JPH03271526A - Starter of diesel engine - Google Patents
Starter of diesel engineInfo
- Publication number
- JPH03271526A JPH03271526A JP7098990A JP7098990A JPH03271526A JP H03271526 A JPH03271526 A JP H03271526A JP 7098990 A JP7098990 A JP 7098990A JP 7098990 A JP7098990 A JP 7098990A JP H03271526 A JPH03271526 A JP H03271526A
- Authority
- JP
- Japan
- Prior art keywords
- cooling water
- engine
- advance
- thermowax
- fuel injection
- 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
- 239000007858 starting material Substances 0.000 title 1
- 239000000498 cooling water Substances 0.000 claims abstract description 44
- 230000007246 mechanism Effects 0.000 claims abstract description 30
- 239000000446 fuel Substances 0.000 claims abstract description 16
- 238000002347 injection Methods 0.000 claims abstract description 16
- 239000007924 injection Substances 0.000 claims abstract description 16
- 238000006073 displacement reaction Methods 0.000 claims description 3
- 239000002826 coolant Substances 0.000 claims 2
- 230000008602 contraction Effects 0.000 abstract 1
- 230000007423 decrease Effects 0.000 description 12
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000006866 deterioration Effects 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 230000001151 other effect Effects 0.000 description 1
- 239000010981 turquoise Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
- F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
- F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
- F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
- F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
- F02M41/125—Variably-timed valves controlling fuel passages
- F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
- F02D1/025—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by means dependent on engine working temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/16—Adjustment of injection timing
- F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
- F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/04—Introducing corrections for particular operating conditions
- F02D41/06—Introducing corrections for particular operating conditions for engine starting or warming up
- F02D41/062—Introducing corrections for particular operating conditions for engine starting or warming up for starting
- F02D41/064—Introducing corrections for particular operating conditions for engine starting or warming up for starting at cold start
-
- 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
- F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
- F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
- F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
- F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
- F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
- F02M41/128—Varying injection timing by angular adjustment of the face-cam or the rollers support
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/38—Pumps characterised by adaptations to special uses or conditions
- F02M59/42—Pumps characterised by adaptations to special uses or conditions for starting of engines
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/462—Delivery valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本願発明は、ディーゼルエンジンの始動装置に関するも
のである。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a starting device for a diesel engine.
（従来の技術）
一般にディーゼルエンジンにおいては、エンジン冷態時
における始動性及び始動直後における半失火の抑制とい
う二つの観点から、エンジン始動時における燃料噴射時
期をエンジン冷却水温に応じて進角させる始動時進角機
構と、エンジン完爆後から所定期間グロープラグへの通
電を継続して燃焼をアシストするアフターグロー機構と
を備えている（例えば、実開昭６０−３８１４６号公報
参照）。(Prior Art) In general, diesel engines are started by advancing the fuel injection timing according to the engine cooling water temperature from the two viewpoints of starting performance when the engine is cold and suppressing half-misfires immediately after starting. It includes a time advance mechanism and an afterglow mechanism that assists combustion by continuing to energize the glow plug for a predetermined period after the engine has completely exploded (see, for example, Japanese Utility Model Application No. 60-38146).
これら各機構における具体的な制御は次の通りである。Specific controls for each of these mechanisms are as follows.
先ず、始動時進角機構における制御であるが、この始動
時進角機構においては、第４図に示すように、始動時の
エンジン冷却水温が低いほど進角量を大きくし、始動後
はエンジン冷却水温が所定温度（例えば、５０℃）に達
するまで徐々に進角量を減じるように制御する。First, regarding the control of the starting advance angle mechanism, as shown in Fig. 4, the advance angle amount is increased as the engine cooling water temperature at the time of starting is lower. The advance amount is controlled to be gradually reduced until the cooling water temperature reaches a predetermined temperature (for example, 50° C.).
一方、アフターグロー機構における制御は、第５図に実
線図示するように、エンジン冷却水温が所定温度以下の
場合（例えば、３０℃以下）には、エンジン完爆後、所
定値のアフターグロー電圧（例えば、５Ｖ）を継続的に
かけて吸気を予熱して燃焼をアシストするようにしてい
る。尚、エンジン始動時においては、グロープラグには
全バッテリー電圧（例えば、１２Ｖ）がかけられる。On the other hand, as shown in the solid line diagram in FIG. 5, the afterglow mechanism control is such that when the engine cooling water temperature is below a predetermined temperature (for example, below 30°C), after the engine has completely exploded, the afterglow voltage ( For example, 5V) is continuously applied to preheat the intake air to assist combustion. Note that when the engine is started, the full battery voltage (for example, 12V) is applied to the glow plug.
このような燃料噴射時期の進角制御とアフターグロー制
御とによってエンジン冷態時における始動性の向上及び
始動直後における半失火の発生防止とが図られるもので
ある。Such advance control and afterglow control of the fuel injection timing improves startability when the engine is cold and prevents half-misfires from occurring immediately after starting.
（発明が解決しようとする課題）
ところで、一般にアフターグロー電圧はバ・ソテリー電
圧によって補正するようにしているため、このバッテリ
ー電圧が何等かの原因で正規の電圧より低下した場合に
は、これに伴ってアフターグロー電圧も低下することに
なる（第５図の破線図示状態）。(Problem to be Solved by the Invention) By the way, the afterglow voltage is generally corrected by the battery voltage, so if the battery voltage drops below the normal voltage for some reason, the afterglow voltage will be corrected. Accordingly, the afterglow voltage also decreases (as shown by the broken line in FIG. 5).
このようにバッテリー電圧の低下に起因してアフターグ
ロー電圧が低下すると、当然にグロープラグ温度も低下
し、この結果、始動後退角機構による進角操作のみては
燃焼をアシストし切れず、結果的に始動性の悪化あるい
は半失火の発生という事態が生じることとなる。When the afterglow voltage decreases due to a decrease in battery voltage, the glow plug temperature naturally decreases, and as a result, combustion cannot be fully assisted by advancing the engine by the start-back angle mechanism alone. This may result in poor startability or partial misfire.
そこで本願発明では、バッテリー電圧が低下している状
態においても良好な始動性を確保し且つ半失火の発生を
確実に防止し得るようにしたディーゼルエンジンの始動
装置を提供することを目的としてなされたものである。Therefore, the present invention aims to provide a diesel engine starting device that can ensure good starting performance even when the battery voltage is low and can reliably prevent the occurrence of half-misfire. It is something.
（課題を解決するための手段）
本願発明ではかかる課題を解決するための具体的手段と
して、
（ｉ）請求項１記載の発明では、エンジン始動時にエン
ジン冷却水温に応じて燃料噴射時期を進角させる始動時
進角機構と、エンジン完爆後からエンジン冷却水温が所
定温度に達するまでの期間グロープラグへの通電を継続
するアフターグロー機構とを備えたディーゼルエンジン
の始動装置において、上記始動時進角機構による進角量
を上記グロープラグに供給されるアフターグロー電圧の
値に応じて制御するようにしたことを特徴とし、（１１
）請求項２記載の発明では、エンジン始動時にエンジン
冷却水温に応じて燃料噴射時期を進角させる始動時進角
機構と、エンジン完爆後からエンジン冷却水温が所定温
度に達するまでの期間グロープラグへの通電を継続する
アフターグロー機構とを備えたディーゼルエンジンの始
動装置において、上記始動時進角機構を、エンジン冷却
水温に対応して膨縮変位するサーモワックスで構成し且
つ該サーモワックスの膨張変位に伴って遅角操作がなさ
れる如くするとともに、上記サーモワックスに供給され
るエンジン冷却水の流量を」−記グローブラグに供給さ
れるアフターグロー電圧の値に応じて制御する冷却水流
量制御機構を備え１、上記始動時進角機構による進角量
を、上記冷却水流量制御機構により上記サーモワックス
に供給されるエンジン冷却水量を調整することによって
制御するようにしたことを特徴としている。(Means for Solving the Problems) In the present invention, as specific means for solving the problems, (i) In the invention according to claim 1, the fuel injection timing is advanced according to the engine cooling water temperature when starting the engine. In a diesel engine starting device, the diesel engine starting device is equipped with a start-up advance mechanism that causes the engine to advance at start-up, and an after-glow mechanism that continues to energize the glow plug for a period from when the engine has completely exploded until the engine cooling water temperature reaches a predetermined temperature. It is characterized in that the amount of advance by the angle mechanism is controlled according to the value of the afterglow voltage supplied to the glow plug, (11)
) The invention according to claim 2 includes a start-up advance mechanism that advances the fuel injection timing according to the engine cooling water temperature when starting the engine, and a glow plug for a period from when the engine is completely detonated until the engine cooling water temperature reaches a predetermined temperature. In a diesel engine starting device equipped with an afterglow mechanism that continues to energize a diesel engine, the starting advance mechanism is made of thermowax that expands and contracts in response to engine cooling water temperature, and the thermowax expands and contracts in response to engine cooling water temperature. Cooling water flow rate control that retards the angle according to the displacement, and controls the flow rate of engine cooling water supplied to the thermowax according to the value of the afterglow voltage supplied to the globe lug. 1, the amount of advance by the start-up advance mechanism is controlled by adjusting the amount of engine cooling water supplied to the thermowax by the cooling water flow rate control mechanism.
（作用）
本願各発明ではこのような構成であるから、■請求項Ｉ
記載の発明においては、アフター・グロー電圧の低下に
よってグロープラグによる予熱作用が低下した場合には
、このアフターグロー電圧の低下状態に対応して燃料噴
射時期の進角量が補正制御され、上記予熱作用の低下に
起因する燃焼性の悪化が補償される、
■請求項２記戦の発明においては、アフターグロ一電圧
の低下によってグロープラグによる予熱作用が低下した
場合には、サーモワックスに供給されるエンジン冷却水
量を減少方向に制御することによって該サーモワックス
の膨張変位が緩慢となりエンジン冷却水温に対する進角
量が実質的に増加せしめられ（第２図参照）、グロープ
ラグによる予熱作用の低下に起因する燃焼性の悪化が補
償される、
等の作用が得られるものである。(Operation) Since each invention of the present application has such a structure, ■Claim I
In the described invention, when the preheating effect of the glow plug is reduced due to a decrease in the afterglow voltage, the advance amount of the fuel injection timing is corrected and controlled in response to the decrease in the afterglow voltage, and the preheating In the invention of claim 2, when the preheating effect of the glow plug is reduced due to a decrease in the afterglow voltage, the deterioration in combustibility caused by the decrease in the glow plug is compensated for. By controlling the amount of engine cooling water in a decreasing direction, the expansion displacement of the thermowax is slowed down, and the amount of advance relative to the engine cooling water temperature is substantially increased (see Figure 2), which reduces the preheating effect of the glow plug. The resulting deterioration in flammability is compensated for, and other effects can be obtained.
（発明の効果）
従って、本願各発明によれば、アフターグロー電圧の低
下に起因する燃焼性の悪化が燃料噴射時期の進角量を増
加させるということによって補償されるため、例えバッ
テリー電圧が低下している場合であっても良好な始動性
が確保されるとともに、半失火の発生が防止され、その
結果、エンジンの信頼性が向上するという効果が得られ
るものである。(Effects of the Invention) Therefore, according to the inventions of the present application, deterioration in combustibility caused by a decrease in afterglow voltage is compensated for by increasing the advance amount of the fuel injection timing. Even when the engine is running, good startability is ensured, the occurrence of half-misfires is prevented, and as a result, the reliability of the engine is improved.
また、特に請求項２記載の発明においては、上記の効果
に加えて、バッテリー電圧（即ち、アフターグロー電圧
）の低下状態に応じて直接的に進角操作を行うのではな
く、サーモワックスに供給されるエンジン冷却水の流量
調整によって間接的に行うものであるため、その構成が
簡単で且つ制御も行い易いという効果も得られる。Moreover, in addition to the above-mentioned effect, in particular, in the invention as claimed in claim 2, instead of directly performing an advance operation according to the state of decrease in battery voltage (i.e., afterglow voltage), the supply to the thermowax is Since this is done indirectly by adjusting the flow rate of the engine cooling water, the structure is simple and the control is easy to perform.
（実施例）
以下、添付図面を参照して本願発明の好適な実施例を説
明する。(Embodiments) Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.
第１図には、本願の請求項２記載の発明の実施例にかか
るディーゼルエンジンの始動装置が示されており、同図
において符号１は燃料噴射ポンプであり、また符号２は
該燃料噴射ポンプｌの燃料噴射時期を調整するタイマー
（図示省略）に連結されたタイマー軸であって、このタ
イマー軸２には操作レバー３がスプリング９によって常
時進角側に回動付勢された状態で取り付けられている。FIG. 1 shows a diesel engine starting device according to an embodiment of the invention set forth in claim 2 of the present application, and in the figure, reference numeral 1 represents a fuel injection pump, and reference numeral 2 represents the fuel injection pump. This is a timer shaft connected to a timer (not shown) that adjusts the fuel injection timing of 1, and an operating lever 3 is attached to this timer shaft 2 with a spring 9 constantly urging it to rotate toward the advance side. It is being
そして、この操作レバー３の回動操作によって燃料噴射
時期を進角あるいは遅角操作することができるようにな
っている。By rotating the control lever 3, the fuel injection timing can be advanced or retarded.
一方、この操作レバー３の側方には、冷却水室５内を流
通するエンジン冷却水の温度に応じて膨縮変位するサー
モワックス４か配置されており、該操作レバー３は上記
スプリング９によって常時該サーモワックス４の作動子
４ａに当接仕しめられている。On the other hand, on the side of this operating lever 3, a thermowax 4 that expands and contracts depending on the temperature of the engine cooling water flowing in the cooling water chamber 5 is arranged, and the operating lever 3 is moved by the spring 9. It is always in contact with the actuator 4a of the thermowax 4.
さらに、上記冷却水室５には冷却水通路６を介してエン
ジン（図示省略）側からエンジン冷却水が常時供給され
るが、その供給量は該冷却水通路６に設けた電磁バルブ
７（特許請求の範囲中の冷却水流量制御機構に該当する
）によってその通路面積を増減させることによって制御
される。また、上記電磁バルブ７の作動制御は、アフタ
ーグロー電圧に対応してコントロールユニット８から出
力される制御信号によって行なわれる。具体的には、第
３図に示すように、アフターグロー電圧が低下するほど
冷却水通路６の通路面積を絞るように制御される。Furthermore, engine cooling water is constantly supplied to the cooling water chamber 5 from the engine (not shown) side via a cooling water passage 6, but the amount of the supplied amount is determined by a solenoid valve 7 (patent (corresponding to the cooling water flow rate control mechanism in the claims) by increasing or decreasing the passage area. Further, the operation of the electromagnetic valve 7 is controlled by a control signal output from the control unit 8 in response to the afterglow voltage. Specifically, as shown in FIG. 3, the passage area of the cooling water passage 6 is controlled to be narrowed as the afterglow voltage decreases.
このような構成とすることによって、第２図に示すよう
な進角特性が実現されるものである。即ち、正規のバッ
テリー電圧の下ではアフターグロー電圧として５Ｖの電
圧が供給され、グロープラグは適正温度に維持される。With such a configuration, advance angle characteristics as shown in FIG. 2 are realized. That is, under a normal battery voltage, a voltage of 5V is supplied as an afterglow voltage, and the glow plug is maintained at an appropriate temperature.
そして、この場合、始動後退角機構における進角特性は
第２図に実線で示すような特性となり（第４図に示す特
性と同じ）、また上記電磁バルブ７は全開状態となって
いる。In this case, the advance angle characteristic of the starting receding angle mechanism is as shown by the solid line in FIG. 2 (same as the characteristic shown in FIG. 4), and the electromagnetic valve 7 is fully open.
一方、何等かの原因でバッテリー電圧が正規電圧よりも
低下し、これに伴ってアフターグロー電圧が例えば４．
５■に低下した状態においてエンジンを始動させる場合
には、グロープラグによる予熱性が低下するので、これ
を補填してその始動性を確保し且つ半失火の発生を防止
すべく進角補正が行なわれる。即ち、先ずこのアフター
グロー電圧の低下量に対応して電磁バルブ７が閉弁方向
に操作され、冷却水通路６の通路面積が現在のアフター
グロー電圧に対応した通路面積（第３図参照）に設定さ
れる。すると、通路面積が絞られた分だけサーモワック
ス４側に供給されるエンジン冷却水量が減少し、例えエ
ンジン冷却水温は同じであっても該サーモワックス４に
伝達される熱量が減少するため該サーモワックス４の作
動子４ａの突出動（即ち、遅角操作）が通路全開時より
も緩慢となる。この結果、第２図に破線で示すように、
正規状態（実線図示）よりも高温側にズして同一水温に
対する進角量が正規状態時よりも増加する進角特性が得
られ、これによってアフターグロー電圧の低下による予
熱性の悪化が燃料噴射時期の進角量の増加補正により補
償され、例えバッテリー電圧が低下した状態であっても
エンジンの始動が確実となりまた半失火の発生が未然に
防止されるものである。On the other hand, for some reason, the battery voltage drops below the normal voltage, and as a result, the afterglow voltage drops to, for example, 4.
When starting the engine in a state where the engine temperature has dropped to 5■, the preheating performance by the glow plug will be reduced, so advance angle correction is performed to compensate for this, ensure startability, and prevent half-misfires. It will be done. That is, first, the solenoid valve 7 is operated in the closing direction in response to the amount of decrease in the afterglow voltage, and the passage area of the cooling water passage 6 becomes the passage area corresponding to the current afterglow voltage (see Fig. 3). Set. Then, the amount of engine cooling water supplied to the thermowax 4 side is reduced by the narrowed passage area, and even if the engine cooling water temperature is the same, the amount of heat transferred to the thermowax 4 is reduced. The protruding movement of the actuator 4a of the wax 4 (ie, the retarded operation) becomes slower than when the passage is fully opened. As a result, as shown by the broken line in Figure 2,
An advance angle characteristic is obtained in which the amount of advance for the same water temperature increases as compared to the normal state (shown by the solid line) as compared to the normal state (shown by the solid line). This is compensated for by increasing the timing advance amount, and even if the battery voltage is low, the engine can be started reliably and half-misfires can be prevented from occurring.
第１図は本願発明の実施例にかかるディーゼルエンジン
の始動装置の要部縦断面図、第２図は該始動装置による
進角特性の変化状態説明図、第３図は電磁バルブの制御
特性図、第４図は始動後進角機構の作動特性図、第５図
はアフターグロー機構の作動特性図である。
ｌ・・・燃料噴射ポンプ
２・・・タイマー軸
操作レバー
サーモワックス
冷却水室
冷却水通路
電磁バルブ
コントロールユニット
スプリング
エンノ゛ン冷却水温（’Ｃ）
第２図
１７ターク′η−電圧（Ｙ）
第３図
第４図
工ンン゛ン冷却水−１
（’Ｃ）
第５図FIG. 1 is a vertical cross-sectional view of a main part of a diesel engine starting device according to an embodiment of the present invention, FIG. 2 is an explanatory diagram of changes in advance characteristics by the starting device, and FIG. 3 is a diagram of control characteristics of an electromagnetic valve. , FIG. 4 is an operating characteristic diagram of the starting backward advance angle mechanism, and FIG. 5 is an operating characteristic diagram of the afterglow mechanism. l...Fuel injection pump 2...Timer shaft operation lever Thermowax cooling water chamber Cooling water passage Solenoid valve control unit Spring engine Cooling water temperature ('C) Fig. 2 17 Turquoise 'η - Voltage (Y) Figure 3 Figure 4 Engineering cooling water-1 ('C) Figure 5
Claims (1)
射時期を進角させる始動時進角機構と、エンジン完爆後
からエンジン冷却水温が所定温度に達するまでの期間グ
ロープラグへの通電を継続するアフターグロー機構とを
備えたディーゼルエンジンの始動装置であって、上記始
動時進角機構による進角量を上記グロープラグに供給さ
れるアフターグロー電圧の値に応じて制御するようにし
たことを特徴とするディーゼルエンジンの始動装置。 ２、エンジン始動時にエンジン冷却水温に応じて燃料噴
射時期を進角させる始動時進角機構と、エンジン完爆後
からエンジン冷却水温が所定温度に達するまでの期間グ
ロープラグへの通電を継続するアフターグロー機構とを
備えたディーゼルエンジンの始動装置であって、上記始
動時進角機構を、エンジン冷却水温に対応して膨縮変位
するサーモワックスで構成し且つ該サーモワックスの膨
張変位に伴って遅角操作がなされる如くするとともに、
上記サーモワックスに供給されるエンジン冷却水の流量
を上記グロープラグに供給されるアフターグロー電圧の
値に応じて制御する冷却水流量制御機構を備え、上記始
動時進角機構による進角量を、上記冷却水流量制御機構
により上記サーモワックスに供給されるエンジン冷却水
量を調整することによって制御するようにしたことを特
徴とするディーゼルエンジンの始動装置。[Claims] 1. A start-up advance mechanism that advances the fuel injection timing according to the engine cooling water temperature when starting the engine, and a glow plug for a period from when the engine is completely detonated until the engine cooling water temperature reaches a predetermined temperature. and an afterglow mechanism that continues to energize the diesel engine, the starting device controlling the amount of advance by the start-up advance mechanism in accordance with the value of the afterglow voltage supplied to the glow plug. A diesel engine starting device characterized by: 2. A start-up advance mechanism that advances the fuel injection timing according to the engine coolant temperature when starting the engine, and an after-start mechanism that continues to energize the glow plugs for a period from when the engine has completely exploded until the engine coolant temperature reaches a predetermined temperature. A diesel engine starting device equipped with a glow mechanism, wherein the starting advance mechanism is made of thermowax that expands and contracts in response to the temperature of engine cooling water, and that slows down in accordance with the expansion and displacement of the thermowax. In addition to making the corner manipulation possible,
A cooling water flow rate control mechanism that controls the flow rate of engine cooling water supplied to the thermowax according to the value of the afterglow voltage supplied to the glow plug, and an advance amount by the start-up advance mechanism; A starting device for a diesel engine, characterized in that control is performed by adjusting the amount of engine cooling water supplied to the thermowax by the cooling water flow rate control mechanism.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2070989A JP2840370B2 (en) | 1990-03-20 | 1990-03-20 | Diesel engine starter |
| DE19914108809 DE4108809C2 (en) | 1990-03-20 | 1991-03-18 | Diesel engine with an adjustment device for the injection timing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2070989A JP2840370B2 (en) | 1990-03-20 | 1990-03-20 | Diesel engine starter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03271526A true JPH03271526A (en) | 1991-12-03 |
| JP2840370B2 JP2840370B2 (en) | 1998-12-24 |
Family
ID=13447458
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2070989A Expired - Fee Related JP2840370B2 (en) | 1990-03-20 | 1990-03-20 | Diesel engine starter |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2840370B2 (en) |
| DE (1) | DE4108809C2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009508046A (en) * | 2005-09-12 | 2009-02-26 | フィアット・オートモベイス・エス．エー−フィリアル・メカニカ | Cold start assistance system for alcohol and flex engines with intake and alcohol warming |
| JP2012112266A (en) * | 2010-11-22 | 2012-06-14 | Mitsubishi Motors Corp | Heating control device of internal combustion engine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2689569B1 (en) * | 1992-04-07 | 1996-06-14 | Renault | IMPROVEMENTS ON DIESEL ENGINES. |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2521827C3 (en) * | 1975-05-16 | 1982-09-23 | Volkswagenwerk Ag, 3180 Wolfsburg | Control device for a fuel injection pump of a compression-ignition internal combustion engine |
| JPH0638146A (en) * | 1992-07-21 | 1994-02-10 | Mitsubishi Electric Corp | Equipment cover provided with heat radiating hole |
-
1990
- 1990-03-20 JP JP2070989A patent/JP2840370B2/en not_active Expired - Fee Related
-
1991
- 1991-03-18 DE DE19914108809 patent/DE4108809C2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009508046A (en) * | 2005-09-12 | 2009-02-26 | フィアット・オートモベイス・エス．エー−フィリアル・メカニカ | Cold start assistance system for alcohol and flex engines with intake and alcohol warming |
| JP2012112266A (en) * | 2010-11-22 | 2012-06-14 | Mitsubishi Motors Corp | Heating control device of internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| DE4108809A1 (en) | 1991-09-26 |
| JP2840370B2 (en) | 1998-12-24 |
| DE4108809C2 (en) | 1994-01-27 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |