JPH05118250A - Device for fixing cylinder head to cylinder block for engine - Google Patents
Device for fixing cylinder head to cylinder block for engineInfo
- Publication number
- JPH05118250A JPH05118250A JP30666291A JP30666291A JPH05118250A JP H05118250 A JPH05118250 A JP H05118250A JP 30666291 A JP30666291 A JP 30666291A JP 30666291 A JP30666291 A JP 30666291A JP H05118250 A JPH05118250 A JP H05118250A
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- head
- head mounting
- engine
- cylinder block
- 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
Landscapes
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、エンジンのシリンダ
ヘッドをシリンダブロックへ固定するためのシリンダヘ
ッド固定装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cylinder head fixing device for fixing a cylinder head of an engine to a cylinder block.
【０００２】[0002]
【従来の技術】この種のシリンダヘッド固定装置の基本
的な構造は、図４に示すように構成されている。即ち、
エンジンＥのシリンダブロック１の上寄り部で、シリン
ダ１０の外周の適当間隔置きに、複数個の各ヘッド取付
けボス１４をシリンダブロック１と一体に形成するとと
もに、各ヘッド取付けボス１４にヘッド取付ねじ孔１５
をあけ、シリンダヘッド２に複数本の各ボルト挿通孔２
５を、上記各ヘッド取付ねじ孔１５と同心状に貫通さ
せ、複数本の各ヘッドボルト１３を、上記各ボルト挿通
孔２５に挿通して、上記各ヘッド取付ねじ孔１５に締嵌
することにより、シリンダヘッド２をシリンダブロック
１に固定するように構成されている。そして従来では、
図５の実線で示すように、前記シリンダ１０の肉厚ｔ
は、シリンダ１０の全長に亙り全周がほぼ等しくなるよ
うに形成されていた。2. Description of the Related Art The basic structure of a cylinder head fixing device of this type is constructed as shown in FIG. That is,
In the upper portion of the cylinder block 1 of the engine E, a plurality of head mounting bosses 14 are integrally formed with the cylinder block 1 at appropriate intervals on the outer circumference of the cylinder 10, and a head mounting screw is attached to each head mounting boss 14. Hole 15
The cylinder head 2 and insert a plurality of bolt insertion holes 2
5 by penetrating the head mounting screw holes 15 concentrically, inserting the plurality of head bolts 13 into the bolt insertion holes 25, and tightening the head mounting screw holes 15 into the head mounting screw holes 15. The cylinder head 2 is fixed to the cylinder block 1. And traditionally,
As shown by the solid line in FIG. 5, the wall thickness t of the cylinder 10 is
Were formed so that the entire circumference was substantially equal to the entire length of the cylinder 10.
【０００３】[0003]
【発明が解決しようとする課題】上記従来技術では、高
回転・高負荷運転時に、ブローバイガス量が多くなった
後、ピストン３がシリンダ１０に焼きつくことがある。
その原因を追究したところ、次の理由によるものと理解
できる。そのピストン３の焼きつきは、シリンダ１０の
周方向に沿って断続的に生じており、この焼きつき箇所
は全てヘッド取付ねじ孔１５に近い位置にある。この現
象から判断すると、図５の仮想線で誇張して描いたよう
に、シリンダ１０が周方向に沿って蛇行状に変形したも
のであり、この蛇行状変形はシリンダ１０がヘットボル
ト１３の締付力によりシリンダヘッド２から不均一な拘
束力を受けたためである。In the above-mentioned conventional technique, the piston 3 may be burned on the cylinder 10 after the amount of blow-by gas becomes large at the time of high rotation and high load operation.
After investigating the cause, it can be understood that the reason is as follows. The seizure of the piston 3 occurs intermittently along the circumferential direction of the cylinder 10, and all the seizure points are near the head mounting screw hole 15. Judging from this phenomenon, the cylinder 10 is deformed in a meandering shape along the circumferential direction as exaggeratedly drawn by the imaginary line in FIG. 5, and this meandering deformation causes the cylinder 10 to tighten the head bolt 13 tightly. This is because the cylinder head 2 receives a non-uniform restraining force due to the force.
【０００４】即ち、エンジンの運転に伴うシリンダ径方
向の熱膨張量は、ピストン３が最大で、次にシリンダ１
０、そしてシリンダヘッド２が最小になる。この熱膨張
差から、シリンダ１０はヘットボルト１３の締付力によ
るシリンダヘッド２から軸心Ｚ方向の圧縮応力σを受け
ている。この圧縮応力σは、例えば図５中の等応力線ｇ
で示すように、各ヘッドボルト１３に近い部分では大き
く、遠い部分では小さくなる。That is, the amount of thermal expansion in the cylinder radial direction due to the operation of the engine is maximum in the piston 3 and then in the cylinder 1.
0, and the cylinder head 2 becomes the minimum. Due to this difference in thermal expansion, the cylinder 10 receives a compressive stress σ in the axial Z direction from the cylinder head 2 due to the tightening force of the head bolt 13. This compressive stress σ is, for example, the equal stress line g in FIG.
As indicated by, the head bolt 13 is large in the portion close to each head bolt 13 and is small in the far portion.
【０００５】ここで、シリンダ１０の上寄り部１０ａの
熱膨張を拘束する拘束力Ｆは、図６で示すように、上記
軸心Ｚ方向の圧縮応力σと当該上寄り部１０ａの断面積
Ａとの積により規定される。つまり、各ヘッドボルト１
３に近い部分では拘束力Ｆが大きく、遠い部分では小さ
くなる。このため、シリンダ１０の径方向の熱膨張量
は、各ヘッドボルト１３に近い拘束力Ｆの強い部分では
少なく、逆に各ヘッドボルト１３から遠くて拘束力の弱
い部分では外側へ向かって膨張する。従って図５で誇張
して示すように、シリンダ内周面１０Ａの周方向に凹凸
ができる。Here, the restraining force F for restraining the thermal expansion of the upper side portion 10a of the cylinder 10 is, as shown in FIG. 6, the compressive stress σ in the axial Z direction and the sectional area A of the upper side portion 10a. It is defined by the product of and That is, each head bolt 1
The binding force F is large in the portion close to 3, and is small in the portion far. Therefore, the amount of thermal expansion in the radial direction of the cylinder 10 is small in the portion near the head bolts 13 where the binding force F is strong, and conversely expands outward in the portion far from the head bolts 13 where the binding force is weak. .. Therefore, as exaggeratedly shown in FIG. 5, irregularities are formed in the circumferential direction of the cylinder inner peripheral surface 10A.
【０００６】このシリンダ内周面１０Ａの凹凸は、これ
にピストン３が局部接触することによりエンジンの焼き
付きを誘発する。また、この凹凸によりブローバイガス
量が増え、オイルを過剰に消費量する。本発明はこのよ
うな事情を考慮してなされたもので、 イ．上記シリンダ内周面の凹凸を無くして、ピストンの
局部接触によるエンジンの焼き付きを防止すること、 ロ．上記凹凸によるブローバイガス量を少なくし、オイ
ルの過剰な消費を無くすること、 を技術課題とする。The unevenness of the cylinder inner peripheral surface 10A induces seizure of the engine when the piston 3 locally contacts with the unevenness. Further, the amount of blow-by gas increases due to the unevenness, and the oil is consumed excessively. The present invention has been made in consideration of such circumstances. Eliminating the irregularities on the inner surface of the cylinder to prevent engine seizure due to local contact of the piston, b. The technical problem is to reduce the amount of blow-by gas due to the unevenness and to prevent excessive consumption of oil.
【０００７】[0007]
【課題を解決するための手段】本発明は上記課題を解決
するために、例えば図１〜図２に示すように、前記基本
構成において、前記シリンダ１０の少なくとも上寄り部
１０ａの周方向の肉厚ｔは、前記各ヘッド取付ねじ孔１
５に遠い部分よりも近い部分の方が薄くなるように形成
したことを特徴とするものである。In order to solve the above-mentioned problems, the present invention has, as shown in, for example, FIGS. 1 and 2, in the basic structure, at least the upper portion 10a of the cylinder 10 has a circumferential meat. The thickness t is the head mounting screw hole 1
It is characterized in that it is formed so that the portion closer to 5 is thinner than the portion further away.
【０００８】[0008]
【作 用】本発明は、以下のように作用する。シリンダ
１０の上寄り部１０ａは、前記のようにヘッドボルト１
３の固定に伴うシリンダ１０の軸心Ｚ方向の圧縮応力σ
により拘束される。即ち、このシリンダ１０の軸心Ｚ方
向の応力σは、前記同様例えば図２中の等応力線ｇで示
すように、各ヘッドボルト１３に近い部分では大きく、
遠い部分では小さくなる。ここで、シリンダ１０の上寄
り部１０ａの熱膨張を拘束する拘束力Ｆは、図３で示す
ように、上記軸心Ｚ方向の圧縮応力σと当該上寄り部１
０ａの横断面積Ａとの積により規定される。[Operation] The present invention operates as follows. The upper portion 10a of the cylinder 10 has the head bolt 1 as described above.
3, the compressive stress σ in the axial center Z direction of the cylinder 10
Bound by. That is, the stress σ in the Z-axis direction of the cylinder 10 is large in the portion near each head bolt 13 as shown by the equal stress line g in FIG.
It becomes smaller in the far part. Here, the restraining force F for restraining the thermal expansion of the upper side portion 10a of the cylinder 10 is, as shown in FIG. 3, the compressive stress σ in the axial Z direction and the upper side portion 1 as described above.
It is defined by the product of the cross-sectional area A of 0a.
【０００９】本発明では、シリンダ１０の上寄り部１０
ａの周方向の肉厚ｔは、各ヘッド取付ねじ孔１５に近い
部分ではが薄くしてあり、横断面積Ａはこの部分では小
さく、遠い部分では大きくなる。つまり、シリンダ１０
の全周に亙って拘束力（Ｆ＝σＡ）が一定になり、シリ
ンダ１０は、その全周に亙って一様に膨張する。これに
より、シリンダ内周面の周方向への凹凸を低減ないし除
去できる。従って、シリンダ内周面の凹凸に起因するエ
ンジンの焼き付きを防止し、ブローバイガス量の増加に
よるオイルの過剰消費を少なくすることができる。In the present invention, the upper portion 10 of the cylinder 10 is
The wall thickness t of a in the circumferential direction is thin in a portion close to each head mounting screw hole 15, and the cross-sectional area A is small in this portion and large in a distant portion. That is, the cylinder 10
The restraining force (F = σA) becomes constant over the entire circumference of the cylinder 10, and the cylinder 10 expands uniformly over the entire circumference. As a result, it is possible to reduce or eliminate the unevenness of the inner circumferential surface of the cylinder in the circumferential direction. Therefore, it is possible to prevent the seizure of the engine due to the unevenness of the inner peripheral surface of the cylinder and reduce the excessive consumption of oil due to the increase of the blow-by gas amount.
【００１０】[0010]
【実施例】以下本発明の実施例を図面に基づいてさらに
詳しく説明する。本発明の基本構造は、前述した図４の
エンジンと同様であり、図１は本発明の実施例に係るシ
リンダブロックの部分横断平面図である。即ち、図１の
上半分は図４のV−V線矢視断面図、下半分はシリンダブ
ロックの固定側端面図である。Embodiments of the present invention will now be described in more detail with reference to the drawings. The basic structure of the present invention is similar to that of the engine of FIG. 4 described above, and FIG. 1 is a partial cross-sectional plan view of a cylinder block according to an embodiment of the present invention. That is, the upper half of FIG. 1 is a cross-sectional view taken along the line V-V of FIG. 4, and the lower half is a fixed-side end view of the cylinder block.
【００１１】このシリンダヘッド固定装置は、図１及び
図４で示すように、エンジンＥのシリンダブロック１の
上寄り部で、シリンダ１０の外周の適当間隔置きに、複
数個の各ヘッド取付けボス１４をシリンダブロック１と
一体に形成するとともに、各ヘッド取付けボス１４にヘ
ッド取付ねじ孔１５をあけ、シリンダヘッド２に複数本
の各ボルト挿通孔２５を、上記各ヘッド取付ねじ孔１５
と同心状に貫通させ、複数本の各ヘッドボルト１３を、
上記各ボルト挿通孔２５に挿通して、上記各ヘッド取付
ねじ孔１５に締嵌することにより、シリンダヘッド２を
シリンダブロック１に固定するように構成するように構
成されている。なお、これらの図中、符号３はピスト
ン、４はウォータジャケット、４ａはジャケット連通
孔、５はカム軸、６はタペット、７はプッシュロッド、
８はヘッドジャケットである。As shown in FIGS. 1 and 4, the cylinder head fixing device is provided with a plurality of head mounting bosses 14 at an appropriate interval on the outer periphery of the cylinder 10 at the upper portion of the cylinder block 1 of the engine E. Is formed integrally with the cylinder block 1, a head mounting screw hole 15 is formed in each head mounting boss 14, a plurality of bolt insertion holes 25 are formed in the cylinder head 2, and each head mounting screw hole 15 is formed.
With a plurality of head bolts 13 concentrically,
The cylinder head 2 is fixed to the cylinder block 1 by being inserted into the bolt insertion holes 25 and tightly fitted in the head mounting screw holes 15. In these drawings, reference numeral 3 is a piston, 4 is a water jacket, 4a is a jacket communication hole, 5 is a cam shaft, 6 is a tappet, 7 is a push rod,
8 is a head jacket.
【００１２】図２は本実施例に係るシリンダ１０の図４
V−V線矢視横断平面図である。なお、視認容易のためシ
リンダ１０の断面のハッチングは省いてある。本発明で
は、図２に示すように、上記シリンダ１０の周方向の肉
厚ｔは、その全長に亙り各ヘッド取付ねじ孔１５に近い
部分では薄くしてあり、横断面積Ａはこの部分では小さ
く、遠い部分では大きくなる。つまり、シリンダ１０の
上寄り部１０ａの熱膨張を拘束する拘束力(Ｆ＝σＡ)
は、シリンダ１０の全周に亙って一定になり、シリンダ
１０は、その全周に亙って一様に膨張するように構成さ
れている。これにより、従来シリンダ内周面の周方向に
生じていた凹凸を低減ないし除去できる。従って、その
凹凸に起因するエンジンの焼き付きを防止し、ブローバ
イガス量の増加によるオイルの過剰消費を少なくするこ
とができる。FIG. 2 is a view of the cylinder 10 according to this embodiment shown in FIG.
It is a VV line arrow crossing top view. Note that hatching of the cross section of the cylinder 10 is omitted for easy visual recognition. In the present invention, as shown in FIG. 2, the circumferential wall thickness t of the cylinder 10 is thin over its entire length in the portions near the head mounting screw holes 15, and the cross-sectional area A is small in this portion. , Becomes larger in the far part. That is, the restraint force (F = σA) that restrains the thermal expansion of the upper portion 10a of the cylinder 10.
Is constant over the entire circumference of the cylinder 10, and the cylinder 10 is configured to expand uniformly over the entire circumference. As a result, it is possible to reduce or remove the unevenness that has conventionally been generated in the circumferential direction of the inner peripheral surface of the cylinder. Therefore, seizure of the engine due to the irregularities can be prevented, and excessive consumption of oil due to an increase in the blow-by gas amount can be reduced.
【００１３】なお、上記実施例ではシリンダ１０の周方
向の肉厚ｔが、その全長に亙り各ヘッド取付ねじ孔１５
に近い部分で薄くしてあるものについて例示したが、本
発明はこれに限らず、少なくとも、熱膨張の大きいシリ
ンダ１０の上寄り部１０ａについて、上記肉厚にすれば
足りる。In the above embodiment, the thickness t of the cylinder 10 in the circumferential direction is such that the head mounting screw holes 15 are provided over its entire length.
However, the present invention is not limited to this, and at least the upper portion 10a of the cylinder 10 having a large thermal expansion may have the above thickness.
【００１４】[0014]
【発明の効果】本発明では、シリンダの少なくとも上寄
り部の周方向の肉厚が、各ヘッド取付ねじ孔に近い部分
ではが薄くしてあり、シリンダの全周に亙ってヘッドボ
ルトによる拘束力が一定になるので以下の効果を奏す
る。 イ．シリンダはその全周に亙って一様に膨張するので、
シリンダ内周面の周方向への凹凸を低減ないし除去でき
る。これにより、シリンダ内周面の凹凸に起因するエン
ジンの焼き付きを防止することができる。 ロ．シリンダ内周面の凹凸に起因するブローバイガス量
の増加を解消して、オイルの過剰消費を少なくすること
ができる。According to the present invention, the wall thickness of at least the upper portion of the cylinder in the circumferential direction is thin at the portion near each head mounting screw hole, and the head bolt is restrained over the entire circumference of the cylinder. Since the force becomes constant, the following effects are achieved. I. Since the cylinder expands uniformly over its entire circumference,
It is possible to reduce or eliminate unevenness in the circumferential direction of the inner peripheral surface of the cylinder. As a result, it is possible to prevent the seizure of the engine due to the unevenness of the inner peripheral surface of the cylinder. B. It is possible to eliminate the increase in the amount of blow-by gas due to the unevenness of the inner peripheral surface of the cylinder and reduce the excessive consumption of oil.
【図１】本発明の実施例に係るシリンダブロックの部分
横断平面図である。FIG. 1 is a partial cross-sectional plan view of a cylinder block according to an embodiment of the present invention.
【図２】本発明の実施例に係るシリンダの図４V−V線矢
視横断平面図である。FIG. 2 is a cross-sectional plan view of the cylinder according to the embodiment of the present invention taken along the line VV in FIG.
【図３】本発明に係るシリンダの軸心方向応力、断面
積、拘束力の関係を示すグラフである。FIG. 3 is a graph showing the relationship between the axial stress, the cross-sectional area, and the restraining force of the cylinder according to the present invention.
【図４】本発明の前提構造を示すエンジンの縦断面図で
ある。FIG. 4 is a vertical sectional view of an engine showing a premise structure of the present invention.
【図５】従来例に係るシリンダの図４V−V線矢視横断平
面図である。FIG. 5 is a cross-sectional plan view of the cylinder according to the conventional example taken along the line V-V in FIG.
【図６】従来例に係るシリンダの軸心方向応力、断面
積、拘束力の関係を示すグラフである。FIG. 6 is a graph showing the relationship among axial stress, cross-sectional area, and restraining force of a cylinder according to a conventional example.
Ｅ …エンジン、 １ …シリンダブロッ
ク、２ …シリンダヘッド、 １０…シリンダ、
１０ａ…シリンダの上寄り部、 ｔ …シリンダの上寄
り部の肉厚、１３…ヘッドボルト、 １４…ヘ
ッド取付けボス、１５…ヘッド取付ねじ孔、 ２５
…ボルト挿通孔。E ... Engine, 1 ... Cylinder block, 2 ... Cylinder head, 10 ... Cylinder,
10a ... Upper part of cylinder, t ... Wall thickness of upper part of cylinder, 13 ... Head bolt, 14 ... Head mounting boss, 15 ... Head mounting screw hole, 25
… Bolt insertion holes.
Claims (1)
上寄り部で、シリンダ(１０)の外周の適当間隔置きに、
複数個の各ヘッド取付けボス(１４)をシリンダブロック
(１)と一体に形成するとともに、各ヘッド取付けボス
(１４)にヘッド取付ねじ孔(１５)をあけ、 シリンダヘッド(２)に複数本の各ボルト挿通孔(２５)
を、上記各ヘッド取付ねじ孔(１５)と同心状に貫通さ
せ、 複数本の各ヘッドボルト(１３)を、上記各ボルト挿通孔
(２５)に挿通して、上記各ヘッド取付ねじ孔(１５)に締
嵌することにより、シリンダヘッド(２)をシリンダブロ
ック(１)に固定するように構成したエンジンのシリンダ
ブロックへのシリンダヘッド固定装置において、 前記シリンダ(１０)の少なくとも上寄り部(１０ａ)の周
方向の肉厚(ｔ)は、前記各ヘッド取付ねじ孔(１５)に遠
い部分よりも近い部分の方が薄くなるように形成したこ
とを特徴とするエンジンのシリンダブロックへのシリン
ダヘッド固定装置。1. A cylinder block (1) of an engine (E), which is located at an upper portion of the cylinder block (1) at appropriate intervals on the outer periphery of the cylinder (10).
Cylinder block with multiple head mounting bosses (14)
(1) Formed integrally with each head mounting boss
Drill a head mounting screw hole (15) in (14) and insert a plurality of bolt insertion holes (25) in the cylinder head (2).
Through each of the head mounting screw holes (15) concentrically, and insert a plurality of head bolts (13) into the bolt insertion holes.
A cylinder head for a cylinder block of an engine configured to fix the cylinder head (2) to the cylinder block (1) by inserting the same into the head mounting screw holes (15) through the (25). In the fixing device, the thickness (t) in the circumferential direction of at least the upper portion (10a) of the cylinder (10) is smaller in the portion closer to the head mounting screw holes (15) than in the portion distant from the head mounting screw holes (15). A device for fixing a cylinder head to a cylinder block of an engine, which is characterized in that:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3306662A JP2662835B2 (en) | 1991-10-25 | 1991-10-25 | Cylinder head fixing device to engine cylinder block |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3306662A JP2662835B2 (en) | 1991-10-25 | 1991-10-25 | Cylinder head fixing device to engine cylinder block |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05118250A true JPH05118250A (en) | 1993-05-14 |
| JP2662835B2 JP2662835B2 (en) | 1997-10-15 |
Family
ID=17959815
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3306662A Expired - Fee Related JP2662835B2 (en) | 1991-10-25 | 1991-10-25 | Cylinder head fixing device to engine cylinder block |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2662835B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2131031A1 (en) * | 2007-04-05 | 2009-12-09 | Yamaha Hatsudoki Kabushiki Kaisha | Engine |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0261153U (en) * | 1988-10-26 | 1990-05-07 | ||
| JPH0419644U (en) * | 1990-06-05 | 1992-02-19 |
-
1991
- 1991-10-25 JP JP3306662A patent/JP2662835B2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0261153U (en) * | 1988-10-26 | 1990-05-07 | ||
| JPH0419644U (en) * | 1990-06-05 | 1992-02-19 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2131031A1 (en) * | 2007-04-05 | 2009-12-09 | Yamaha Hatsudoki Kabushiki Kaisha | Engine |
| EP2131031A4 (en) * | 2007-04-05 | 2013-01-02 | Yamaha Motor Co Ltd | Engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2662835B2 (en) | 1997-10-15 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |