JP4792423B2 - Air-cooled V-type engine - Google Patents

Air-cooled V-type engine Download PDF

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JP4792423B2
JP4792423B2 JP2007120057A JP2007120057A JP4792423B2 JP 4792423 B2 JP4792423 B2 JP 4792423B2 JP 2007120057 A JP2007120057 A JP 2007120057A JP 2007120057 A JP2007120057 A JP 2007120057A JP 4792423 B2 JP4792423 B2 JP 4792423B2
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exhaust
suction
banks
intake
bank
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JP2008274863A (en
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博昭 長谷部
慶太 伊藤
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Honda Motor Co Ltd
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Description

本発明は、それぞれシリンダボアを有して、相互間に谷部を画成するようにV字状に並ぶ第1及び第2バンクを、クランク軸を支持するクランクケースに連設すると共に、各バンクの外壁に冷却フィンを突設し、各バンクの頭部に吸、排気弁をV字状に配置し、これら吸、排気弁を開閉駆動する動弁装置を、クランク軸の上方に配設されてクランク軸から駆動されるカム軸と、このカム軸の吸、排気カムによりそれぞれ昇降される第1吸、排気カムフォロワ及び第2吸、排気カムフォロワと、これら第1吸、排気カムフォロワ及び第2吸、排気カムフォロワに下端をそれぞれ連接して第1及び第2バンクの前記谷部側にそれぞれ配設される第1吸、排気プッシュロッド及び第2吸、排気プッシュロッドと、これら第1吸、排気プッシュロッド及び第2吸、排気プッシュロッドの上端を対応するバンクの吸、排気弁にそれぞれ連接する第1吸、排気ロッカアーム及び第2吸、排気ロッカアームとで構成した空冷式型エンジンの改良に関する。   In the present invention, first and second banks each having a cylinder bore and arranged in a V shape so as to define a valley between them are connected to a crankcase that supports a crankshaft, and each bank Cooling fins are provided on the outer wall of each bank, and suction and exhaust valves are arranged in a V shape on the heads of the banks. A valve operating device for opening and closing the suction and exhaust valves is disposed above the crankshaft. The camshaft driven from the crankshaft, the first suction, the exhaust cam follower and the second suction, the exhaust cam follower, and the first suction, the exhaust cam follower and the second suction which are respectively lifted and lowered by the suction of the camshaft and the exhaust cam. The first suction, the exhaust push rod and the second suction, the exhaust push rod, and the first suction and the exhaust, which are respectively connected to the exhaust cam follower and connected to the bottom side of the first and second banks respectively. Push rod Beauty second intake, the upper end of the corresponding bank intake of the exhaust push rod, a first intake which connects respectively to the exhaust valve, the exhaust rocker arm and the second intake relates to an improvement in air-cooled engine that is constituted by the exhaust rocker arm.

かゝる空冷式V型エンジンは、例えば特許文献1に開示されるように、既に知られている。
特開平3−107515号公報
Such an air-cooled V-type engine is already known as disclosed in Patent Document 1, for example.
JP-A-3-107515

かゝる空冷式V型エンジンでは、各バンクの鋳造時、吸気及び排気プッシュロッドを収容するロッド室を一体に形成していたので、各バンク自体が大型化し、しかもロッド室の隅部には必然的に駄肉が多くつくことになり、その軽量化が困難であった。また各バンクのシリンダボアの外壁の、上記ロッド室に臨む部分は、外気に触れることはできないため、多少とも空冷効果が低下することになる。   In such an air-cooled V-type engine, since the rod chambers for accommodating the intake and exhaust push rods were integrally formed at the time of casting each bank, each bank itself increased in size, and at the corner of the rod chamber. Inevitably, a lot of meat was added, making it difficult to reduce the weight. In addition, since the portion of the outer wall of the cylinder bore of each bank facing the rod chamber cannot be exposed to the outside air, the air cooling effect is somewhat reduced.

本発明は、かゝる事情に鑑みてなされたもので、各バンクの軽量化を図ると共に空冷効果を向上させることを可能にした空冷式V型エンジンを提供することを目的とする。   The present invention has been made in view of such circumstances, and an object of the present invention is to provide an air-cooled V-type engine capable of reducing the weight of each bank and improving the air-cooling effect.

上記目的を達成するために、本発明は、それぞれシリンダボアを有して、相互間に谷部を画成するようにV字状に並ぶ第1及び第2バンクを、クランク軸を支持するクランクケースに連設すると共に、各バンクの外壁に冷却フィンを突設し、各バンクの頭部に吸、排気弁をV字状に配置し、これら吸、排気弁を開閉駆動する動弁装置を、クランク軸の上方に配設されてクランク軸から駆動されるカム軸と、このカム軸の吸、排気カムによりそれぞれ昇降される第1吸、排気カムフォロワ及び第2吸、排気カムフォロワと、これら第1吸、排気カムフォロワ及び第2吸、排気カムフォロワに下端をそれぞれ連接して第1及び第2バンクの前記谷部側にそれぞれ配設される第1吸、排気プッシュロッド及び第2吸、排気プッシュロッドと、これら第1吸、排気プッシュロッド及び第2吸、排気プッシュロッドの上端を対応するバンクの吸、排気弁にそれぞれ連接する第1吸、排気ロッカアーム及び第2吸、排気ロッカアームとで構成した空冷式V型エンジンにおいて、シリンダボアを有するシリンダブロックと、吸、排気弁を支持するシリンダヘッドとを一体成形して各バンクを構成すると共に、その各バンクの各吸、排気ロッカアームを、これらの吸、排気プッシュロッド側端部が相互に近接するように平面視でハ字状に配置して、各吸、排気プッシュロッドを相互に近接させ、各吸、排気プッシュロッドを個別に収容すべく互いに並列した各一対の管状のロッドカバーの下端部を、各バンクのシリンダブロックに一体に形成されてそれぞれ前記谷部側に張り出した下部支持部に設けた一対の下部取り付け孔にそれぞれ圧入させると共に、その各一対の管状のロッドカバーの上端部を、各バンクのシリンダヘッドに一体に形成されてそれぞれ前記谷部側に張り出した上部支持部に設けた一対の上部取り付け孔にそれぞれ圧入させ、前記上部取り付け孔を、前記下部取り付け孔より大径に形成すると共に、前記ロッドカバーの上端部を、その上端部以外の部分よりも大径の大径部に形成し、各バンクの冷却フィンに、ロッドカバーの各バンク外壁への近接配置を可能にする切欠きを、該切欠きの内面がロッドカバーの、前記大径部よりも小径の中間部外周に対向するように設けたことを徴とする。 In order to achieve the above object, the present invention provides a crankcase that has a cylinder bore and supports first and second banks arranged in a V shape so as to define a trough between the first and second banks. In addition, a cooling fin is provided on the outer wall of each bank, and suction and exhaust valves are arranged in a V shape on the heads of the banks, and the valve operating devices for opening and closing the suction and exhaust valves are provided. A camshaft disposed above the crankshaft and driven from the crankshaft, a first suction, an exhaust cam follower and a second suction, and an exhaust cam follower that are lifted and lowered by the suction and exhaust cams of the camshaft, respectively. Suction, exhaust cam follower and second suction, exhaust cam follower is connected to the lower end of the first and second banks, respectively, the first suction, exhaust push rod and second suction, exhaust push rod And these Air-cooled V-type composed of one suction, exhaust push rod and second suction, upper suction pump rod at the corresponding bank suction, first suction, exhaust rocker arm and second suction, exhaust rocker arm respectively connected to the exhaust valve In an engine, a cylinder block having a cylinder bore and a cylinder head that supports suction and exhaust valves are integrally formed to constitute each bank, and each suction and exhaust rocker arm of each bank is configured with these suction and exhaust push rods. side end portion disposed in V-shape in plan view so as to be close to each other, each intake and exhaust push rods in proximity to one another, each intake, each pair of parallel with each other to accommodate individual exhaust push rod provided in the lower end portion of the rod cover tubular to the lower support portion that projects on the valley side respectively are formed integrally with the cylinder block of each bank Each of the pair of lower mounting holes is press-fitted, and the upper ends of the pair of tubular rod covers are formed integrally with the cylinder heads of the banks and are provided on upper support portions projecting toward the valleys. The upper mounting hole is formed in a larger diameter than the lower mounting hole, and the upper end portion of the rod cover is formed into a large diameter portion larger than the portion other than the upper end portion. formed, the cooling fins of each bank, a notch that allows close proximity to each bank outer wall of the rod cover, the inner surface of the notch is of the rod cover, the small diameter of the intermediate portion outer periphery than the large diameter portion that provided so as to face the shall be the feature.

本発によれば、各吸、排気プッシュロッドの大部分を各バンク外に配置することが可能となり、各バンクにロッド室の形成を不要とすると共に、駄肉を削減して、各バンクのコンパクト化、延いては軽量化を図ることができ、しかもロッド室を持たない分、各バンクのシリンダボアの外壁を広い範囲で外気に露出させることが可能となり、空冷効果を高めることができる。 According to the onset bright, each intake, it is the majority of the exhaust push rod can be arranged outside each bank, along with eliminating the need for formation of the rod chamber to each bank, to reduce the paddings, each bank Therefore, the outer wall of the cylinder bore of each bank can be exposed to a wide range and the air cooling effect can be enhanced.

また各バンク外に配置される吸、排気プッシュロッドは、各バンクの上、下端部からそれぞれ前記谷部側に張り出した上部及び下部支持部に支持される一対の管状ロッドカバーに個別に収容されて保護され、しかもロッドカバーは、第1及び第2バンク間の谷部側に配置されることで、両バンクによりロッドカバーを他物との接触から保護することができるのみならず、V型エンジンのコンパクト化を図ることができる。 Further, the suction and exhaust push rods arranged outside each bank are individually accommodated in a pair of tubular rod covers supported by upper and lower support portions projecting from the upper and lower ends of each bank to the valley side. In addition, the rod cover is arranged on the valley side between the first and second banks, so that both banks can protect the rod cover from contact with other objects. Ru it is possible to reduce the size of the engine.

その上、各バンクを、シリンダブロック及びシリンダヘッドを一体成形して構成すると共に、そのシリンダヘッドに前記上部支持部を、またシリンダブロックに前記下部支持部をそれぞれ一体に形成したことで、上部及び下部支持部に、ロッドカバーの上端及び下端部を圧入する上部及び下部取り付け孔の同軸加工が可能となり、それらの同軸精度を高めることができ、その結果、上部及び下部取り付け孔へのロッドカバーの圧入が常に適正となり、圧入部のシール性を確保することができる。 In addition, each bank is formed by integrally forming a cylinder block and a cylinder head, and the upper support portion is formed integrally with the cylinder head, and the lower support portion is formed integrally with the cylinder block. Coaxial machining of the upper and lower mounting holes for press-fitting the upper and lower ends of the rod cover into the lower support part is possible, and the coaxial accuracy of these can be improved, and as a result, the rod cover to the upper and lower mounting holes can be improved. The press-fitting is always appropriate, and the sealing property of the press-fitting part can be secured.

しかも前記上部取り付け孔を、下部取り付け孔より大径に形成する一方、ロッドカバーの上端部を、その上端部以外の部分よりも大径の大径部に形成したので、各ロッドカバーの、上部取り付け孔への挿入を容易に行うことができると共に、各ロッドカバーの上端及び下端部を、上部及び下部取り付け孔へそれぞれ略同時に圧入することができ、圧入作業が容易になる。 Moreover, since the upper mounting hole is formed to have a larger diameter than the lower mounting hole, the upper end portion of the rod cover is formed to have a larger diameter portion than the portion other than the upper end portion. Insertion into the mounting hole can be easily performed, and the upper end and lower end of each rod cover can be press-fitted almost simultaneously into the upper and lower mounting holes, thereby facilitating press-fitting work.

また特に各バンクの各吸、排気ロッカアームを、これらの吸、排気プッシュロッド側端部が相互に近接するように平面視でハ字状に配置して、各吸、排気プッシュロッドを相互に近接させ、各バンクの冷却フィンには、各吸、排気プッシュロッドを個別に収容する各ロッドカバーの各バンク外壁への近接配置を可能にする切欠きを、該切欠きの内面がロッドカバーの、前記大径部よりも小径の中間部外周に対向するように設けたので、切欠きの幅を最小にして、切欠きによる冷却フィンの放熱機能の低下を最小限にとどめることができる。In particular, the suction and exhaust rocker arms of each bank are arranged in a letter C shape in plan view so that the suction and exhaust push rod side ends are close to each other, and the suction and exhaust push rods are close to each other. The cooling fins of each bank have notches that allow the rod covers that individually accommodate the suction and exhaust push rods to be placed close to the outer walls of the banks, and the inner surfaces of the notches are the rod covers. Since it is provided so as to face the outer periphery of the intermediate portion having a smaller diameter than the large diameter portion, the width of the notch can be minimized, and the deterioration of the heat radiation function of the cooling fin due to the notch can be minimized.

本発明の実施例の形態を、添付図面に示す本発明の好適な実施例に基づいて以下にに説明する。   The form of the Example of this invention is demonstrated below based on the suitable Example of this invention shown to an accompanying drawing.

図1は本発明に係る空冷式汎用V型エンジンの縦断正面図、図2は図1の2−2線断面図、図3は図1の3矢視図、図4は図1の4−4線断面図、図5は図4の5−5線断面図、図6は図4の6−6線断面図、図7は気化器の取り付け要領説明図、図8はエアクリーナの取り付け要領説明図、図9は図1中の第1バンク部の拡大図、図10は図9の10−10線に沿う第1バンク単体断面図、図11は図19の11矢視図、図12は図9の12矢視図、図13は図12の13−13線断面図、図14は図2の14部拡大図、図15は図14の15−15線断面図である。   1 is a longitudinal front view of an air-cooled general-purpose V-type engine according to the present invention, FIG. 2 is a cross-sectional view taken along line 2-2 of FIG. 1, FIG. 3 is a view taken along arrow 3 in FIG. 4 is a sectional view taken along the line 5-5 in FIG. 4, FIG. 6 is a sectional view taken along the line 6-6 in FIG. 4, FIG. 7 is an explanatory diagram for installing the vaporizer, and FIG. 8 is an explanatory diagram for installing the air cleaner. FIG. 9 is an enlarged view of the first bank portion in FIG. 1, FIG. 10 is a sectional view of the first bank along the line 10-10 in FIG. 9, FIG. 11 is a view taken in the direction of arrow 11 in FIG. FIG. 13 is a cross-sectional view taken along line 12-13 in FIG. 9, FIG. 13 is a cross-sectional view taken along line 13-13 in FIG. 12, FIG.

先ず図1〜図3において、空冷式汎用V型エンジンは、クランクケース1の上部に、左右V字状に並ぶ第1バンクB1及び第2バンクB2を連設して構成され、クランクケース1の底部には設置用フランジ2が形成される。また始動装置Stが一方のバンクB1の下方空間に収まるように、クランクケース1の一側部に設けられる。   First, in FIGS. 1 to 3, the air-cooled general-purpose V-type engine includes a first bank B <b> 1 and a second bank B <b> 2 that are arranged in a left and right V-shape on the upper side of the crankcase 1. An installation flange 2 is formed at the bottom. Further, the starter St is provided on one side of the crankcase 1 so as to be accommodated in the space below the one bank B1.

第1バンクB1及び第2バンクB2は、それぞれシリンダボア3aを有してクランクケース1にボルト結合されるシリンダブロック3と、シリンダボア3aに連なる燃焼室4aを有してシリンダブロック3に一体に連設されるシリンダヘッド4とで構成され、そのシリンダヘッド4の端面には、ヘッドカバー5がボルト結合される。各バンクB1、B2は鋳造により一体成形されるもので、それぞれの外面には多数の空冷用フィン6,6…が一体に突設される。   Each of the first bank B1 and the second bank B2 has a cylinder block 3 having a cylinder bore 3a and bolted to the crankcase 1, and a combustion chamber 4a connected to the cylinder bore 3a, and is integrally connected to the cylinder block 3. The head cover 5 is bolted to the end surface of the cylinder head 4. The banks B1, B2 are integrally formed by casting, and a large number of air cooling fins 6, 6,.

クランクケース1の前後両端壁で1本のクランク軸7が支承され、このクランク軸7のクランクピン7pに、第1及び第2バンクB1、B2のシリンダボア3a,3aに嵌装されるピストン8,8がコンロッド9,9を介して連接される。クランクケース1の前後一方の端壁1aは、クランク軸7の一端部の支持を可能につゝ、クランクケース1の本体側に対して着脱し得るようになっている。   One crankshaft 7 is supported by both front and rear walls of the crankcase 1, and pistons 8 fitted to the cylinder bores 3a and 3a of the first and second banks B1 and B2 are mounted on the crankpin 7p of the crankshaft 7. 8 are connected via connecting rods 9 and 9. The front and rear end walls 1a of the crankcase 1 can be attached to and detached from the main body side of the crankcase 1 while being able to support one end of the crankshaft 7.

図1に示すように、第1及び第2バンクB1、B2は、両バンクB1、B2の開き角度α、即ち第1バンクB1のシリンダ中心線A1と第2バンクB2のシリンダ中心線2とのなす角度αが90°となるように配置される。一方、クランク軸7には、各バンクB1、B2のピストン8の慣性力と釣り合うカウンタウエイト7wがクランクピン7pと反対に付設される。   As shown in FIG. 1, the first and second banks B1 and B2 have an opening angle α between both banks B1 and B2, that is, the cylinder center line A1 of the first bank B1 and the cylinder center line 2 of the second bank B2. The formed angle α is 90 °. On the other hand, a counterweight 7w that counterbalances the inertial force of the piston 8 of each bank B1, B2 is attached to the crankshaft 7 opposite to the crankpin 7p.

また第1及び第2バンクB1、B2は、第1バンクB1のシリンダ中心線A1及び第2バンクB2のシリンダ中心線A2がそれぞれクランク軸7の回転中心A3から両バンクB1、B2と反対側に偏倚した点Pを通るように配置される。この配置によれば、第1及び第2バンクB1、B2間に画成される谷部11を、両バンクB1、B2の開き角度α=90°を維持したまゝで広くすることができる。この谷部11にはV型エンジンEの一補機である気化器C全体と、クリーナエレメント10を内蔵するエアクリーナAcの一部とが収容される。   In the first and second banks B1, B2, the cylinder center line A1 of the first bank B1 and the cylinder center line A2 of the second bank B2 are respectively opposite to the banks B1, B2 from the rotation center A3 of the crankshaft 7. It is arranged so as to pass through the biased point P. According to this arrangement, the valley 11 defined between the first and second banks B1 and B2 can be widened while maintaining the opening angle α = 90 ° between the banks B1 and B2. The valley portion 11 accommodates the entire carburetor C, which is an auxiliary machine for the V-type engine E, and a part of the air cleaner Ac that contains the cleaner element 10.

気化器Cは、図6に明示するように、気化器本体12に、第1及び第2バンクB1、B2の配列方向に並ぶ水平方向(クランク軸7と直交する方向)の第1及び第2吸気道131,132を相互に近接配置した形成してなる2連型であり、気化器本体12の下部には、フロートチャンバ12a及び燃料カット用電磁弁12bが取り付けられる。   As clearly shown in FIG. 6, the carburetor C has first and second horizontal directions (directions orthogonal to the crankshaft 7) aligned with the carburetor body 12 in the arrangement direction of the first and second banks B <b> 1 and B <b> 2. The air intake passages 131 and 132 are formed in a close-up arrangement, and a float chamber 12a and a fuel cut solenoid valve 12b are attached to the lower part of the carburetor body 12.

図1、図4及び図5に示すように、第1及び第2バンクB1、B2のシリンダヘッド4,4には、各燃焼室4aの他に、各燃焼室4aに開口する吸気ポート14及び排気ポート15が形成される。これら吸気ポート14及び排気ポート15の燃焼室4aへの開口端部は、吸気弁座80及び排気弁座81に形成される。その際、吸気弁座80は排気弁座81より大径に形成される。またこれら吸気弁座80、排気弁座81及び、点火プラグ23を螺着するプラグ取り付け孔87とは、相互に近接しつゝ燃焼室4aの中心を囲むように配置される。   As shown in FIGS. 1, 4 and 5, the cylinder heads 4 and 4 of the first and second banks B1 and B2 include an intake port 14 opened to each combustion chamber 4a in addition to each combustion chamber 4a. An exhaust port 15 is formed. Open ends of the intake port 14 and the exhaust port 15 to the combustion chamber 4a are formed in the intake valve seat 80 and the exhaust valve seat 81, respectively. At that time, the intake valve seat 80 is formed with a larger diameter than the exhaust valve seat 81. The intake valve seat 80, the exhaust valve seat 81, and the plug mounting hole 87 into which the spark plug 23 is screwed are disposed so as to surround the center of the combustion chamber 4a.

図9〜図11に示すように、各バンクB1、B2のシリンダヘッド4には、吸気弁座80及び排気弁座81とそれぞれ協働して吸気ポート14及び排気ポート15をそれぞれ開閉する吸気弁35a,35b及び排気弁36a,36bが取り付けられ、また燃焼室4aに電極を臨ませる点火プラグ23が螺着される。その際、上記吸気弁35a,35b及び排気弁36a,36bはV字状をなすように配置され、吸気及び排気弁35,36には、これらを閉弁方向に付勢する弁ばね61,62が装着される。   As shown in FIGS. 9 to 11, the cylinder heads 4 of the banks B1 and B2 have intake valves that open and close the intake ports 14 and 15 in cooperation with the intake valve seats 80 and the exhaust valve seats 81, respectively. 35a, 35b and exhaust valves 36a, 36b are attached, and a spark plug 23 is screwed so that the electrode faces the combustion chamber 4a. At this time, the intake valves 35a and 35b and the exhaust valves 36a and 36b are arranged in a V shape, and the intake and exhaust valves 35 and 36 are valve springs 61 and 62 for urging them in the valve closing direction. Is installed.

V字状に配置される吸気弁35a,35b及び排気弁36a,36bの各軸線の、シリンダボア3aの中心線に対する傾斜角度θ1、θ2は、図10に示すように、吸気弁座80及び排気弁座81を、シリンダボア3aに挿入される回転刃具82,83により切削加工し得る範囲で極力大きく設定される。   As shown in FIG. 10, the inclination angles θ1 and θ2 of the axes of the intake valves 35a and 35b and the exhaust valves 36a and 36b arranged in a V shape with respect to the center line of the cylinder bore 3a are as shown in FIG. The seat 81 is set as large as possible within a range that can be cut by the rotary blades 82 and 83 inserted into the cylinder bore 3a.

図1、図4、図5及び図6に示すように、第1及び第2バンクB1、B2の吸気ポート14,14に前記第1及び第2吸気道131,132が吸気マニフォルド16を介して接続される。   As shown in FIGS. 1, 4, 5, and 6, the first and second intake passages 131, 132 are connected to the intake ports 14, 14 of the first and second banks B 1, B 2 through the intake manifold 16. Connected.

即ち、吸気マニフォルド16は、第1及び第2バンクB1、B2の吸気ポート14,14と第1及び第2吸気道131,132間をそれぞれ連通すべく水平面上で谷部11外側方にU字状に湾曲した第1及び第2管路17,18を備えており、第1及び第2管路17,18の下流端には個別フランジ191,192が形成され、また上流端には、これらを一体に連結する共通フランジ20が形成され、個別フランジ191,192は第1及び第2シリンダヘッド4,4のシリンダヘッド4,4にそれぞれボルト24,24で結合される。共通フランジ20には、断熱板21と、気化器Cの下流端及び上流端にそれぞれ形成される第1及び第2取り付けフランジ28,29と、エアクリーナAcの、エルボ状の空気出口管22の外周に形成される取り付けフランジ30が複数のボルトにより共締めされる。   That is, the intake manifold 16 is U-shaped on the outer side of the valley portion 11 on the horizontal plane so as to communicate between the intake ports 14 and 14 of the first and second banks B1 and B2 and the first and second intake passages 131 and 132, respectively. The first and second pipes 17 and 18 are curved in a shape, and individual flanges 191 and 192 are formed at the downstream ends of the first and second pipes 17 and 18, respectively. Are connected to the cylinder heads 4 and 4 of the first and second cylinder heads 4 and 4 by bolts 24 and 24, respectively. The common flange 20 includes a heat insulating plate 21, first and second attachment flanges 28 and 29 formed at the downstream end and the upstream end of the vaporizer C, and the outer periphery of the elbow-shaped air outlet pipe 22 of the air cleaner Ac. The mounting flange 30 formed in the step is fastened together by a plurality of bolts.

次に、上記共締め構造について、図4〜図8により説明する。   Next, the joint fastening structure will be described with reference to FIGS.

上記共締め構造には,2本の植え込みボルト25,25と,2本の押さえボルト26,26とが使用される。2本の植え込みボルト25,25は、吸気マニフォルド16の共通フランジ20の一側部の上下2箇所に植え込まれ、共通フランジ20の他側部には,2本の押さえボルト26,26が螺着される上下一対のねじ孔27,27が設けられる。また断熱板21及び気化器Cの第1、第2取り付けフランジ28,29及びエアクリーナAcの取り付けフランジ30には,2本の植え込みボルト25,25が通る第1ボルト孔31,31,31′,31′と,2本の押さえボルト26,26が通る第2ボルト孔32,32とが設けられるが、特に、気化器Cの第1取り付けフランジ28の第1ボルト孔31′,31′は、該フランジ28の外側方に開放した切欠き状に形成される。   Two stud bolts 25 and 25 and two holding bolts 26 and 26 are used in the above-described tightening structure. The two stud bolts 25, 25 are planted in two places above and below one side of the common flange 20 of the intake manifold 16, and two holding bolts 26, 26 are screwed on the other side of the common flange 20. A pair of upper and lower screw holes 27, 27 to be worn are provided. The first and second mounting flanges 28 and 29 of the heat insulating plate 21 and the vaporizer C and the mounting flange 30 of the air cleaner Ac are provided with first bolt holes 31, 31, 31 ′ through which the two stud bolts 25, 25 pass. 31 'and second bolt holes 32, 32 through which the two holding bolts 26, 26 pass. In particular, the first bolt holes 31', 31 'of the first mounting flange 28 of the vaporizer C are The flange 28 is formed in a notch shape opened to the outside.

尚、断熱板21の前後には、必要に応じてガスケットが介装される。   In addition, a gasket is interposed before and after the heat insulating plate 21 as necessary.

図1〜図3、図9、図14及び図15において、第1及び第2バンクB1、B2の各吸気弁35a,35b及び排気弁36a,36bを開閉する動弁装置37が、クランクケース1から各バンクB1、B2のシリンダヘッド4に亙り設けられる。この動弁装置37は、クランク軸7の直上でそれと平行にクランクケース1の前後両端壁で支承されるカム軸38と、クランク軸7の回転を1/2に減速してこのカム軸38に伝達するタイミング伝動装置39(図2参照)とを備える。タイミング伝動装置39は、クランクケース1の着脱可能の端壁1aの内面に隣接する位置でクランク軸7に固設される駆動タイミングギヤ40と、カム軸38に固着されて駆動タイミングギヤ40と噛合する従動タイミングギヤ41とで構成される。   1-3, FIG. 9, FIG. 14 and FIG. 15, the valve operating device 37 for opening and closing the intake valves 35a and 35b and the exhaust valves 36a and 36b of the first and second banks B1 and B2 is the crankcase 1. To the cylinder heads 4 of the banks B1 and B2. The valve operating device 37 includes a camshaft 38 supported by the front and rear end walls of the crankcase 1 directly above and parallel to the crankshaft 7, and the rotation of the crankshaft 7 is reduced by half to the camshaft 38. And a timing transmission device 39 (see FIG. 2) for transmission. The timing transmission device 39 meshes with the drive timing gear 40 fixed to the crankshaft 7 at a position adjacent to the inner surface of the detachable end wall 1 a of the crankcase 1 and the camshaft 38. And a driven timing gear 41.

カム軸38には、図14及び図15に示すように、吸気カム38i及び排気カム38eが一体に形成されており、吸気カム38iは、第1及び第2吸気カムフォロワ42a,42b、第1及び第2吸気プッシュロッド44a,44b、第1及び第2吸気ロッカアーム71a,71b(図1、図3参照)を介して第1及び第2バンクB1、B2の吸気弁35a,35bに連接され、また排気カム38eは、第1及び第2排気カムフォロワ43a,43b、第1及び第2排気プッシュロッド45a,45b、第1及び第2排気ロッカアーム72a,72bを介して第1及び第2バンクB1、B2の排気弁36a,36bに連接される。吸気プッシュロッド44a,44b及び排気プッシュロッド45a,45bは、対応するバンクB1、B2の谷部11側の側面に沿って配置される。   As shown in FIGS. 14 and 15, an intake cam 38 i and an exhaust cam 38 e are integrally formed on the cam shaft 38. The intake cam 38 i includes first and second intake cam followers 42 a and 42 b, first and second intake cam followers 42 a and 42 b. It is connected to the intake valves 35a and 35b of the first and second banks B1 and B2 via the second intake push rods 44a and 44b, the first and second intake rocker arms 71a and 71b (see FIGS. 1 and 3), and The exhaust cam 38e is connected to the first and second banks B1 and B2 via the first and second exhaust cam followers 43a and 43b, the first and second exhaust push rods 45a and 45b, and the first and second exhaust rocker arms 72a and 72b. Are connected to the exhaust valves 36a and 36b. The intake push rods 44a and 44b and the exhaust push rods 45a and 45b are arranged along the side surfaces of the corresponding banks B1 and B2 on the valley 11 side.

図14及び図15に明示するように、第1及び第2吸気カムフォロワ42a,42b及び第1及び第2排気カムフォロワ43a,43bは、カム軸38の直上でそれと平行にクランクケース1に取り付けられる1本のカムフォロワ軸46に揺動自在に支承されるボス部47と、対応するカム38i,38eに摺接するスリッパ部48とを備えており、第1及び第2吸気カムフォロワ42a,42bでは、それらのボス部47,47をカムフォロワ軸46上で互いに当接して隣接させると共に、スリッパ部48,48を吸気カム38iを挟んで正対させるべく、これらスリッパ部48,48の、カム軸38の軸方向に沿う一端部を互い違いに延出させており、また第1及び第2排気カムフォロワ43a,43bでも、それらのボス部47,47をカムフォロワ軸46上で互いに当接して隣接させると共に、スリッパ部48,48を排気カム38eを挟んで正対させるべく、これらスリッパ部48,48の、カム軸38の軸方向に沿う一端部を互い違いに延出させている。   As clearly shown in FIGS. 14 and 15, the first and second intake cam followers 42 a and 42 b and the first and second exhaust cam followers 43 a and 43 b are attached to the crankcase 1 immediately above and parallel to the cam shaft 38. The first cam follower shaft 46 includes a boss portion 47 that is swingably supported by the cam follower shaft 46, and a slipper portion 48 that is in sliding contact with the corresponding cams 38i and 38e. In the first and second intake cam followers 42a and 42b, The boss portions 47 and 47 are brought into contact with and adjacent to each other on the cam follower shaft 46, and the slipper portions 48 and 48 are opposed to each other across the intake cam 38i in the axial direction of the cam shaft 38. The first and second exhaust cam followers 43a and 43b also have boss portions 47 and 47 extending in a staggered manner. The cam follower shaft 46 is abutted against and adjacent to each other, and the slipper portions 48 and 48 are alternately opposed to each other along the axial direction of the cam shaft 38 so that the exhaust cam 38e is sandwiched between the slipper portions 48 and 48. It is extended to.

カムフォロワ軸46は、一端部がクランクケース1の支持孔50に支持され、他端部が、クランクケース1にボルト52で固着されるブラケット51によって支持される。このカムフォロワ軸46には、第1及び第2排気カムフォロワ43a,43bの一方のボス部47の外端面に当接するディスタンスカラー53と、第1及び第2吸気カムフォロワ42a,42b及び第1及び第2排気カムフォロワ43a,43bのボス部47,47間に介在するコイルばね54とが設けられ、これによって第1及び第2吸、排気カムフォロワ42a,43a;42b,43bは、カムフォロワ軸46の所定の中間部に隣接状態に保持される。そして、吸、排気カム38i,38e、並びに第1及び第2吸、排気カムフォロワ42a,43a;42b,43bの大部分は、クランク軸7のクランクピン7pの両端面の延長面F、F間Dに収まるように配置される。   One end of the cam follower shaft 46 is supported by the support hole 50 of the crankcase 1, and the other end is supported by a bracket 51 fixed to the crankcase 1 with a bolt 52. The cam follower shaft 46 includes a distance collar 53 that abuts on an outer end surface of one boss portion 47 of the first and second exhaust cam followers 43a and 43b, first and second intake cam followers 42a and 42b, and first and second. A coil spring 54 interposed between the boss portions 47, 47 of the exhaust cam followers 43a, 43b is provided, whereby the first and second suction and exhaust cam followers 42a, 43a; 42b, 43b are arranged at a predetermined intermediate position of the cam follower shaft 46. Is held adjacent to the part. And most of the suction and exhaust cams 38i and 38e and the first and second suction and exhaust cam followers 42a and 43a; 42b and 43b are extended surfaces F and F between both end surfaces of the crankpin 7p of the crankshaft 7. It is arranged to fit in.

図15に示すように、第1及び第2吸気カムフォロワ42a,42b及び第1及び第2排気カムフォロワ43a,43bの背面には半球状の係合凹部55,55…が形成されており、第1及び第2吸気カムフォロワ42a,42bの係合凹部55,55には第1及び第2吸気プッシュロッ44a,44bの半球状の下端部が係合し、第1及び第2排気カムフォロワ43a,43bの係合凹部55,55には第1及び第2排気プッシュロッド45a,45bの半球状の下端部が係合する。   As shown in FIG. 15, hemispherical engagement recesses 55, 55... Are formed on the back surfaces of the first and second intake cam followers 42a, 42b and the first and second exhaust cam followers 43a, 43b. And the hemispherical lower ends of the first and second intake push locks 44a, 44b engage with the engaging recesses 55, 55 of the second intake cam followers 42a, 42b, and the first and second exhaust cam followers 43a, 43b The hemispherical lower ends of the first and second exhaust push rods 45a and 45b are engaged with the engaging recesses 55 and 55, respectively.

図3に示すように、第1、第2バンクB1、B2において、第1、第2吸気ロッカアーム71a,71b及び第1、第2排気ロッカアーム72a,72aは、それぞれ対応するシリンダヘッド4にロッカ軸85,86を介して揺動自在に軸支される。各吸、排気ロッカアーム71a,72a;71b,72bは、これらの吸、排気プッシュロッド44a,45a;44b,45b側端部が相互に近接するように平面視でハ字状に配置され、これにより各吸、排気プッシュロッド44a,45a;44b,45bが相互に近接配置される。   As shown in FIG. 3, in the first and second banks B1 and B2, the first and second intake rocker arms 71a and 71b and the first and second exhaust rocker arms 72a and 72a are respectively connected to the corresponding cylinder heads 4 by rocker shafts. It is pivotally supported via 85 and 86. The suction and exhaust rocker arms 71a, 72a; 71b, 72b are arranged in a letter C shape in plan view so that the suction and exhaust push rods 44a, 45a; 44b, 45b side ends are close to each other. The suction and exhaust push rods 44a, 45a; 44b, 45b are arranged close to each other.

こうして隣接配置される各吸、排気プッシュロッド44a,45a;44b,45bを収容する管状のロッドカバー59,60(図1、図9、図11及び図12参照)が各バンクB1、B2に次のように取り付けられる。   Tubular rod covers 59 and 60 (see FIGS. 1, 9, 11 and 12) for housing the suction and exhaust push rods 44a and 45a; 44b and 45b adjacent to each other are next to the banks B1 and B2. It is attached like this.

即ち、各バンクB1、B2には、その上、下端部からそれぞれ両バンクB1、B2間の谷部11側に張り出した上部及び下部支持部74,75が一体に形成され、これら上部支持部74にはロッドカバー59,60の上端部が圧入される上部取り付け孔74h,74hが、また下部支持部75にはロッドカバー59,60の下端部が圧入される下部取り付け孔75h,75hが設けられる。各上部取り付け孔74h及び下部取り付け孔75hは同軸上に配置されると共に、上部取り付け孔74hは下部取り付け孔75hより大径に形成される。これに対応してロッドカバー59,60の上端部59a,60aは、他の部分より大径に形成される。したがって、ロッドカバー59,60は、上部取り付け孔74h,74hに上方から容易に挿入することができ、そして上部取り付け孔74h,74h及び下部取り付け孔75h,75hへの圧入を略同時に行うことができる。   That is, each of the banks B1 and B2 is integrally formed with upper and lower support portions 74 and 75 projecting from the upper and lower ends thereof to the valley 11 side between the banks B1 and B2, respectively. Are provided with upper mounting holes 74h and 74h into which the upper ends of the rod covers 59 and 60 are press-fitted, and the lower support part 75 is provided with lower mounting holes 75h and 75h into which the lower ends of the rod covers 59 and 60 are press-fitted. . Each upper mounting hole 74h and lower mounting hole 75h are coaxially arranged, and the upper mounting hole 74h is formed to have a larger diameter than the lower mounting hole 75h. Correspondingly, the upper end portions 59a, 60a of the rod covers 59, 60 are formed to have a larger diameter than the other portions. Therefore, the rod covers 59 and 60 can be easily inserted into the upper mounting holes 74h and 74h from above, and can be press-fitted into the upper mounting holes 74h and 74h and the lower mounting holes 75h and 75h almost simultaneously. .

各バンクB1、B2において、弁ばね61,62及び吸気ロッカアーム71a,71b及び排気ロッカアーム72a,72bは、各シリンダヘッド4及びヘッドカバー5間に画成される動弁室63に収容され、この動弁室63は、ロッドカバー59,60の中空部を通してクランクケース1内と連通される。   In each of the banks B1 and B2, the valve springs 61 and 62, the intake rocker arms 71a and 71b, and the exhaust rocker arms 72a and 72b are accommodated in a valve operating chamber 63 defined between each cylinder head 4 and the head cover 5, and this valve The chamber 63 communicates with the inside of the crankcase 1 through the hollow portions of the rod covers 59 and 60.

一方、図9及び図12に示すように、各バンクB1、B2の冷却フィン6には、上記ロッドカバー59,60の各バンクB1、B2外壁への近接配置を可能にするU字状の切欠き6aが、該切欠き6aの内面がロッドカバー59,60の、前記大径部59a,60aよりも小径の中間部59b,60b外周に対向するように設けられる。 On the other hand, as shown in FIGS. 9 and 12, the cooling fins 6 of the banks B1 and B2 have U-shaped cuts that enable the rod covers 59 and 60 to be disposed close to the outer walls of the banks B1 and B2. The notch 6a is provided so that the inner surface of the notch 6a faces the outer periphery of the intermediate portions 59b and 60b of the rod covers 59 and 60 having a smaller diameter than the large diameter portions 59a and 60a .

再び図2において、カム軸38には、カム軸38の一般面から排気カム38eのベース面にかけて平坦部64が形成され、この平坦部64にデコンプ部材66が枢軸65を介して揺動自在に支持される。このデコンプ部材66は鋼板製であって、V型エンジンEの停止ないし始動時、排気カム38eのベース面側に位置して該ベース面より先端部を突出させるデコンプアーム66aと、V型エンジンEのアイドリング以上の回転時、上記デコンプアーム66aを前記ベース面より退去させるべく遠心力を発生する遠心ウエイト66bとよりなっており、このデコンプ部材66には、デコンプアーム66aを前記ベース面側に位置させる方向に付勢する戻しばね69が接続され、以上によりデコンプ装置70が構成される。   In FIG. 2 again, a flat portion 64 is formed on the cam shaft 38 from the general surface of the cam shaft 38 to the base surface of the exhaust cam 38 e, and the decompression member 66 is swingable through the pivot 65 on the flat portion 64. Supported. The decompression member 66 is made of a steel plate. When the V-type engine E is stopped or started, the decompression member 66a is located on the base surface side of the exhaust cam 38e and protrudes from the base surface. And a centrifugal weight 66b for generating a centrifugal force to retreat the decompression arm 66a from the base surface during rotation more than idling. The decompression arm 66a is positioned on the base surface side of the decompression member 66. The return spring 69 that is biased in the direction to be moved is connected, and the decompression device 70 is configured as described above.

而して、V型エンジンEの始動時には、デコンプアーム66aは、その先端部を排気カム38eのベース面より突出させる位置を占める(図15鎖線示参照)ので、圧縮行程でもデコンプアーム66aによる第1及び第2排気カムフォロワ43a,43bの微小リフトにより第1及び第2バンクB1、B2の排気弁36a,36bを僅かに開くことでシリンダボア3a,3a内の圧縮圧力を下げ、始動負荷を軽減することができる。V型エンジンEの始動後、カム軸38が所定回転数以上に回転すれば、遠心ウエイト66bがそれに働く遠心力で戻しばね69のセット荷重に抗して半径方向外方に揺動するので、デコンプアーム66aを排気カム38eのベース面から退去させることになる。   Thus, when the V-type engine E is started, the decompression arm 66a occupies a position in which the tip of the decompression arm 66a protrudes from the base surface of the exhaust cam 38e (see the chain line in FIG. 15). By slightly opening the exhaust valves 36a and 36b of the first and second banks B1 and B2 by the minute lift of the first and second exhaust cam followers 43a and 43b, the compression pressure in the cylinder bores 3a and 3a is lowered, and the starting load is reduced. be able to. If the camshaft 38 rotates more than a predetermined number of revolutions after starting the V-type engine E, the centrifugal weight 66b swings radially outward against the set load of the return spring 69 by the centrifugal force acting on it. The decompression arm 66a is moved away from the base surface of the exhaust cam 38e.

以上において、吸、排気プッシュロッド44a,45a;44b,45bには全て互換性が付与され、同一のプッシュロッドの使用が可能となっている。また吸、排気カムフォロワ42a,43a;42b,43bにも全て互換性が付与され、同一のカムフォロワの使用が可能となっている。さらにロッドカバー59,60にも互換性が付与され、同一のロッドカバーの使用が可能となっている。こうすることで部品の量産性を高めることができる。   In the above, the suction and exhaust push rods 44a, 45a; 44b, 45b are all provided with compatibility, and the same push rod can be used. In addition, the intake and exhaust cam followers 42a, 43a; 42b, 43b are all compatible, and the same cam follower can be used. Furthermore, the rod covers 59 and 60 are provided with compatibility, and the same rod cover can be used. In this way, the mass productivity of parts can be increased.

次に、この実施例の作用にいて説明する。 Next, it describes the operation of this embodiment.

前述のように、第1及び第2バンクB1、B2は、両バンクB1、B2の開き角度αが90°となるように配置される一方、クランク軸7には、各バンクB1、B2のピストン8の慣性力と釣り合うカウンタウエイト7wがクランクピン7pと反対に付設されるので、周知のように、各バンクB1、B2のピストン8の上死点及び下死点での慣性力は、カウンタウエイト7wの遠心力と釣り合うことになり、したがって特別な1次バランサ機構を設けずとも、V型エンジンEの1次慣性力を平衡させることができる。   As described above, the first and second banks B1 and B2 are arranged such that the opening angle α of both banks B1 and B2 is 90 °, while the crankshaft 7 has pistons of the banks B1 and B2. Since the counterweight 7w that balances the inertial force of 8 is attached opposite to the crankpin 7p, the inertial force at the top dead center and the bottom dead center of the pistons 8 of the banks B1 and B2 is, as is well known, Therefore, the primary inertial force of the V-type engine E can be balanced without providing a special primary balancer mechanism.

しかも、第1及び第2バンクB1、B2は、第1バンクB1のシリンダ中心線A1及び第2バンクB2のシリンダ中心線A2がそれぞれクランク軸7の回転中心A3から両バンクB1、B2と反対側に偏倚した点Pを通るように配置されるので、第1及び第2バンクB1、B2間に画成される谷部11を、両バンクB1、B2の開き角度α=90°を維持したまゝで広くすることができ、したがって。この谷部11にはV型エンジンEの一補機である気化器C全体と、エアクリーナAcの一部とを余裕をもって収容し得て、全高が低くコンパクトなV型エンジンEを提供することができる。   Moreover, the first and second banks B1 and B2 are such that the cylinder center line A1 of the first bank B1 and the cylinder center line A2 of the second bank B2 are opposite to the banks B1 and B2 from the rotation center A3 of the crankshaft 7, respectively. Therefore, the valley portion 11 defined between the first and second banks B1 and B2 is maintained at the opening angle α = 90 ° between the banks B1 and B2. Can be widened with acupuncture and therefore. The valley portion 11 can accommodate the entire carburetor C, which is a supplement to the V-type engine E, and a part of the air cleaner Ac with a margin, and provides a compact V-type engine E with a low overall height. it can.

また、その際、気化器Cは、第1及び第2バンクB1、B2の配列方向に並ぶ水平方向(クランク軸7と直交する方向)の第1及び第2吸気道131,132を有する2連型に構成されると共に、一対の管路17,18を介して第1及び第2バンクB1、B2の吸気ポート14,14に個別に接続されるので、両バンクB1、B2の吸気干渉を回避すると共に吸気抵抗を最少にして、V型エンジンEの出力性能向上を図ることができる。   Further, at that time, the carburetor C has two series of first and second intake passages 131 and 132 in a horizontal direction (a direction orthogonal to the crankshaft 7) arranged in the arrangement direction of the first and second banks B1 and B2. Since it is configured as a mold and individually connected to the intake ports 14 and 14 of the first and second banks B1 and B2 through a pair of pipes 17 and 18, intake interference between both banks B1 and B2 is avoided. In addition, the intake resistance can be minimized and the output performance of the V-type engine E can be improved.

しかも、上記一対の管路17,18は、それらの上流側端部に、それらを一体に連結する共通フランジ20を形成して吸気マニフォルド16に構成されるので、共通フランジ20を2連型気化器Cの下流端に接続することで、V型エンジンEの吸気系を簡単に構成することができ、その吸気系の組立性が良好となる。   In addition, the pair of pipe lines 17 and 18 are formed in the intake manifold 16 by forming a common flange 20 integrally connecting them at their upstream end portions, so that the common flange 20 is double vaporized. By connecting to the downstream end of the vessel C, the intake system of the V-type engine E can be easily configured, and the assemblability of the intake system is improved.

吸気マニフォルド16の共通フランジ20に、断熱板21、気化器C及びエアクリーナAcを取り付けるに当たっては、図7(A)に示すように、先ず、共通フランジ20に立設される上下2本の植え込みボルト25,25に、断熱板21の第1ボルト孔31,31を嵌め込み、次いで気化器Cの第1取り付けフランジ28の切欠き状の第1ボルト孔31′,31′を植え込みボルト25,25にその側方から係合した後(図7(A)参照)、気化器C全体を断熱板21側に移動させつゝ、第2取り付けフランジ29の第1ボルト孔31,31を植え込みボルト25,25に嵌め込む(図8参照)。こうすることで、軸方向長さが比較的長い気化器Cを、気化器Cの軸方向長さより短い移動量で植え込みボルト25,25との所定の嵌合位置にセットすることができるから、セット作業を迅速に行うことができ、しかも植え込みボルト25,25の外端部外方に気化器C全体を受け入れるような広い空間が存在しない場合でも、気化器Cの定位置への仮止めが可能となる。この実施例の場合は、図4に示すように、植え込みボルト25,25の外端部外方に、大径の前記従動タイミングギヤ41の存在によりクランクケース1の膨出部1sが存在しており、この膨出部1sが気化器Cのフロートチャンバ12aや燃料カット用電磁弁12bの、植え込みボルト25,25の外端部外方への受け入れを邪魔するので、膨出部1sに干渉されない上記気化器Cの定位置への仮止め構造は極めて有効である。   In attaching the heat insulating plate 21, the vaporizer C, and the air cleaner Ac to the common flange 20 of the intake manifold 16, first, as shown in FIG. The first bolt holes 31, 31 of the heat insulating plate 21 are fitted into 25, 25, and then the notched first bolt holes 31 ′, 31 ′ of the first mounting flange 28 of the vaporizer C are inserted into the stud bolts 25, 25. After engaging from the side (see FIG. 7A), the entire vaporizer C is moved to the heat insulating plate 21 side, and the first bolt holes 31, 31 of the second mounting flange 29 are inserted into the stud bolts 25, 25 (see FIG. 8). By carrying out like this, since the carburetor C whose axial direction length is comparatively long can be set to the predetermined fitting position with the implantation bolts 25 and 25 by the movement amount shorter than the axial direction length of the carburetor C, Even when there is no wide space for receiving the entire carburetor C outside the outer ends of the implanted bolts 25, 25, the setting operation can be performed quickly, and the temporary fixing of the carburetor C to the fixed position is possible. It becomes possible. In the case of this embodiment, as shown in FIG. 4, the bulging portion 1s of the crankcase 1 is present outside the outer ends of the studs 25, 25 due to the presence of the large-diameter driven timing gear 41. The bulging portion 1s prevents the float chamber 12a of the carburetor C and the fuel-cut solenoid valve 12b from receiving the implanted bolts 25, 25 outside the outer ends, so that the bulging portion 1s is not interfered with. The temporary fixing structure of the vaporizer C at a fixed position is extremely effective.

次いで、図8に示すように、エアクリーナAcの取り付けフランジ30の第1ボルト孔31,31を植え込みボルト25,25に嵌め込み、最後に植え込みボルト25,25の外端部にナット33,33を螺合緊締する一方、全ての第2ボルト孔32,32に押さえボルト26,26を挿通して、共通フランジ20のねじ孔27,27に螺合緊締する。押さえボルト26の第2ボルト孔32への挿通に際しては、押さえボルト26を気化器Cの全長以上に移動させる必要があるが、押さえボルト26は細いから、その移動空間は一般的に容易に確保できる。   Next, as shown in FIG. 8, the first bolt holes 31, 31 of the mounting flange 30 of the air cleaner Ac are fitted into the stud bolts 25, 25, and finally nuts 33, 33 are screwed onto the outer ends of the stud bolts 25, 25. On the other hand, the holding bolts 26 and 26 are inserted into all the second bolt holes 32 and 32 and screwed and tightened into the screw holes 27 and 27 of the common flange 20. When the presser bolt 26 is inserted into the second bolt hole 32, it is necessary to move the presser bolt 26 over the entire length of the vaporizer C. However, since the presser bolt 26 is thin, its movement space is generally easily secured. it can.

以上において,2本の植え込みボルト25,25を使用することは、これら植え込みボルト25,25に断熱板21、気化器C及びエアクリーナAcの各2個の第1ボルト孔31,31を嵌め込むことにより、これら断熱板21、気化器C及びエアクリーナAcの植え込みボルト25,25周りの回転を阻止した確実な仮止め状態を得ることになり、したがってその後の押さえボルト26,26の各第2ボルト孔32,32への挿通作業及びねじ孔27,27への螺合作業が容易となる。   In the above, the use of the two stud bolts 25 and 25 means that the two first bolt holes 31 and 31 of the heat insulating plate 21, the vaporizer C, and the air cleaner Ac are fitted into the stud bolts 25 and 25, respectively. Thus, a reliable temporary fixing state in which the rotation of the heat insulating plate 21, the vaporizer C and the air cleaner Ac around the implanted bolts 25 and 25 is prevented is obtained, and accordingly, the second bolt holes of the subsequent holding bolts 26 and 26 are obtained. The insertion operation to 32 and 32 and the screwing operation to the screw holes 27 and 27 become easy.

また押さえボルト26,26を併用することで、切欠き状の第1ボルト孔31′,31′の存在に影響されることなく、気化器Cを定位置に的確に固定することができ、さらに気化器Cの下流及び上流端に形成される第1及び第2取り付けフランジ28,29が植え込みボルト25,25及び押さえボルト26,26により共通フランジ20に締結されるので、気化器Cの取り付け強度を高めることができる。   Further, by using the holding bolts 26 and 26 together, the carburetor C can be accurately fixed in place without being affected by the presence of the notched first bolt holes 31 ′ and 31 ′. Since the first and second attachment flanges 28 and 29 formed at the downstream and upstream ends of the vaporizer C are fastened to the common flange 20 by the implantation bolts 25 and 25 and the holding bolts 26 and 26, the attachment strength of the vaporizer C Can be increased.

共通フランジ20から気化器C及びエアクリーナAcを取り外す際には、上記の作業手順を逆に行えばよい。   When removing the vaporizer C and the air cleaner Ac from the common flange 20, the above work procedure may be reversed.

動弁装置37においては、各バンクB1、B2の各吸、排気ロッカアーム71a,72a;71b,75bを、これらの吸、排気プッシュロッド44a,45a;44b,45b側端部が相互に近接するように平面視でハ字状に配置して、各吸、排気プッシュロッド44a,45a;44b,45bを相互に近接させ、各吸、排気プッシュロッド44a,45a;44b,45bをそれぞれ収容する各一対の管状のロッドカバー59,60の上下両端を、各バンクB1、B2の上、下端部からそれぞれ前記谷部11側に張り出した上部及び下部支持部74,75に支持させると共に、各バンクB1、B2の冷却フィン6に、ロッドカバー59,60の各バンクB1、B2外壁への近接配置を可能にする切欠き6aを設けたので、各吸、排気プッシュロッド44a,45a;44b,45bの大部分を各バンクB1、B2外に配置することが可能となり、各バンクB1、B2にロッド室の形成を不要とすると共に、駄肉を削減して、各バンクB1、B2のコンパクト化、延いては軽量化を図ることができ、しかもロッド室を持たない分、各バンクB1、B2のシリンダボア3aの外壁を広い範囲で外気に露出させることが可能となり、空冷効果を高めることができる。   In the valve train 37, the suction and exhaust rocker arms 71a, 72a; 71b, 75b of the banks B1, B2 are arranged so that their suction and exhaust push rods 44a, 45a; 44b, 45b side ends are close to each other. Each pair of suction and exhaust push rods 44a, 45a; 44b, 45b are arranged close to each other in plan view, and each pair of suction and exhaust push rods 44a, 45a; 44b, 45b is accommodated. The upper and lower ends of the tubular rod covers 59, 60 are supported by upper and lower support portions 74, 75 projecting from the upper and lower ends of the banks B1, B2 to the valley 11 side, respectively, and the banks B1, Since the cooling fin 6 of B2 is provided with a notch 6a that enables the rod covers 59 and 60 to be arranged close to the outer walls of the banks B1 and B2, each suction and exhaust block is provided. Most of the shrods 44a and 45a; 44b and 45b can be arranged outside the banks B1 and B2, so that the formation of the rod chambers in the banks B1 and B2 is unnecessary, and the waste is reduced. The banks B1 and B2 can be made compact, and hence lighter, and since the rod chamber is not provided, the outer walls of the cylinder bores 3a of the banks B1 and B2 can be exposed to the outside in a wide range. The air cooling effect can be enhanced.

また各バンクB1、B2外に配置される吸、排気プッシュロッド44a,45a;44b,45bは、各バンクB1、B2の上、下端部からそれぞれ前記谷部11側に張り出した上部及び下部支持部74,75に支持されるロッドカバー59,60に収容されて保護され、しかもロッドカバー59,60は、第1及び第2バンクB1、B2間の谷部11側に配置されることで、両バンクB1、B2によりロッドカバー59,60を他物との接触から保護される。   The suction and exhaust push rods 44a, 45a; 44b, 45b arranged outside the banks B1, B2 are upper and lower support portions that project from the upper and lower ends of the banks B1, B2 to the valley 11 side, respectively. The rod covers 59 and 60 are housed and protected by the rod covers 59 and 60 supported by 74 and 75, and the rod covers 59 and 60 are disposed on the valley 11 side between the first and second banks B1 and B2. The rod covers 59 and 60 are protected from contact with other objects by the banks B1 and B2.

さらに各バンクB1、B2の各吸、排気ロッカアーム71a,72a;71b,75bを、これらの吸、排気プッシュロッド44a,45a;44b,45b側端部が相互に近接するように平面視でハ字状に配置して、各吸、排気プッシュロッド44a,45a;44b,45bを相互に近接させ、各バンクB1、B2の冷却フィン6に、各吸、排気プッシュロッド44a,45a;44b,45bを収容するロッドカバー59,60の各バンクB1、B2外壁への近接配置を可能にする切欠き6aを設けたので、切欠き6aの幅を最小にして、切欠きによる冷却フィン6の放熱機能の低下を最小限にとどめることができる。   Further, each suction and exhaust rocker arm 71a, 72a; 71b, 75b of each bank B1, B2 is shaped like a letter C in plan view so that these suction and exhaust push rods 44a, 45a; 44b, 45b side ends are close to each other. The suction and exhaust push rods 44a and 45a; 44b and 45b are arranged close to each other, and the suction and exhaust push rods 44a and 45a; 44b and 45b are placed on the cooling fins 6 of the banks B1 and B2. Since the notches 6a that allow the rod covers 59 and 60 to be accommodated to be disposed close to the outer walls of the banks B1 and B2 are provided, the width of the notches 6a is minimized and the heat dissipation function of the cooling fins 6 by the notches is provided. Degradation can be minimized.

また各カムフォロワ42a,43a,42b,43bを、カム軸38の直上でそれと平行にクランクケース1に取り付けられる1本のカムフォロワ軸46に揺動自在に支承されるボス部47と、対応するカム38i,38eに摺接するスリッパ部48とで構成し、第1及び第2吸気カムフォロワ42a,42bでは、それらのボス部47,47をカムフォロワ軸46上で互いに当接して隣接させると共に、スリッパ部48,48を吸気カム38iを挟んで正対させるべく、これらスリッパ部48,48の、カム軸38の軸方向に沿う一端部を互い違いに延出させ、また第1及び第2排気カムフォロワ43a,43bでも、それらのボス部47,47をカムフォロワ軸46上で互いに当接して隣接させると共に、スリッパ部48,48を排気カム38eを挟んで正対させるべく、これらスリッパ部48,48の、カム軸38の軸方向に沿う一端部を互い違いに延出させたので、単一のカム軸38及びカムフォロワ軸46上で第1吸、排気カムフォロワ42a,43a及び第2吸、排気カムフォロワ42b,43bを集中配置することができ、これにより動弁装置37のコンパクト化、特に、カム軸38の短縮化が可能となる。しかも第1及び第2吸気カムフォロワ42a,42b、第1及び第2排気カムフォロワ43a,43bのそれぞれにおいて、カム38i,38eを挟んで対向するスリッパ48,48;48,48を正対させるべく、これらスリッパの、カム軸38の軸方向に沿う一端部を互い違いに延出させたことで、スリッパ48,48;48,48の対応するカム38i,38eとの摺接面積を充分に確保することができ、したがって摺接部の面圧を充分に低下させ、その耐摩耗性の向上に寄与し得る。   Each cam follower 42a, 43a, 42b, 43b is mounted on a cam follower shaft 46 mounted on the crankcase 1 directly above and parallel to the cam shaft 38, and a corresponding cam 38i. In the first and second intake cam followers 42a and 42b, the boss portions 47 and 47 are brought into contact with and adjacent to each other on the cam follower shaft 46, and the slipper portion 48 and One end of the slippers 48 and 48 along the axial direction of the cam shaft 38 is alternately extended so that the 48 is opposed to the intake cam 38i, and the first and second exhaust cam followers 43a and 43b are also provided. The bosses 47 and 47 are brought into contact with and adjacent to each other on the cam follower shaft 46, and the slippers 48 and 48 are connected to the exhaust cover. Since the end portions of the slipper portions 48, 48 along the axial direction of the cam shaft 38 are alternately extended so as to face each other across the 38e, the first cam shaft 38 and the cam follower shaft 46 have a first end. The suction and exhaust cam followers 42a and 43a and the second suction and exhaust cam followers 42b and 43b can be arranged in a concentrated manner, whereby the valve operating device 37 can be made compact, in particular, the cam shaft 38 can be shortened. In addition, in each of the first and second intake cam followers 42a and 42b and the first and second exhaust cam followers 43a and 43b, the slippers 48 and 48; 48 and 48 facing each other with the cams 38i and 38e therebetween are opposed to each other. By alternately extending the end portions of the slipper along the axial direction of the cam shaft 38, it is possible to sufficiently secure a sliding contact area with the corresponding cams 38i and 38e of the slippers 48 and 48; Therefore, it is possible to sufficiently reduce the surface pressure of the sliding contact portion and contribute to the improvement of the wear resistance.

また両バンクB1、B2の第1及び第2吸、排気カムフォロワ42a,43a;42b,43b、並びに吸、排気カム38i,38eの大部分をクランク軸7のクランクピン7pの両端面の延長面F、F間Dに収めたので、動弁装置37のコンパクト化を一層図ることができると共に、クランク軸7の回転中、クランクピン7p周りから飛散する潤滑オイルにより吸、排気カム38i,38e周りを効果的に潤滑することができる。   Also, the first and second suction and exhaust cam followers 42a and 43a; 42b and 43b of both banks B1 and B2 and the majority of the suction and exhaust cams 38i and 38e are extended surfaces F of both end surfaces of the crankpin 7p of the crankshaft 7. , The valve operating device 37 can be made more compact, and the crankshaft 7 is sucked by the lubricating oil scattered around the crankpin 7p and rotated around the exhaust cams 38i and 38e while the crankshaft 7 is rotating. It can be effectively lubricated.

さらにカム軸38に、その一般面から排気カム38eのベース面にかけて平坦部64を形成し、この平坦部64にデコンプ部材66を揺動自在に軸支し、このデコンプ部材66を、V型エンジンEの停止ないし始動時、排気カム38eのベース面側の作動位置にあって、V型エンジンEの圧縮行程で第1及び第2排気カムフォロワ43a,43bをリフトさせるべく該ベース面より先端部を突出させるデコンプアーム66aと、V型エンジンEのアイドリング以上の回転時、前記デコンプアーム66aを前記ベース面より退去させるべく遠心力を発生する遠心ウエイト66bとより構成し、このデコンプ部材66に、デコンプアーム66aを前記作動位置に向かって付勢する戻しばね69を接続したので、第1及び第2排気カムフォロワ43a,43bにおいて、それらのボス部をカムフォロワ軸上で互いに当接して隣接させると共に、スリッパを排気カムを挟んで正対させるべく、これらスリッパの、カム軸38の軸方向に沿う一端部を互い違いに延出させたことゝ相俟って、デコンプ部材66の作動位置では、デコンプアーム66aの先端部を排気カム38e側に僅かに突出させるだけで、その先端部を第1及び第2排気カムフォロワ43a,43bに略等しく摺接させながら、それらに微小リフトを付与することができる。その際、デコンプアーム66aの先端部の排気カム38e側への突出長さが小さくて足りることは、両バンクB1、B2に共通する単一のデコンプ装置70のコンパクト化を図ること、並びに排気カム38eのベース面の有効面積の、前記平坦部64の形成に伴なう減少を最小限にとどめ、排気カム38e及び排気カムフォロワ43a,43bの耐久性の向上を図ることを可能にすることを意味する。   Further, a flat portion 64 is formed on the cam shaft 38 from its general surface to the base surface of the exhaust cam 38e, and a decompression member 66 is pivotally supported on the flat portion 64 so that the decompression member 66 can be used as a V-type engine. When E is stopped or started, the tip of the exhaust cam 38e is at the operating position on the base surface side so that the first and second exhaust cam followers 43a and 43b are lifted during the compression stroke of the V-type engine E. A decompression arm 66a that protrudes, and a centrifugal weight 66b that generates centrifugal force to cause the decompression arm 66a to retreat from the base surface when the V-type engine E rotates more than idling, and the decompression member 66 includes Since the return spring 69 that biases the arm 66a toward the operating position is connected, the first and second exhaust cam followers 43 are connected. 43b, the bosses are abutting and adjacent to each other on the cam follower shaft, and the ends of the slippers along the axial direction of the cam shaft 38 are staggered so that the slippers face each other with the exhaust cam interposed therebetween. In combination with the extension of the decompression member 66, the distal end portion of the decompression arm 66a is slightly protruded toward the exhaust cam 38e, and the distal end portion of the decompression arm 66a is projected to the first and second exhaust cam followers 43a. , 43b can be given a minute lift while being slidably contacted substantially equally. At this time, the fact that the protruding length of the distal end portion of the decompression arm 66a toward the exhaust cam 38e is small is sufficient to reduce the size of the single decompression device 70 common to both the banks B1 and B2, and the exhaust cam. This means that it is possible to minimize the reduction of the effective area of the base surface of 38e due to the formation of the flat portion 64 and to improve the durability of the exhaust cam 38e and the exhaust cam followers 43a and 43b. To do.

また前記平坦部64は、カム軸38の一般面から排気カムのベース面にかけて形成され、この平坦部64に軸支したデコンプ部材66のデコンプアーム66aを、V型エンジンEの停止ないし始動時、排気カム38eのベース面側に突出させるようにしたので、第1及び第2排気カムフォロワ43a,43bのスリッパ部38,38を排気カム38eの外側方に張り出す必要がなく、動弁装置37のコンパクト化を維持しつゝ始動時のデコンプ作用を行うことができる。   The flat portion 64 is formed from the general surface of the camshaft 38 to the base surface of the exhaust cam, and the decompression arm 66a of the decompression member 66 pivotally supported on the flat portion 64 is used when the V-type engine E is stopped or started. Since the exhaust cam 38e protrudes toward the base surface side, the slipper portions 38, 38 of the first and second exhaust cam followers 43a, 43b do not need to protrude outward from the exhaust cam 38e. Decompression at start-up can be performed while maintaining compactness.

以上、本発明の実施例を詳述したが、本発明はその要旨を逸脱しない範囲で種々の設計変更を行うことが可能である。   As mentioned above, although the Example of this invention was explained in full detail, this invention can perform a various design change in the range which does not deviate from the summary.

本発明に係る空冷式汎用V型エンジンの縦断正面図。1 is a longitudinal front view of an air-cooled general-purpose V-type engine according to the present invention. 図1の2−2線断面図。FIG. 2 is a sectional view taken along line 2-2 in FIG. 1. 図1の3矢視図。FIG. 3 is a view taken in the direction of arrow 3 in FIG. 1. 図1の4−4線断面図。FIG. 4 is a sectional view taken along line 4-4 of FIG. 図4の5−5線断面図。FIG. 5 is a sectional view taken along line 5-5 of FIG. 図4の6−6線断面図。FIG. 6 is a sectional view taken along line 6-6 in FIG. 図1の4−4線断面図。FIG. 4 is a sectional view taken along line 4-4 of FIG. 気化器の取り付け要領説明図。Explanatory drawing of how to install the vaporizer. 図1中の第1バンク部の拡大図。The enlarged view of the 1st bank part in FIG. 図9の10−10線に沿う第1バンク単体断面図。FIG. 10 is a cross-sectional view of a first bank alone taken along line 10-10 in FIG. 9; 図19の11矢視図。FIG. 11 is a view taken in the direction of arrow 11 in FIG. 19. 図9の12矢視図。FIG. 12 is a view taken in the direction of arrow 12 in FIG. 9. 図12の13−13線断面図。FIG. 13 is a sectional view taken along line 13-13 of FIG. 図2の14部拡大図。FIG. 14 is an enlarged view of a portion 14 in FIG. 2. 図14の15−15線断面図。FIG. 15 is a sectional view taken along line 15-15 in FIG. 14;

B1・・・・第1バンク
B2・・・・第2バンク
E・・・・・V型エンジン
1・・・・・クランクケース
3・・・・・シリンダブロック
3a・・・・シリンダボア
4・・・・・シリンダヘッド
7・・・・・クランク軸
11・・・・谷部
35a,35b・・・吸気弁
36a,36b・・・排気弁
38・・・・カム軸
42a,42b・・・第1、第2吸気カムフォロワ
43a,43b・・・第1、第2排気カムフォロワ
44a,44b・・・第1、第2吸気プッシュロッド
45a,45b・・・第1、第2排気プッシュロッド
59,60・・・・・ロッドカバー
59a,60a・・・ロッドカバーの上端部(大径部)
59b,60b・・・ロッドカバーの中間部
71a,71b・・・吸気ロッカアーム
72a,72b・・・排気ロッカアーム
74・・・・上部支持部
75a・・・上部取り付け孔
75・・・・下部支持部
75a・・・下部取り付け孔
B1... First bank B2... Second bank E ... V-type engine 1 ... Crankcase 3 ... Cylinder block 3a ... Cylinder bore 4 ... ... Cylinder head 7 ... Crankshaft 11 ... Valleys 35a, 35b ... Intake valves 36a, 36b ... Exhaust valves 38 ... Camshafts 42a, 42b ... 1, second intake cam followers 43a, 43b ... first, second exhaust cam followers 44a, 44b ... first, second intake push rods 45a, 45b ... first, second exhaust push rods 59, 60・ ・ ・ ・ ・ Rod cover
59a, 60a ... The upper end of the rod cover (large diameter part)
59b, 60b ... Rod cover intermediate portions 71a, 71b ... Intake rocker arms 72a, 72b ... Exhaust rocker arms 74 ... Upper support 75a ... Upper mounting hole 75 ... Lower support 75a ... Lower mounting hole

Claims (1)

それぞれシリンダボア(3a)を有して、相互間に谷部(11)を画成するようにV字状に並ぶ第1及び第2バンク(B1、B2)を、クランク軸(7)を支持するクランクケース(1)に連設すると共に、各バンク(B1、B2)の外壁に冷却フィン(6)を突設し、各バンク(B1、B2)の頭部に吸、排気弁(35a,36a;35b,36b)をV字状に配置し、これら吸、排気弁(35a,36a;35b,36b)を開閉駆動する動弁装置(37)を、クランク軸(7)の上方に配設されてクランク軸(7)から駆動されるカム軸(38)と、このカム軸(38)の吸、排気カム(38i,38e)によりそれぞれ昇降される第1吸、排気カムフォロワ(42a,43a)及び第2吸、排気カムフォロワ(42b,43b)と、これら第1吸、排気カムフォロワ(42a,43a)及び第2吸、排気カムフォロワ(42b,43b)に下端をそれぞれ連接して第1及び第2バンク(B1、B2)の前記谷部(11)側にそれぞれ配設される第1吸、排気プッシュロッド(44a,45a)及び第2吸、排気プッシュロッド(44b,45b)と、これら第1吸、排気プッシュロッド(44a,45a)及び第2吸、排気プッシュロッド(44b,45b)の上端を対応するバンク(B1、B2)の吸、排気弁(35a,36a;35b,36b)にそれぞれ連接する第1吸、排気ロッカアーム(71a,72a)及び第2吸、排気ロッカアーム(71b,72b)とで構成した空冷式V型エンジンにおいて、 シリンダボア(3a)を有するシリンダブロック(3)と、吸、排気弁(35a,36a;35b,36b)を支持するシリンダヘッド(4)とを一体成形して各バンク(B1、B2)を構成すると共に、その各バンク(B1、B2)の各吸、排気ロッカアーム(71a,72a;71b,72b)を、これらの吸、排気プッシュロッド(44a,45a;44b,45b)側端部が相互に近接するように平面視でハ字状に配置して、各吸、排気プッシュロッド(44a,45a;44b,45b)を相互に近接させ、
各吸、排気プッシュロッド(44a,45a;44b,45b)を個別に収容すべく互いに並列した各一対の管状のロッドカバー(59,60)の下端部を、各バンク(B1、B2)のシリンダブロック(3)に一体に形成されてそれぞれ前記谷部(11)側に張り出した下部支持部(75)に設けた一対の下部取り付け孔(75h)にそれぞれ圧入させると共に、その各一対の管状のロッドカバー(59,60)の上端部(59a,60a)を、各バンク(B1、B2)のシリンダヘッド(4)に一体に形成されてそれぞれ前記谷部(11)側に張り出した上部支持部(74)に設けた一対の上部取り付け孔(74h)にそれぞれ圧入させ、
前記上部取り付け孔(74h)を前記下部取り付け孔(75h)より大径に形成すると共に、前記ロッドカバー(59,60)の上端部(59a,60a)を、その上端部(59a,60a)以外の部分よりも大径に形成し、
各バンク(B1、B2)の冷却フィン(6)に、ロッドカバー(59,60)の各バンク(B1、B2)外壁への近接配置を可能にする切欠き(6a)を、該切欠き(6a)の内面がロッドカバー(59,60)の、前記大径部(59a,60a)よりも小径の中間部(59b,60b)外周に対向するように設けたことを特徴とする空冷式V型エンジン。
Each has a cylinder bore (3a) and supports the crankshaft (7) with the first and second banks (B1, B2) arranged in a V shape so as to define a trough (11) between them. In addition to the continuous connection to the crankcase (1), the cooling fins (6) protrude from the outer walls of the banks (B1, B2), and the suction and exhaust valves (35a, 36a) are placed on the heads of the banks (B1, B2). 35b, 36b) are arranged in a V shape, and a valve operating device (37) for opening and closing the intake and exhaust valves (35a, 36a; 35b, 36b) is disposed above the crankshaft (7). The camshaft (38) driven from the crankshaft (7), the suction of the camshaft (38), the first suction and exhaust cam followers (42a, 43a) which are lifted and lowered by the exhaust cams (38i, 38e), and A second suction and exhaust cam follower (42b, 43b); The first suction and exhaust cam followers (42a and 43a) and the second suction and exhaust cam followers (42b and 43b) are connected to the lower ends of the first suction and exhaust cam followers (42b and 43b). First suction, exhaust push rods (44a, 45a) and second suction, exhaust push rods (44b, 45b), these first suction, exhaust push rods (44a, 45a) and second First suction and exhaust rocker arms (71a, 72a) connected to the suction and exhaust valves (35a, 36a; 35b, 36b) of the corresponding banks (B1, B2) at the upper ends of the suction and exhaust push rods (44b, 45b) and the second intake, exhaust rocker arm (71b, 72b) in the configuration with air-cooled V-type engine out with a cylinder bore (3a) a cylinder block having a (3), Exhaust valves (35a, 36a; 35b, 36b) together constitute the integrally molded to each of the banks (B1, B2) and a cylinder head (4) which supports the, each intake of each bank (B1, B2), The exhaust rocker arms (71a, 72a; 71b, 72b) are arranged in a letter C shape in plan view so that their suction and exhaust push rod (44a, 45a; 44b, 45b) side ends are close to each other. Each suction and exhaust push rod (44a, 45a; 44b, 45b) is brought close to each other,
The lower ends of each pair of tubular rod covers (59, 60) arranged in parallel with each other to accommodate the respective suction and exhaust push rods (44a, 45a; 44b, 45b) are connected to the cylinders of the banks (B1, B2). A pair of lower mounting holes (75h) provided in the lower support part (75) formed integrally with the block (3) and projecting toward the trough part (11) are respectively press-fitted. Upper support portions (59, 60) of the rod cover (59, 60) are integrally formed with the cylinder heads (4) of the banks (B1, B2), and are extended to the trough portions (11). (74) are respectively press-fitted into the pair of upper mounting holes (74h),
The upper mounting hole (74h) has a larger diameter than the lower mounting hole (75h), and the upper end portions (59a, 60a) of the rod cover (59, 60) are other than the upper end portions (59a, 60a). Forming a larger diameter than the part of
The cooling fins (6) of each bank (B1, B2), notch that allows close proximity to each bank (B1, B2) an outer wall of the rod cover (59, 60) and (6a), notch An air-cooling type characterized in that the inner surface of (6a) is provided so as to face the outer periphery of the intermediate part (59b, 60b) having a smaller diameter than the large-diameter part (59a, 60a) of the rod cover (59, 60). V-type engine.
JP2007120057A 2007-04-27 2007-04-27 Air-cooled V-type engine Active JP4792423B2 (en)

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