JPH0257209B2 - - Google Patents
Info
- Publication number
- JPH0257209B2 JPH0257209B2 JP57133815A JP13381582A JPH0257209B2 JP H0257209 B2 JPH0257209 B2 JP H0257209B2 JP 57133815 A JP57133815 A JP 57133815A JP 13381582 A JP13381582 A JP 13381582A JP H0257209 B2 JPH0257209 B2 JP H0257209B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- intake
- shaft
- valve body
- air
- 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.)
- Expired - Lifetime
Links
- 230000008878 coupling Effects 0.000 claims description 10
- 238000010168 coupling process Methods 0.000 claims description 10
- 238000005859 coupling reaction Methods 0.000 claims description 10
- 238000002485 combustion reaction Methods 0.000 description 10
- 238000003754 machining Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 2
- 229920003002 synthetic resin Polymers 0.000 description 2
- 239000000057 synthetic resin Substances 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M13/00—Arrangements of two or more separate carburettors; Carburettors using more than one fuel
- F02M13/02—Separate carburettors
- F02M13/023—Special construction of the control rods
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
- F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
- F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
- F02D9/109—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps having two or more flaps
- F02D9/1095—Rotating on a common axis, e.g. having a common shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
- F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
- F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
- F02D9/107—Manufacturing or mounting details
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
- F05C2225/08—Thermoplastics
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
Description
【発明の詳細な説明】
この発明はそれぞれ吸気弁を介して燃焼室に連
らなる高負荷用通路と全域用通路とを備え、前記
高負荷用通路に低負荷運転中に閉じる空気弁を設
けた多気筒エンジンの吸気装置に関するもので、
特に前記空気弁を開閉作動させる作動装置の改良
に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention includes a high-load passage and a wide-area passage each connected to a combustion chamber via an intake valve, and the high-load passage is provided with an air valve that closes during low-load operation. This relates to the intake system of multi-cylinder engines.
In particular, the present invention relates to an improvement in an operating device for opening and closing the air valve.
従来、前述の如き高負荷用通路と全域用通路と
の二種の吸気通路を有するエンジンは公知に属す
る(例えば特開昭55−51920号公報)。空気弁は一
般に蝶形弁が用いられるので、エンジンが多気筒
であると、前記空気弁の弁軸は他気筒の吸気管を
貫通させる必要がある。そのため、弁軸が長大に
なり、弁軸の軸孔の形成に高精度の加工が要求さ
れる。この発明は斯かる軸孔の加工に高精度を必
要としないよう、前記弁軸を1個或いは2個の気
筒毎の短小なものとし、それらを構造簡単な軸継
手によつて接続した点に特徴がある。 Conventionally, an engine having two types of intake passages, a high-load passage and a wide-area passage as described above, is known (for example, Japanese Patent Laid-Open No. 51920/1983). Since the air valve is generally a butterfly valve, if the engine has multiple cylinders, the valve stem of the air valve must pass through the intake pipes of other cylinders. Therefore, the valve stem becomes long, and high-precision machining is required to form the shaft hole of the valve stem. The present invention has the advantage that, in order to avoid the need for high precision in machining such shaft holes, the valve shafts are made short and small for each cylinder or two, and they are connected by a shaft coupling with a simple structure. It has characteristics.
以下、本発明を図示の実施例によつて説明す
る。 Hereinafter, the present invention will be explained with reference to illustrated embodiments.
1は水冷式直列6気筒エンジンのエンジン本体
であり、シリンダ2、シリンダヘツド3及びピス
トン4によつて形成される燃焼室5を有し、この
燃焼室5には二個の吸気弁6,7を通じて高負荷
用通路8と全域用通路9及び排気弁10を通じて
排気通路11とが接続されている。12は点火
栓、13は従来公知のツインカム形動弁機構であ
る。15,16はシリンダヘツド3内の吸気通路
8,9をなす吸気ポートであり、そのシリンダヘ
ツド3側面の開口部には空気弁17と吸気分岐管
18が接続されている。空気弁17は弁胴17a
とその弁胴を貫く弁軸17bおよびこの弁軸17
bによつて支持された蝶形の弁体17cとで構成
されている。吸気分岐管18は分岐管18aと集
合部18bとを分配箱18cで連結してなり、集
合部18bには人為的に操作される絞り弁19が
設けられている。斯くて吸気ポート15,16と
弁胴17a及び吸気分岐管18は、燃焼室5を大
気中に通じる一連の吸気通路を構成する。20は
前記吸気ポート15,16間を連通する透孔、2
1は燃料噴射ノズルである。 Reference numeral 1 designates an engine body of a water-cooled in-line six-cylinder engine, which has a combustion chamber 5 formed by a cylinder 2, a cylinder head 3, and a piston 4. Two intake valves 6 and 7 are installed in this combustion chamber 5. The high load passage 8 is connected to the exhaust passage 11 through the wide range passage 9 and the exhaust valve 10. 12 is a spark plug, and 13 is a conventionally known twin cam type valve mechanism. Reference numerals 15 and 16 indicate intake ports forming intake passages 8 and 9 within the cylinder head 3, and an air valve 17 and an intake branch pipe 18 are connected to openings on the side surfaces of the cylinder head 3. The air valve 17 has a valve body 17a
and a valve shaft 17b that passes through the valve body, and this valve shaft 17.
It is composed of a butterfly-shaped valve body 17c supported by b. The intake branch pipe 18 is formed by connecting a branch pipe 18a and a collecting part 18b with a distribution box 18c, and the collecting part 18b is provided with a throttle valve 19 that is manually operated. In this way, the intake ports 15, 16, the valve body 17a, and the intake branch pipe 18 constitute a series of intake passages that communicate the combustion chamber 5 to the atmosphere. 20 is a through hole communicating between the intake ports 15 and 16;
1 is a fuel injection nozzle.
前記空気弁17は絞り弁19の下流に生じる吸
気負圧に応動するダイヤララム22によつて開閉
制御される。ダイヤララム22は、弾膜22aに
よつて大気に通じる大気室22bと、絞り弁19
の下流側の吸気通路内に通じる負圧室22cとに
区画されている。22dは弾膜22aに設けられ
たロツドで、ばね22eによつて空気弁17を閉
じ方向へ付勢されている。前記ロツド22dの他
端は前記弁軸17bの端部に固定されたアーム1
7dに連結されている。よつて、ダイヤララム2
2は絞り弁19の下流に生じる吸気負圧が高い
(圧力が低い)低負荷運転時は、空気弁17を閉
じる。前記弁胴17aは2個の気筒につき1個設
置され、第3図で示すように左気筒用L、中気筒
用M、右気筒Rからなつており、それらは互いに
ブラケツト23とボルト23aによつて連結され
ている。各弁軸17b間の接続は左気筒用Lと中
気筒用Mとの間ではアーム17dにより、また、
中気筒用Mと右気筒用Rとの間では軸継手24に
よつて接続されている。軸継手24は第5図で示
すように各弁軸17bの互いに対向する端部に形
成した切欠溝25とそれらの間に介在させた合成
樹脂製の連結部材26とからなつている。前記連
結部材26を外筒26aと外筒の内部に十字状に
交叉して配され一体的に塑造された2枚の板状の
係止片26bとで構成し、前記板状の係止片26
bを切欠溝25に係脱自在に係止させてある。す
なわち、これらの係止片26bと切欠溝25との
組合せによつてオルダム形の軸継手構造としてい
る。27は前記弁胴17aに圧入したピン28と
連結部材24の突部26cとの間に設けた戻しば
ね、29は防塵用シールである。 The air valve 17 is controlled to open and close by a dial ram 22 that responds to the intake negative pressure generated downstream of the throttle valve 19. The dial ram 22 includes an atmospheric chamber 22b that communicates with the atmosphere through a bullet film 22a, and a throttle valve 19.
It is divided into a negative pressure chamber 22c communicating with the intake passage on the downstream side. Reference numeral 22d denotes a rod provided on the elastic membrane 22a, and is biased toward closing the air valve 17 by a spring 22e. The other end of the rod 22d is connected to the arm 1 fixed to the end of the valve shaft 17b.
7d. So, dialer lum 2
2 closes the air valve 17 during low load operation when the intake negative pressure generated downstream of the throttle valve 19 is high (pressure is low). One valve body 17a is installed for each two cylinders, and as shown in FIG. 3, it consists of L for the left cylinder, M for the middle cylinder, and R for the right cylinder, which are connected to each other by brackets 23 and bolts 23a. are connected together. Connection between each valve shaft 17b is made by an arm 17d between L for the left cylinder and M for the middle cylinder, and
A shaft coupling 24 connects M for the middle cylinder and R for the right cylinder. As shown in FIG. 5, the shaft joint 24 consists of notched grooves 25 formed at mutually opposing ends of each valve shaft 17b and a synthetic resin connecting member 26 interposed between them. The connecting member 26 is composed of an outer cylinder 26a and two integrally molded plate-shaped locking pieces 26b disposed criss-cross inside the outer cylinder, and the plate-shaped locking pieces 26b are integrally molded. 26
b is removably engaged with the notched groove 25. That is, the combination of these locking pieces 26b and the notched grooves 25 provides an Oldham type shaft joint structure. 27 is a return spring provided between the pin 28 press-fitted into the valve body 17a and the protrusion 26c of the connecting member 24, and 29 is a dustproof seal.
次にこのエンジンの動作を説明する。エンジン
が始動し、絞り弁19が低開度で運転されると、
その下流の吸気通路8,9に生じる吸気負圧が高
い(圧力が低い)ので、前記空気弁17が高負荷
用通路8を閉じ、吸気の全量が全域用通路9のみ
を経て燃焼室5へ導かれ、吸気流速が速くエンジ
ンによい加速応答性が得られる。エンジンの負荷
が増し絞り弁19の開度が予定以上の高開度に達
するとその下流の吸気通路8,9に生じる吸気負
圧が低く(圧力が高く)なり、前記空気弁17が
高負荷用通路8を開き、本発は両吸気前記を経て
燃焼室5へ導かれる。すなわち、吸気通路面積が
十分大きくとれるので通気抵抗が減じ、エンジン
に大出力が得られる。ここで、空気弁17の弁軸
17bは3本に分割されているので、各弁胴17
aの軸孔の長さが徒らに長くなることがなく、そ
の加工が容易に行い得る。また、各弁軸17bの
間はそれらの端部に形成した切欠溝25と合成樹
脂製の連結部材26とからなるオルダム形の軸継
手が形成されているので、たとえ各弁胴17aの
軸孔の加工精度が適当でなくとも、またエンジン
の熱によつてそれらの同芯度が狂うことがあつて
も、更には組付け精度が適当でなくとも円滑に作
動する。気筒間の燃焼ばらつきに大きく影響する
のは、空気弁が非作動のときに吸気通路と弁体1
7cとの隙間から洩れる空気量にばらつきであ
る。したがつて、空気弁の非作動時に、全ての気
筒の弁体17cが所定の隙間をもつて確実に閉じ
るようにする必要がある。そこで、第5図を例に
とつていうなら、戻しばね27により左側の弁軸
17bと軸継手26との間のがたさえ無くしてお
けば、右側の弁軸17bと軸継手26の嵌合関係
の設定により、左側の弁体群が閉じた状態で右側
の弁体群も吸気通路を閉じることになる。すなわ
ち、戻しばね27は、右側の弁軸17bと軸継手
26間のがたを弁体が閉じる方向にのみ付勢する
ものであるから、最も気筒間の燃焼ばらつきに影
響する空気弁が非作動時の空気量のばらつきを少
なくすることができる。 Next, the operation of this engine will be explained. When the engine starts and the throttle valve 19 is operated at a low opening,
Since the intake negative pressure generated in the downstream intake passages 8 and 9 is high (pressure is low), the air valve 17 closes the high-load passage 8, and the entire amount of intake air passes only through the wide area passage 9 to the combustion chamber 5. This results in a high intake flow rate and good acceleration response for the engine. When the load on the engine increases and the opening degree of the throttle valve 19 reaches a higher opening degree than expected, the intake negative pressure generated in the intake passages 8 and 9 downstream thereof becomes low (high pressure), and the air valve 17 is under high load. The combustion passage 8 is opened, and the main combustion air is guided into the combustion chamber 5 through both intakes. That is, since the area of the intake passage can be made sufficiently large, ventilation resistance is reduced, and a large output can be obtained from the engine. Here, since the valve shaft 17b of the air valve 17 is divided into three parts, each valve body 17
The length of the shaft hole a is not unnecessarily long, and the machining can be easily performed. Moreover, since an Oldham-type shaft joint is formed between each valve shaft 17b, which is composed of a notched groove 25 formed at the end thereof and a connecting member 26 made of synthetic resin, even if the shaft hole of each valve body 17a is Even if the machining accuracy of the parts is not appropriate, even if their concentricity is disturbed by the heat of the engine, and even if the assembly accuracy is not appropriate, they will operate smoothly. The main cause of combustion variation between cylinders is the air intake passage and valve body 1 when the air valve is inactive.
There are variations in the amount of air leaking from the gap with 7c. Therefore, it is necessary to ensure that the valve bodies 17c of all cylinders are closed with a predetermined gap when the air valves are not in operation. Therefore, using FIG. 5 as an example, if the return spring 27 eliminates the looseness between the left valve stem 17b and the shaft coupling 26, the right valve stem 17b and the shaft coupling 26 will fit together. Due to the relationship settings, when the left valve body group is closed, the right valve body group also closes the intake passage. In other words, the return spring 27 biases the play between the right valve shaft 17b and the shaft coupling 26 only in the direction in which the valve body closes, so that the air valve that most affects the combustion variation between cylinders is inoperative. It is possible to reduce variations in the amount of air at different times.
この発明は以上説明したように、エンジン本体
の側部に、弁胴とこの弁胴を貫く弁軸によつて支
持された螺形の弁体とかちなる空気弁を複数個取
付け、前記弁軸を同心上に整列させて弁軸間を軸
継手によつて連結するものにおいて、前記弁軸間
を、弁軸の端部とともにオルダム形の軸継手構造
を構成する連結部材を介して連結したから、構造
が簡単で部品点数が少なく加工ないし組付け精度
をそれほど厳格に管理する必要がないので廉価に
製造できる。また、各空気弁を各気筒の吸気通路
を貫通する大型のものに較べ弁胴および弁軸の加
工が容易に行える。さらに、前記連結部材と弁胴
との間に、連結部材を回転方向に付勢する戻しば
ねを介装したから、このばねの付勢力によつて連
結部材と弁軸との間の間隙が吸収されるため、所
謂ガタツキがなくなり複数ある弁体の開閉を同期
させることができ、気筒間のばらつきが少なくな
るという利点もある。 As explained above, this invention includes a plurality of air valves each consisting of a valve body and a spiral valve body supported by a valve stem passing through the valve body, which are attached to the side of an engine body, and the valve stem is connected to the valve body. In the valve shafts arranged concentrically and connected by a shaft joint, since the valve shafts are connected via a connecting member that constitutes an Oldham-type shaft joint structure together with the end of the valve shaft, The structure is simple, the number of parts is small, and there is no need to strictly control processing or assembly accuracy, so it can be manufactured at low cost. Further, the valve body and valve stem can be easily machined compared to a large-sized one in which each air valve passes through the intake passage of each cylinder. Furthermore, since a return spring that biases the coupling member in the rotational direction is interposed between the coupling member and the valve body, the gap between the coupling member and the valve shaft is absorbed by the biasing force of this spring. Therefore, there is an advantage that so-called rattling is eliminated, the opening and closing of a plurality of valve bodies can be synchronized, and variations among cylinders are reduced.
図面はこの発明の一実施例を示すものであり、
第1図は要部を破断したエンジンの側面図、第2
図は一部を破断して示す平面図、第3図は−
断面図、第4図は−断面を拡大して示す拡大
断面図、第5図は要部を分解して示す斜視図、第
6図は連結部材26の正面図、第7図はその−
断面図、第8図は背面図である。
17……空気弁、18……吸気分岐管、19…
…絞り弁、22……ダイヤフラム、24……軸継
手、25……切欠溝、26……連結部材。
The drawings show one embodiment of the invention,
Figure 1 is a side view of the engine with main parts broken away, Figure 2
The figure is a partially cutaway plan view, and Figure 3 is -
4 is an enlarged sectional view showing the cross section, FIG. 5 is an exploded perspective view of the main parts, FIG. 6 is a front view of the connecting member 26, and FIG. 7 is its -
The sectional view and FIG. 8 are rear views. 17...Air valve, 18...Intake branch pipe, 19...
... Throttle valve, 22 ... Diaphragm, 24 ... Shaft joint, 25 ... Notch groove, 26 ... Connection member.
Claims (1)
胴を貫く弁軸17bによつて支持された蝶形の弁
体17cとからなる空気弁17を複数個取付け、
前記弁軸17bを同心上に整列させて弁軸間を軸
継手によつて連結するものにおいて、前記弁軸1
7b,17b間を弁軸の端部とともにオルダム形
の軸継手構造を構成する連結部材26を介して連
結し、この連結部材と弁胴17aとの間に、連結
部材を回転方向に付勢する戻しばね27を介装し
てなる多気筒エンジンの空気弁作動装置。1. A plurality of air valves 17 each consisting of a valve body 17a and a butterfly-shaped valve body 17c supported by a valve shaft 17b passing through the valve body are attached to the side of the engine body,
The valve shafts 17b are arranged concentrically and the valve shafts are connected by a shaft coupling, in which the valve shafts 17b are connected concentrically.
7b and 17b are connected together with the end of the valve shaft via a connecting member 26 that constitutes an Oldham type shaft coupling structure, and the connecting member is biased in the rotational direction between this connecting member and the valve body 17a. A pneumatic valve operating device for a multi-cylinder engine that includes a return spring 27.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP13381582A JPS5925048A (en) | 1982-08-02 | 1982-08-02 | Air-valve operating apparatus for multicyclinder engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP13381582A JPS5925048A (en) | 1982-08-02 | 1982-08-02 | Air-valve operating apparatus for multicyclinder engine |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS5925048A JPS5925048A (en) | 1984-02-08 |
JPH0257209B2 true JPH0257209B2 (en) | 1990-12-04 |
Family
ID=15113681
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP13381582A Granted JPS5925048A (en) | 1982-08-02 | 1982-08-02 | Air-valve operating apparatus for multicyclinder engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5925048A (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6626421B2 (en) * | 2000-02-16 | 2003-09-30 | Denso Corporation | Manufacturing method for a throttle body of an internal combustion engine and a related throttle apparatus |
DE10236587A1 (en) * | 2002-08-09 | 2004-02-26 | Pierburg Gmbh | door assembly |
DE10335561A1 (en) * | 2003-08-02 | 2005-03-10 | Mann & Hummel Gmbh | Intake module |
DE102004063017A1 (en) * | 2004-12-22 | 2006-07-13 | Mann + Hummel Gmbh | Intake manifold for a multi-cylinder internal combustion engine |
DE102011102018A1 (en) * | 2011-05-19 | 2012-11-22 | Friedrich Boysen Gmbh & Co. Kg | Valve device used in gas exhaust system for motor vehicle, has valve connected with actuator by connectors and resilient coupling that is formed of sleeve-shape and provided with bellows |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS587107Y2 (en) * | 1977-04-04 | 1983-02-07 | 三菱電機株式会社 | engine ignition system |
-
1982
- 1982-08-02 JP JP13381582A patent/JPS5925048A/en active Granted
Also Published As
Publication number | Publication date |
---|---|
JPS5925048A (en) | 1984-02-08 |
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