
が形成されている。なお、冷却水は、シリンダブロック
2の水冷ジャケット(図示せず)から排気側ジ中ケッl
−31b内に流入し、中央ジャケット31C,吸気側ジ
ャケット31gを通って排水口31dに流出する。また
冷却水の供給開始時には、中央ジャケット31C内の空
気は上記連通孔31eを遣って吸気側ジャケット3Ia
側に排気される。Further, a water cooling jacket is formed in the lower head 1O so as to cover the upper part of the combustion recess 12. This water cooling jacket includes an intake side jacket 31a located from the intake passages 13a to 13c to the inner wall 10a side of the lower head 10, and the exhaust passages 13d and 1.
It consists of an exhaust side jacket 31b located from the portion 3e to the outer wall 10b side, and a central jacket 31c located between the intake passage and the exhaust passage. Further, at a position connecting the upper ends of the center jacket 31c and the intake side jacket 31a, the left and right intake passages 13a,
A communicating hole 31e is formed by drilling at the position sandwiching the hole 13e.
is formed. The cooling water is supplied from the water cooling jacket (not shown) of the cylinder block 2 to the exhaust side pipe.
-31b, passes through the central jacket 31C, the intake side jacket 31g, and flows out to the drain port 31d. Moreover, when the supply of cooling water is started, the air in the central jacket 31C is transferred to the intake side jacket 3Ia through the communication hole 31e.
Exhaust to the side.
そして上記吸気開口12a〜12c、排気開口12d、
12eには吸気弁14.排気弁15の弁板部14a、1
5aがそれぞれ配設されている。The intake openings 12a to 12c, the exhaust opening 12d,
12e has an intake valve 14. Valve plate portion 14a, 1 of exhaust valve 15
5a are arranged respectively.
該答弁14,15の弁棒14b、15bの上端部は、上
記上部ヘッド1)に形成されたガイド穴1)a、llb
内に位置している。このガイド穴1)a及びllbは、
それぞれ3個づつ、及び2個づつ半径方向に連続するよ
う、つまり境界壁がなくなる大きさに形成されており、
該各ガイド穴IIa、Ilb内には補強用の吸気、排気
インサート16.17が鋳込まれている。そして上記吸
気。The upper ends of the valve stems 14b, 15b of the counter valves 14, 15 are formed in the guide holes 1)a, llb formed in the upper head 1).
Located within. These guide holes 1) a and llb are
Three pieces each and two pieces each are formed so as to be continuous in the radial direction, that is, to a size that eliminates the boundary wall,
Reinforcing intake and exhaust inserts 16, 17 are cast into each guide hole IIa, Ilb. And the above intake.
排気インサート16.17に形成された摺動穴内には有
底筒状の吸気、排気リフタ18.19が摺動自在に挿入
されており、該吸気、排気リフタ18.19の底面内側
に上記弁棒14b、15bの上端面がパットを介して当
接している。またこの弁棒14b、15bの上端付近に
はリテーナ2゜21が装着されており、該リテーナ20
.21と、上記下部ヘッドに形成されたばね座12g、
12hとの間には二重構造の唆気、排気付勢ばね22゜
23が介設されている。これにより上記吸気、排気弁1
4.15は吸気開口、排気開口を閉じる方向に付勢され
ている。また上記吸気リフタ18排気リフタ19に転接
するように吸気カム軸24排気カム軸25が配設されて
いる。該各カム軸24.25は、上部ヘッド1)に形成
された軸受部と、ポルト32aで固定されたカムキャッ
プ32とで軸支されており、該各カム軸24.25のカ
ム山で上記各吸気、排気リフタ18.19を押し下げる
ことにより吸気弁14.排気弁15を下降させるように
なっている。A bottomed cylindrical intake/exhaust lifter 18.19 is slidably inserted into the sliding hole formed in the exhaust insert 16.17, and the above-mentioned valve is installed inside the bottom surface of the intake/exhaust lifter 18.19. The upper end surfaces of the rods 14b and 15b are in contact with each other via pads. Further, a retainer 2°21 is attached near the upper end of the valve stems 14b and 15b, and the retainer 20
.. 21, a spring seat 12g formed on the lower head,
A double-structured air/exhaust biasing spring 22 and 23 is interposed between the air pump 12h and the air pump 12h. As a result, the above intake and exhaust valves 1
4.15 is biased in the direction of closing the intake opening and the exhaust opening. Further, an intake camshaft 24 and an exhaust camshaft 25 are arranged so as to be in rolling contact with the intake lifter 18 and the exhaust lifter 19. Each of the camshafts 24.25 is pivotally supported by a bearing portion formed in the upper head 1) and a cam cap 32 fixed by a port 32a, and the cam ridges of each camshaft 24.25 Intake valve 14. by depressing each intake and exhaust lifter 18.19. The exhaust valve 15 is lowered.
ここで上記吸気付勢ばね22の外径は吸気リフタ18と
略同一径になっており、かつ該吸気付勢ばね22の上端
が吸気リフタ18の下端に位置するように上記リテーナ
20.及びばね座12gの高さ位置が設定されている。Here, the outer diameter of the intake biasing spring 22 is approximately the same diameter as the intake lifter 18, and the retainer 20. and the height position of the spring seat 12g.
その結果、吸気カム軸側部分は、吸気リフタ18に吸気
付勢ばね22を2段重ねした構造になっている。As a result, the intake camshaft side portion has a structure in which the intake lifter 18 and the intake bias spring 22 are stacked in two stages.
また上記排気付勢ばね23の外径は排気リフタ17の内
径より若干小さくなっており、かつ排気リフタ17内に
排気付勢ばね23の上部が挿入されるように排気リテー
ナ21.及びばね座12hの高さ位置が設定されている
。その結果、排気カム軸側部分は、排気付勢ばね23の
上部を排気リフタ19で覆ういわゆるパケット構造とな
っている。Further, the outer diameter of the exhaust biasing spring 23 is slightly smaller than the inner diameter of the exhaust lifter 17, and the exhaust retainer 21. and the height position of the spring seat 12h. As a result, the exhaust camshaft side portion has a so-called packet structure in which the upper part of the exhaust biasing spring 23 is covered with the exhaust lifter 19.
また、排気カム軸25の軸芯から排気ばね座12hまで
の寸法L2は、吸気カム軸24の軸芯から吸気ばね座1
2gまでの寸法L1より小さく設定されており、その結
果、排気口12eから排気ばね座12hまでの中央シャ
ケ7)寸法L2’は、吸気開口12Cから吸気ばね座1
2gまでの中央ジャケット寸法Ll’より大きくなって
いる。なお、カム軸の軸芯から開口までの寸法は、吸気
側排気側とも略同一となっている。In addition, the dimension L2 from the axis of the exhaust camshaft 25 to the exhaust spring seat 12h is from the axis of the intake camshaft 24 to the intake spring seat 12h.
As a result, the dimension L2' of the central bracket 7) from the exhaust port 12e to the exhaust spring seat 12h is set smaller than the dimension L1 from the intake opening 12C to the intake spring seat 1.
It is larger than the central jacket dimension Ll' up to 2g. Note that the dimensions from the axis of the camshaft to the opening are approximately the same on both the intake and exhaust sides.
次に本実施例の作用効果について説明する。Next, the effects of this embodiment will be explained.
本実施例エンジンでは、排気弁15は、吸気弁3本に対
して2本と少ないので、1本当たりの排気開口面積を増
大するため吸気弁14より大径のものが採用されており
、またバルブリフト量が大きく設定されている。そのた
め排気付勢ばね23は、ばね定数の大きい大径で、かつ
ばね長の長いものが採用されており、従って排気リフタ
19゜排気付勢ばね23等の配置構造の如何によっては
、排気カム軸位置が高くなってエンジン全高が高くなっ
たり、逆に排気ばね座位置が低くなって排気側ジャケラ
)31bが十分に確保できない懸念がある0本実施例で
は、吸気側については2段重ね構造を採用し、排気側に
ついてはバケット構造を採用することにより、排気側の
カム軸〜ばね座間寸法L2を、吸気側のカム軸〜ばね座
間寸法Llより低く設定したので、排気側の排気開口〜
ばね座間寸法L2’を増大でき、エンジン全高を抑えな
がら排気側ジャケット31bを十分に確保して冷却効率
を改善できる。In the engine of this embodiment, the number of exhaust valves 15 is two compared to three intake valves, so a larger diameter than the intake valve 14 is used to increase the exhaust opening area per exhaust valve. The valve lift amount is set to a large value. Therefore, the exhaust biasing spring 23 has a large spring constant, a large diameter, and a long spring length. There is a concern that the position of the exhaust spring seat may become higher and the overall height of the engine becomes higher, or conversely, the position of the exhaust spring seat may become lower and that sufficient exhaust side jacket (31b) may not be secured. By adopting a bucket structure on the exhaust side, the camshaft to spring seat dimension L2 on the exhaust side is set lower than the camshaft to spring seat dimension Ll on the intake side, so the exhaust opening on the exhaust side
The spring seat space dimension L2' can be increased, and the exhaust side jacket 31b can be secured sufficiently to improve cooling efficiency while suppressing the overall height of the engine.
またこの場合、吸気側については、吸気リフタI8と吸
気付勢ばね22とを2段重ねにする構造を採用したので
、つまり付勢ばねをリフタ内に挿入する必要がないので
、吸気リフタI8が比較的小径のもので済み、従って3
つの吸気リフタ18を無理なく配設することができる。Furthermore, in this case, on the intake side, a structure in which the intake lifter I8 and the intake biasing spring 22 are stacked in two stages is adopted, meaning that there is no need to insert the biasing spring into the lifter. It only requires a relatively small diameter, so 3
Two intake lifters 18 can be arranged without difficulty.
上記実施例では、排気側のカム軸〜ばね座間寸法L2を
吸気側のカム軸〜ばね座間寸法L1より小さく設定した
が、上記排気側寸法L2を吸気側寸法L1と同一に設定
することもでき、このように設定したので本願請求項(
3)の発明である。In the above embodiment, the exhaust side camshaft to spring seat dimension L2 is set smaller than the intake side camshaft to spring seat dimension L1, but the exhaust side dimension L2 can also be set to be the same as the intake side dimension L1. , Since it is set in this way, the claim of the present application (
This is the invention of 3).
このように排気側のカム軸〜ばね座間寸法L2を吸気側
の寸法L1と同一に設定した場合は、排気付勢ばね23
としてさらにばね長の長いものが採用できる。そのため
エンジン全高を抑えながらバルブリフト量をさらに増大
でき、その結果、排気弁本数を吸気弁より少なくしなが
ら、十分な排気効率を確保できる。In this way, when the exhaust side camshaft-spring seat dimension L2 is set to be the same as the intake side dimension L1, the exhaust biasing spring 23
As a result, a spring with an even longer length can be used. Therefore, the amount of valve lift can be further increased while suppressing the overall height of the engine, and as a result, sufficient exhaust efficiency can be ensured while the number of exhaust valves is smaller than that of intake valves.
以上のように本願の請求項filの発明に係る4サイク
ルエンジンの動弁装置によれば、吸気側を2段重ね構造
と、排気側をパケット構造としたのでエンジン全高を抑
えながら吸気リフタを無理なく配設でき、請求項+2)
の発明によれば、排気側のカム軸〜ばね座間寸法を吸気
側寸法より小さく設定したので、その分だけ排気側の排
気開口〜ばね座間寸法が大きくなり、従ってエンジン全
高を抑えながら排気側ジャケットを大きくして冷却性を
改善できる効果があり、また請求項(3)の発明によれ
ば、排気側のカム軸〜ばね座間寸法を吸気側と同一に設
定したので、排気付勢ばねのばね長を長くでき、エンジ
ン全高を抑えながらバルブリフト量を増大して排気効率
を改善できる効果がある。As described above, according to the valve train for a four-stroke engine according to the invention of claim fil of the present application, the intake side has a two-stage stacked structure and the exhaust side has a packet structure, so that the intake lifter cannot be easily installed while suppressing the overall height of the engine. claim +2)
According to the invention, since the dimension between the camshaft and the spring seat on the exhaust side is set smaller than the dimension on the intake side, the dimension between the exhaust opening and the spring seat on the exhaust side becomes correspondingly larger. According to the invention of claim (3), since the dimension between the camshaft and the spring seat on the exhaust side is set to be the same as that on the intake side, the spring of the exhaust biasing spring This has the effect of increasing the valve lift amount and improving exhaust efficiency while suppressing the overall engine height.
第1図ないし第3図は本願請求項+1). (21の発
明の一実施例による4サイクルエンジンの動弁装置を説
明するための図であり、第1図はそのノリンダヘッド部
分の断面正面図、第2図は上部ヘッドの平面図、第3図
は該実施例装置が採用された4サイクルエンジンの正面
図である。
図において、1は4サイクルエンジン、4はシリンダヘ
ッド、6は気筒、12g、12hはばね座、14は吸気
弁、15は排気弁、18.19は吸気、排気リフタ、2
2.23は吸気、排気付勢ばね、24.25は吸気、排
気カム軸、Llは吸気カム軸の軸芯からばね座までの寸
法、L2は排気カム軸の軸芯からばね座までの寸法であ
る。
特許出願人 ヤマハ発動機株式会社
代理人 弁理士 下布 努
第1図Figures 1 to 3 are claims +1). (This is a diagram for explaining a valve train for a four-stroke engine according to an embodiment of the invention in No. 21, in which FIG. 1 is a cross-sectional front view of the norinda head portion thereof, FIG. 2 is a plan view of the upper head, and FIG. Figure 3 is a front view of a four-stroke engine in which the device of this embodiment is adopted.In the figure, 1 is a 4-stroke engine, 4 is a cylinder head, 6 is a cylinder, 12g and 12h are spring seats, 14 is an intake valve, 15 is an exhaust valve, 18.19 is an intake and exhaust lifter, 2
2.23 is the intake and exhaust biasing springs, 24.25 is the intake and exhaust camshafts, Ll is the dimension from the axis of the intake camshaft to the spring seat, and L2 is the dimension from the axis of the exhaust camshaft to the spring seat. It is. Patent Applicant Yamaha Motor Co., Ltd. Agent Patent Attorney Tsutomu Shimofu Figure 1
Claims (3)
2本の排気弁を配設するとともに、該各吸気、排気弁の
上端部とシリンダヘッドに形成された吸気、排気ばね座
との間に該各弁を閉方向に付勢する吸気、排気付勢ばね
を配設し、上記各弁の上端面に当接するように吸気、排
気リフタを装着し、該各リフタを介して上記吸気弁、排
気弁をそれぞれ吸気カム軸、排気カム軸で開閉駆動する
ようにした4サイクルエンジンの動弁装置において、上
記吸気付勢ばねの外径と吸気リフタの外径とを略同一に
設定して、該吸気付勢ばねの上端をリフタの下端付近に
位置させるとともに、上記排気付勢ばねの外径を排気リ
フタの内径より小さく設定して、該排気付勢ばねの上部
を排気リフタ内に挿入したことを特徴とする4サイクル
エンジンの動弁装置。(1) Three intake valves and two exhaust valves with a larger diameter than the intake valves are provided per cylinder, and intake and exhaust spring seats are formed at the upper end of each intake and exhaust valve and the cylinder head. An intake/exhaust biasing spring for biasing each valve in the closing direction is disposed between the valves, and an intake/exhaust lifter is attached so as to come into contact with the upper end surface of each of the valves. In the valve operating system for a four-cycle engine in which the intake valve and the exhaust valve are driven to open and close by an intake camshaft and an exhaust camshaft, respectively, the outer diameter of the intake bias spring and the outer diameter of the intake lifter are approximately the same. The upper end of the intake biasing spring is located near the lower end of the lifter, and the outer diameter of the exhaust biasing spring is set to be smaller than the inner diameter of the exhaust lifter, so that the upper end of the exhaust biasing spring is positioned near the lower end of the lifter. A valve train for a four-stroke engine, characterized in that the valve is inserted into the engine.
ら排気ばね座までの寸法を吸気カム軸の軸芯から吸気ば
ね座までの寸法より小さく設定したことを特徴とする4
サイクルエンジンの動弁装置。(2) Claim (1) is characterized in that the dimension from the axis of the exhaust camshaft to the exhaust spring seat is set smaller than the dimension from the axis of the intake camshaft to the intake spring seat.
Valve gear for cycle engines.
ら排気ばね座までの寸法を吸気カム軸の軸芯から吸気ば
ね座までの寸法と同一に設定したことを特徴とする4サ
イクルエンジンの動弁装置。(3) The four-cycle cycle according to claim (1), characterized in that the dimension from the axis of the exhaust camshaft to the exhaust spring seat is set to be the same as the dimension from the axis of the intake camshaft to the intake spring seat. Engine valve gear.
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2235268A JP2950953B2 (en) | 1990-09-04 | 1990-09-04 | Valve system for 4-cycle engine |
US07/753,710 US5385125A (en) | 1990-09-04 | 1991-09-03 | Four cycle engine |
EP91114944A EP0474217B1 (en) | 1990-09-04 | 1991-09-04 | A valve operating mechanism for an internal combustion engine |
DE1991621030 DE69121030T2 (en) | 1990-09-04 | 1991-09-04 | Valve drive device for an internal combustion engine |
EP95114828A EP0691457B1 (en) | 1990-09-04 | 1991-09-04 | Internal combustion engine |
DE1991631403 DE69131403T2 (en) | 1990-09-04 | 1991-09-04 | Internal combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2235268A JP2950953B2 (en) | 1990-09-04 | 1990-09-04 | Valve system for 4-cycle engine |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH04116209A true JPH04116209A (en) | 1992-04-16 |
JP2950953B2 JP2950953B2 (en) | 1999-09-20 |
Family
ID=16983579
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2235268A Expired - Lifetime JP2950953B2 (en) | 1990-09-04 | 1990-09-04 | Valve system for 4-cycle engine |
Country Status (3)
Country | Link |
---|---|
EP (2) | EP0691457B1 (en) |
JP (1) | JP2950953B2 (en) |
DE (2) | DE69131403T2 (en) |
Cited By (1)
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US11002459B2 (en) | 2016-11-16 | 2021-05-11 | Koninklijke Philips N.V. | Control device and operating method for air treatment apparatuses |
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US5685265A (en) * | 1993-12-28 | 1997-11-11 | Yamaha Hatsudoki Kabushiki Kaisha | Multi valve engine |
JP3360224B2 (en) * | 1993-12-28 | 2002-12-24 | ヤマハ発動機株式会社 | 4 cycle engine |
DE102005048561A1 (en) * | 2005-10-11 | 2007-04-12 | Bayerische Motoren Werke Ag | Cylinder head for inline internal combustion engine, has exhaust gas turbocharger arranged at suction system and exhaust system, where fresh gas inlet geometry and exhaust gas outlet geometry are mirrored |
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JPH073167B2 (en) * | 1985-11-01 | 1995-01-18 | ヤマハ発動機株式会社 | Camshaft drive for 4-cycle engine |
US4745887A (en) * | 1986-03-18 | 1988-05-24 | Honda Giken Kogyo Kabushiki Kaisha | Engine provided with cooling device in motorcycle |
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JPH02123207A (en) * | 1988-10-31 | 1990-05-10 | Yamaha Motor Co Ltd | Apparatus for operating valve of four-cycle engine |
JP2960942B2 (en) * | 1990-01-23 | 1999-10-12 | ヤマハ発動機株式会社 | Valve system for 4-cycle engine |
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-
1991
- 1991-09-04 DE DE1991631403 patent/DE69131403T2/en not_active Expired - Fee Related
- 1991-09-04 EP EP95114828A patent/EP0691457B1/en not_active Expired - Lifetime
- 1991-09-04 DE DE1991621030 patent/DE69121030T2/en not_active Expired - Lifetime
- 1991-09-04 EP EP91114944A patent/EP0474217B1/en not_active Expired - Lifetime
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11002459B2 (en) | 2016-11-16 | 2021-05-11 | Koninklijke Philips N.V. | Control device and operating method for air treatment apparatuses |
Also Published As
Publication number | Publication date |
---|---|
DE69131403T2 (en) | 1999-10-28 |
EP0691457A2 (en) | 1996-01-10 |
EP0474217B1 (en) | 1996-07-24 |
DE69121030T2 (en) | 1996-12-12 |
EP0691457B1 (en) | 1999-06-30 |
JP2950953B2 (en) | 1999-09-20 |
EP0691457A3 (en) | 1996-03-06 |
DE69131403D1 (en) | 1999-08-05 |
DE69121030D1 (en) | 1996-08-29 |
EP0474217A2 (en) | 1992-03-11 |
EP0474217A3 (en) | 1992-11-25 |
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