JP2587047B2 - Fuel injection device for internal combustion engines - Google Patents
Fuel injection device for internal combustion enginesInfo
- Publication number
- JP2587047B2 JP2587047B2 JP62011506A JP1150687A JP2587047B2 JP 2587047 B2 JP2587047 B2 JP 2587047B2 JP 62011506 A JP62011506 A JP 62011506A JP 1150687 A JP1150687 A JP 1150687A JP 2587047 B2 JP2587047 B2 JP 2587047B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- piston
- fuel injection
- section
- opening
- 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
- 238000002347 injection Methods 0.000 title claims description 117
- 239000007924 injection Substances 0.000 title claims description 117
- 239000000446 fuel Substances 0.000 title claims description 42
- 238000002485 combustion reaction Methods 0.000 title claims description 6
- 230000009471 action Effects 0.000 claims description 6
- 238000007599 discharging Methods 0.000 claims description 4
- 238000013016 damping Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 claims description 2
- 238000010586 diagram Methods 0.000 description 17
- 239000002828 fuel tank Substances 0.000 description 6
- 230000005284 excitation Effects 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000008034 disappearance Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000013017 mechanical damping Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 1
- 238000002788 crimping Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000003302 ferromagnetic material Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000005086 pumping 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0059—Arrangements of valve actuators
- F02M63/0064—Two or more actuators acting on two or more valve bodies
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
- F02D35/0007—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for using electrical feedback
-
- 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
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
- F02D41/402—Multiple injections
- F02D41/403—Multiple injections with pilot injections
-
- 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
-
- 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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
-
- 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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure
-
- 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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/005—Arrangement of electrical wires and connections, e.g. wire harness, sockets, plugs; Arrangement of electronic control circuits in or on fuel injection apparatus
-
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
-
- 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
- F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
-
- 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
-
- 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0043—Two-way valves
-
- 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0059—Arrangements of valve actuators
- F02M63/0063—Two or more actuators acting on a single valve body
-
- 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
-
- 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
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
- F02D41/402—Multiple injections
-
- 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
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
- F02D41/406—Electrically controlling a diesel injection pump
- F02D41/408—Electrically controlling a diesel injection pump of the distributing type
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/24—Fuel-injection apparatus with sensors
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
- F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical means
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/40—Engine management systems
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、内燃機関特にディーゼル機関用の燃料噴射
装置であって、複数の噴射ノズルと、連続的に各噴射ノ
ズルに燃料噴射量を吐出する分配形噴射ポンプとが設け
られていて、この場合噴射量が相前後して噴射される前
噴射量と主噴射量とに分けられるようになっており、さ
らに、分配形噴射ポンプのポンプ作業室と放圧導管との
間を開閉制御する電磁制御式の弁装置が設けられてい
て、該弁装置が、前噴射時及び主噴射時にはポンプ作業
室を放圧導管に対して閉鎖し、吐出終了時における圧力
降下制御のためには放圧導管への所定の流過横断面を開
制御する形式のものに関する。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fuel injection device for an internal combustion engine, particularly a diesel engine, and a plurality of injection nozzles and a distribution for continuously discharging a fuel injection amount to each injection nozzle. Type injection pump is provided, and in this case, the injection amount is divided into a pre-injection amount and a main injection amount which are injected one after another, and further, a pump work chamber of the distribution type injection pump and An electromagnetically controlled valve device for controlling the opening and closing between the pressure relief conduit and the pressure relief conduit is provided. The valve device closes the pump working chamber with respect to the pressure relief conduit at the time of the pre-injection and the main injection, and at the end of discharge. For the pressure drop control in (1), the present invention relates to a type in which a predetermined flow cross section to a pressure relief conduit is controlled to open.
従来の技術 直接噴射式の燃料噴射装置を備えたディーゼル機関で
は、衝撃的な燃焼に基づく雑音の問題が存在する。実験
によれば、吐出時間中において必要な噴射量を約3〜5m
m3の小さな前噴射量と、所定の時間をおいて前噴射の前
後に噴射される主噴射量とに分けることによって、雑音
は著しく減じられることが判明した。2. Description of the Related Art In a diesel engine having a direct injection type fuel injection device, there is a problem of noise due to shocking combustion. According to the experiment, the required injection amount during the discharge time is about 3-5m
It has been found that the noise is significantly reduced by dividing the pre-injection amount as small as m 3 into the main injection amount injected before and after the pre-injection at a predetermined time interval.
冒頭に述べた形式の公知の燃料噴射装置では、分配形
噴射ポンプの吐出時間中における前噴射と主噴射とを得
るためにばねを介してプレロードをかけられた偏位ピス
トンが設けられていて、この偏位ピストンは規定の噴射
圧以上では規定の容積を解放するようになっており、こ
れによって吐出圧は噴射ノズルの閉鎖圧未満に短時間の
うちに降下し、ひいては噴射ノズルがノズルニードルに
よって閉鎖される。しかしながらこの場合温度に関連し
た油圧効果が基づいて変動する運転特性を甘受しなくて
はならない。In known fuel injectors of the type mentioned at the outset, a deflection piston is provided which is preloaded via a spring in order to obtain a pre-injection and a main injection during the delivery time of the dispensing injection pump, The displacement piston releases a prescribed volume above the prescribed injection pressure, whereby the discharge pressure drops in a short time to below the closing pressure of the injection nozzle, and thus the injection nozzle is moved by the nozzle needle. Will be closed. In this case, however, it is necessary to accept operating characteristics which vary on the basis of the temperature-related hydraulic effect.
発明の課題 ゆえに本発明の課題は温度などによって運転特性が変
化せず、常に規定の良好な運転特性を維持することがで
きる燃料噴射装置を提供することである。SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a fuel injection device whose operating characteristics do not change depending on the temperature and the like, and which can always maintain specified good operating characteristics.
課題を解決するための手段 この課題を解決するために本発明の構成では、冒頭に
述べた形式の燃料噴射装置において、弁装置の流過横断
面が少なくとも2つの段階に調節可能に構成されてお
り、弁装置が吐出時間中に、吐出終了時に完全に開放さ
れる流過横断面に比べて減じられた流過横断面を短時間
開制御するように構成されている。According to one aspect of the invention, a fuel injection device of the type described at the outset is characterized in that the flow cross section of the valve device is adjustable in at least two stages. In addition, the valve device is configured such that during the discharge time, the flow cross-section that is reduced compared to the flow cross-section that is completely opened at the end of discharge is controlled to be opened for a short time.
発明の効果 本発明のように構成された燃料噴射装置には公知のも
のに比べて、変動する運転特性が回避されるという利点
がある。前噴射の後及び主噴射の後で放圧導管に開制御
される流過横断面を本発明のように異ならせて設定する
ことによって、最適な噴射過程のために不可欠な2つの
要求すなわち、高い機関回転数時にも前噴射と主噴射と
の間の時間的な間隔が小さいという要求と、吐出終了時
における迅速な圧力消滅のために主噴射の終了時におけ
る圧力降下制御横断面が大きいという要求とを満たすこ
とができる。この場合開制御される流過横断面は弁開口
の寸法と弁部材の開放行程の値とに関連している。つま
り弁装置の短い切換え時間は開放行程が小さい場合に達
成することができる。Advantageous Effects of the Invention The fuel injection device configured as in the present invention has an advantage that a fluctuating operating characteristic is avoided as compared with a known device. By setting the flow cross sections, which are controlled open to the pressure relief conduit after the pre-injection and after the main injection, differently as in the present invention, two essential requirements for an optimal injection process are: The requirement that the time interval between the pre-injection and the main injection be small even at a high engine speed, and that the pressure drop control cross-section at the end of the main injection is large due to the rapid disappearance of pressure at the end of discharge. Can meet with your request. In this case, the flow cross section that is controlled to open depends on the size of the valve opening and the value of the opening stroke of the valve member. That is, a short switching time of the valve device can be achieved when the opening stroke is small.
実施態様 特許請求の範囲の従属項に記載した手段によって、本
発明による燃料噴射装置の有利な実施態様が可能であ
る。Embodiments Advantageous embodiments of the fuel injection device according to the invention are possible by means of the dependent claims.
例えば特許請求の範囲第2項記載のように構成されて
いると、一定の弁開口において調節可能な流過横断面
が、スライダ又は突き棒として構成された弁部材の開放
行程に影響を与えることによって得られる。For example, when configured as claimed in claim 2, an adjustable flow cross section at a certain valve opening influences the opening stroke of a valve member configured as a slider or a push rod. Obtained by
特許請求の範囲第3項及び(又は)第4項記載の有利
な実施態様によって、少なくとも2つの異なった所定値
への開放行程の異なった調節を比較的簡単に実現するこ
とができる。By means of the advantageous embodiments of claims 3 and / or 4, different adjustments of the opening stroke to at least two different predetermined values can be realized relatively simply.
特許請求の範囲第5項記載の有利な実施態様によっ
て、弁部材の機械的な緩衝が前噴射の終了時に生ぜしめ
られ、これによって電磁弁の短時間の開放時における弁
部材のはね返りが回避される。According to an advantageous embodiment of the invention, a mechanical damping of the valve element is produced at the end of the pre-injection, so that the valve element does not spring during a brief opening of the solenoid valve. You.
また特許請求の範囲第6項記載の有利な実施態様によ
って、吐出開始時における電磁弁の第1の閉鎖のための
切換え時間を極めて短くすることができる。それという
のはこの場合弁部材の閉鎖距離が既に小さな行程距離に
定められているからである。According to the advantageous embodiment of claim 6, the switching time for the first closing of the solenoid valve at the start of the discharge can be very short. This is because in this case the closing distance of the valve member is already set to a small stroke distance.
特許請求の範囲第8項記載の有利な実施態様では、開
閉時における電磁弁の切換え時間を著しく減じるのに役
立つ。An advantageous embodiment according to claim 8 serves to significantly reduce the switching time of the solenoid valve during opening and closing.
さらにまた特許請求の範囲第9項記載の実施態様によ
って、開放制御のために所定された流過横断面は、互い
に異なった開放横断面を備えた弁開口を有する互いに並
列に接続された電磁弁によって調節される。これによっ
てより小さな行程距離に基づいて電磁弁の開放時には極
端に短い切換え時間を得ることができ、この場合主噴射
の終了時における大きな圧力降下制御横断面を断念する
必要も、また、前噴射の終了時における大きな圧力降下
制御横断面、つまり極めて大きな吐出圧低下のために前
噴射と主噴射との間に許されないほど大きな間隔を惹起
するおそれのある大きな圧力降下制御横断面を甘受する
必要もない。Furthermore, according to an embodiment of the invention, the flow cross-sections determined for the opening control have solenoid valves connected in parallel with valve openings having different opening cross-sections. Adjusted by. This makes it possible to obtain an extremely short switching time when the solenoid valve is opened based on a smaller stroke distance, in which case it is necessary to abandon the large pressure drop control cross section at the end of the main injection, and It is also necessary to accept a large pressure drop control cross section at the end, i.e. a large pressure drop control cross section which can cause an unacceptably large gap between the pre-injection and the main injection due to a very large discharge pressure drop. Absent.
実施例 次に図面につき本発明の実施例を説明する。Embodiment Next, an embodiment of the present invention will be described with reference to the drawings.
第1図に部分的に示された、ディーゼル機関用の燃料
噴射装置は、複数の噴射ノズルここでは4つの噴射ノズ
ル10を有しており、これらの噴射ノズルは各1つの噴射
導管11を介して燃料分配形噴射ポンプ13の接続管片12と
接続されている。The fuel injection device for a diesel engine, partially shown in FIG. 1, has a plurality of injection nozzles, here four injection nozzles 10, each of which is connected via one injection conduit 11. To the connecting pipe piece 12 of the fuel distribution type injection pump 13.
分配形噴射ポンプ13のケーシング14にはバレル15が配
置されており、このバレル15内においてプランジャ16は
往復運動と同時に回転運動を行う。プランジャ16はカム
駆動装置17によって軸18を介して駆動され、軸18はディ
ーゼル機関の回転数の半分の回転数で回転する。プラン
ジャ16とバレル15とによってポンプ作業室19は制限され
ており、このポンプ作業室19には分配形噴射ポンプ13の
ケーシング14における吸込み室21から供給通路20を介し
て燃料が供給される。ポンプ作業室19から燃料は軸方向
の中心孔22と半径方向の分配孔23とを介して半径方向の
吐出孔24に向かって順々に分配される。これらの吐出孔
24はそれぞれ接続管片12と接続されている。プランジャ
16の端部範囲には縦溝25が設けられており、これらの縦
溝25はプランジャ16の、ポンプ作業室19を制限している
端面に開口していて、プランジャ16の吸込み行程中は供
給通路20とポンプ作業室19とを接続している。吸込み室
21はフィードポンプ26によって燃料タンク27からの燃料
で満たされていて、調圧弁28を介して、燃料タンク27に
開口している戻し導管29と接続されている。A barrel 15 is disposed in a casing 14 of the distribution type injection pump 13, and in this barrel 15, a plunger 16 performs a reciprocating motion and a rotating motion simultaneously. The plunger 16 is driven by a cam driving device 17 via a shaft 18, and the shaft 18 rotates at half the rotational speed of the diesel engine. The pump working chamber 19 is restricted by the plunger 16 and the barrel 15, and fuel is supplied to the pump working chamber 19 from the suction chamber 21 in the casing 14 of the distribution type injection pump 13 via the supply passage 20. Fuel is sequentially distributed from the pump working chamber 19 toward the radial discharge hole 24 through the axial center hole 22 and the radial distribution hole 23. These discharge holes
24 are connected to the connection pipe pieces 12 respectively. Plunger
In the end area of 16 there are provided longitudinal grooves 25 which open into the end face of the plunger 16 which restricts the pump working chamber 19 and which are supplied during the suction stroke of the plunger 16. The passage 20 and the pump working chamber 19 are connected. Suction chamber
Numeral 21 is filled with fuel from a fuel tank 27 by a feed pump 26 and is connected via a pressure regulating valve 28 to a return conduit 29 opening to the fuel tank 27.
ケーシング14には電磁制御式の弁装置30が一体に組み
込まれており、この弁装置30の電気的な接続端子31は切
換え信号発信器32と接続されている。弁装置30は第1図
において部分的に破断して示されており、断面図で示さ
れている流入孔33はポンプ作業室19において開口してい
て、プランジャ16の吸い込み側ここでは供給通路20と接
続された放圧通路34を有している。弁装置30は吐出時間
のためにポンプ作業室19を放圧通路34から閉鎖し、吐出
終了時にはポンプ作業室19における迅速な圧力消滅のた
めに放圧通路34への所定の流過横断面を開制御する。An electromagnetically controlled valve device 30 is integrally incorporated in the casing 14, and an electrical connection terminal 31 of the valve device 30 is connected to a switching signal transmitter 32. The valve device 30 is shown partially cut away in FIG. 1, and the inlet 33, shown in cross section, is open in the pump working chamber 19 and is located on the suction side of the plunger 16, here the supply passage 20. And a pressure release passage 34 connected to the pressure release passage 34. The valve device 30 closes the pump working chamber 19 from the pressure relief passage 34 for the discharge time, and at the end of the discharge, a predetermined flow cross section to the pressure relief passage 34 for rapid pressure disappearance in the pump working chamber 19. Open control.
電磁制御式の弁装置30の第1実施例は第2図に縦断面
図で示されている。弁装置30は、分配形噴射ポンプ13の
ケーシング14にねじ込み可能な弁ケーシング35を有して
おり、この弁ケーシング35内には電磁弁36と調節マグネ
ット37とが取り付けられてる。電磁弁36及び調節マグネ
ット37はそれぞれ強磁性材料から成るコア38;39を有し
ており、このコア38;39はそれぞれ鉢形の内部にリング
状のマグネットコイル40;41を保持している。コア38,39
の開口はそれぞれプレート42;43によっておおわれてお
り、このプレート42;43は中央に貫通孔を有していて、
この貫通孔を貫いて可動子44;45の中央円筒形の管片が
延びている。可動子44;45はコア38;39に、可動子44;45
の調節距離を規定する空隙46;47をおいて対向位置して
いる。コア38;39の開口はそれぞれガイドブシュ48;49が
配置されている。ガイドブシュ48においては弁部材50が
かつガイドブシュ49においては調節ピストン51がそれぞ
れ2つのガイド区分501,502;511,512で案内されてい
る。弁部材50及び調節ピストン51は端部側にそれぞれ圧
着プレート503;513を有しており、この圧着プレートは
可動子44;45の中空円筒形の管片に突出していて、可動
子と堅く結合されている。可動子44;45は弁開放ばね52
もしくな戻しばね53の作用下で開放位置に保たれてお
り、両ばねはそれぞれ圧着プレート503;513を可動子44;
45のリング状の接触肩部441;451に押し付けている。弁
開放ばね52と戻しばね53とはそれぞれ所属のガイドブシ
ュ48;49の環状肩部において支持されている。A first embodiment of the electromagnetically controlled valve device 30 is shown in longitudinal section in FIG. The valve device 30 has a valve casing 35 which can be screwed into the casing 14 of the distribution type injection pump 13, in which a solenoid valve 36 and an adjusting magnet 37 are mounted. Each of the solenoid valve 36 and the adjusting magnet 37 has a core 38, 39 made of a ferromagnetic material, and the core 38, 39 holds a ring-shaped magnet coil 40, 41 inside a bowl. Core 38,39
Are covered by plates 42, 43, respectively, which have a central through hole,
A central cylindrical tube piece of the mover 44; 45 extends through the through hole. The movers 44 and 45 are attached to the cores 38 and 39 and the movers 44 and 45
Are positioned opposite each other with a gap 46; Guide bushes 48; 49 are arranged in the openings of the cores 38, 39, respectively. In the guide bush 48, the valve member 50 and in the guide bush 49 the adjusting piston 51 are guided in two guide sections 501, 502; 511, 512, respectively. The valve member 50 and the adjusting piston 51 have, on the end side, crimping plates 503, 513, respectively, which protrude into the hollow cylindrical tube piece of the armatures 44, 45 and are firmly connected to the armatures. Have been. Movers 44 and 45 are valve opening springs 52
The springs are kept in the open position under the action of a return spring 53, and both springs respectively move the pressure plates 503; 513 to the mover 44;
It is pressed against 45 ring-shaped contact shoulders 441; 451. The valve opening spring 52 and the return spring 53 are supported on the annular shoulders of the associated guide bush 48; 49, respectively.
弁部材50は端部側の弁ヘッド504で弁座54と協働し、
この弁座504は弁開口55を取り囲んでいる。弁開口55
は、分配形噴射ポンプ13のポンプ作業室19に開口してい
る流入孔33を制限している。流入孔33と弁開口55と弁座
54とは弁座体56に取り付けられており、この弁座体はリ
ング状のコア38と一緒に中空室57を形成し、この中空室
からは流出孔58が放圧通路34に通じている。ガイドブシ
ュ48はコア38を越えて弁座体56にまで突出して環状室59
を制限しており、この環状室59はガイドブシュ48におけ
る接続孔60を介して中空室57と接続されている。The valve member 50 cooperates with the valve seat 54 at an end-side valve head 504,
The valve seat 504 surrounds the valve opening 55. Valve opening 55
Restricts the inflow hole 33 opened in the pump working chamber 19 of the distribution type injection pump 13. Inflow hole 33, valve opening 55, and valve seat
The valve seat 54 is attached to a valve seat 56, which forms a hollow chamber 57 together with the ring-shaped core 38, from which an outlet hole 58 communicates with the pressure release passage 34. . The guide bush 48 protrudes beyond the core 38 to the valve seat 56 and an annular chamber 59.
The annular chamber 59 is connected to the hollow chamber 57 via a connection hole 60 in the guide bush 48.
調節マグネット37の調節ピストン51は電磁弁36の可動
子44における中央開口を貫いて延び、そこで弁部材50の
圧着プレート503に係合する。反対の側において調節ピ
ストン51はその圧着プレート513でケーシングに対して
不動のストッパ61に接触している。接続端子31を介し
て、電磁弁36及び調節マグネット37のマグネットコイル
40,41には励磁電流が供給される。The adjustment piston 51 of the adjustment magnet 37 extends through the central opening in the armature 44 of the solenoid valve 36 and engages with the pressure plate 503 of the valve member 50 there. On the opposite side, the adjusting piston 51 is in contact with a stop 61 which is stationary with respect to the casing at its crimp plate 513. The magnet coil of the solenoid valve 36 and the adjustment magnet 37 via the connection terminal 31
An excitation current is supplied to 40 and 41.
調節マグネット37を用いていまや弁座54と弁部材50の
弁ヘッド504との間における流過横断面は弁部材50の開
放時に2つの段階に調節され得る。これは弁部材50の開
放行程が2つの値h1とh2とに調節可能であることに基づ
き、この場合h1はh2よりも大である。調節マグネット37
が励磁されていない場合調節ピストン51は第2図に示さ
れた位置を占めている。弁部材50は最大行程h1進んだ後
に初めてその圧着プレート503で調節ピストン51に接触
する。調節マグネット37が励磁されると、可動子45が引
き付けられ、調節ピストン51は弁部材50に向かって、そ
のガイド区分512がケーシングに対して不動のストッパ6
2に接触するまで運動する。調節ピストン51が調節距離h
aだけこのように軸方向運動することによって、弁部材5
0の開放行程はこの調節距離haだけ減じられ、この結果
電磁弁36の開放時には弁部材50の圧着プレート503は開
放行程h2=h1−haの後で既に調節ピストン51に接触する
ことになる。With the aid of the adjusting magnet 37, the flow cross section between the valve seat 54 and the valve head 504 of the valve member 50 can be adjusted in two stages when the valve member 50 is opened. This is based on that opening stroke of the valve member 50 is adjustable in two values h 1 and h 2, in this case h 1 is greater than h 2. Adjustable magnet 37
When is not energized, the adjusting piston 51 occupies the position shown in FIG. The valve member 50 is in contact first the adjusting piston 51 in its crimped plate 503 after traveling up stroke h 1. When the adjusting magnet 37 is excited, the armature 45 is attracted, and the adjusting piston 51 moves toward the valve member 50 so that the guide section 512 moves the stopper 6 which is immovable with respect to the casing.
Exercise until you touch 2. Adjusting piston 51 is adjusted distance h
a Only by this way to axial movement, the valve member 5
Opening stroke of 0 is reduced by the adjustment path h a, pressure disk 503 of the valve member 50 during the opening of this result the solenoid valve 36 is in contact with the opening stroke h 2 = h 1 -h already adjusting piston 51 after a Will be.
次に分配形噴射ポンプ13との関連における上述の弁装
置30の作用形式を第5図に示された線図を参照しながら
説明する。この場合線図a〜gにはそれぞれ時間tを関
数として、プランジャ16の軸方向行程に相当するカム駆
動装置17のカム行程hN(a)、ポンプ作業室19において
生じるフィード圧p(b)、噴射ノズル10におけるノズ
ルニードルの行程hD(c)、電磁弁36の弁部材50の行程
hV(d)、電磁弁36のための切換えパルス(e)、調節
マグネット37のための切換えパルス(f)及び電磁弁36
の励磁電流i(g)が示されている。Next, the mode of operation of the valve device 30 in connection with the distribution type injection pump 13 will be described with reference to the diagram shown in FIG. In this case, the diagrams a to g respectively show the cam stroke h N (a) of the cam drive 17 corresponding to the axial stroke of the plunger 16 and the feed pressure p (b) generated in the pump working chamber 19 as a function of time t. The stroke h D of the nozzle needle in the injection nozzle 10 (c), the stroke of the valve member 50 of the solenoid valve 36
h V (d), switching pulse (e) for solenoid valve 36, switching pulse (f) for adjusting magnet 37 and solenoid valve 36
Are shown in FIG.
時点t1において電磁弁36と調節マグネット37とが一緒
に制御される。電磁弁36は閉鎖し、弁部材50の開放行程
は小さな値h2に固定される。電磁弁36の閉鎖後電磁弁36
の励磁電流iは保持電流iH1に制限される。時点tNにお
いてプランジャ16はその下死点に達し、その吐出行程を
開始する。ポンプ作業室19における圧力pが上昇し、ノ
ズルニードルの閉鎖圧の超過後(ノズル開放圧pD)
にノズル10が開放して前噴射が始まる。An electromagnetic valve 36 and adjusting the magnet 37 is controlled together in time t 1. Solenoid valve 36 is closed, the opening stroke of the valve member 50 is fixed to a small value h 2. Solenoid valve 36 after solenoid valve 36 is closed
Is limited to the holding current i H1 . The plunger 16 reaches its bottom dead center at time t N, begins its discharge stroke. After the pressure p in the pump working chamber 19 rises and exceeds the nozzle needle closing pressure (nozzle opening pressure p D )
Then, the nozzle 10 is opened and the pre-injection starts.
時点t2において電磁弁36は遮断される。弁部材50は調
節された開放行程h2まで開放する。ポンプ作業室19にお
ける圧力が降下し、ノズル開放圧よりも下がる。ノズル
ニードルは再び閉鎖し、前噴射が終了する。励磁電流i
は迅速に消滅し、次いで保持電流iH2に高められる。こ
れによって電磁弁36の再入力時における無駄時間がなく
なる。Solenoid valve 36 at time t 2 is cut off. The valve member 50 is opened until the opening stroke h 2 that has been modulated. The pressure in the pump working chamber 19 drops and falls below the nozzle opening pressure. The nozzle needle closes again and the pre-injection ends. Exciting current i
Disappears quickly and is then increased to the holding current i H2 . This eliminates a dead time when the solenoid valve 36 is re-input.
時点t3において電磁弁36には再び全電流が供給され
る。電磁弁36は閉鎖し、ポンプ作業室における圧力pが
再び上昇し、ノズル開放圧pDを上回ると共に主噴射
が始まる。調節マグネット47の励磁は時点t3において遮
断され、これによって調節ピストン51は戻しばね53を介
して第2図に示された位置に戻される。これによって弁
部材50のために全開放行程h1が利用可能になる。Total current is again supplied to the solenoid valve 36 at time t 3. Solenoid valve 36 is closed, the pressure p is increased again in the pump work chamber, the main injection is started with above the nozzle opening pressure p D. Excitation of the adjusting magnet 47 is shut off at time t 3, whereby the adjusting piston 51 is returned to the position shown in Figure 2 through the springs 53 return. This entire opening stroke h 1 for the valve member 50 becomes available.
時点t4において電磁弁30の励磁電流が再び遮断され
る。弁開放ばね52の作用下で弁部材50は調節ピストン51
におけるストッパのところまで移動する。弁座54と弁ヘ
ッド504との間におけるいまや利用可能な大きな流過横
断面を通してポンプ作業室19における圧力は急激に降下
させられる。ノズル開放圧pDが下回られるやいな
や、ノズルニードルの閉鎖が始まり、主噴射が終了す
る。Exciting current of the solenoid valve 30 is cut off again at the instant t 4. Under the action of the valve opening spring 52, the valve member 50
Move to the stop in. Through the now available large flow cross-section between the valve seat 54 and the valve head 504, the pressure in the pump work chamber 19 is rapidly reduced. As soon as the nozzle opening pressure p D is lower than the closing of the nozzle needle starts, the main injection ends.
第3図には第1図に示された電磁式の弁装置30の別の
実施例が示されている。この実施例が第2図に示された
電磁式の弁装置30と異なっている点は、調節マグネット
37の調節ピストン50′への衝突時における弁部材のはね
返り又はずれ運動を回避するために機械的な緩衝装置が
設けられていることだけである。このために調節ピスト
ン51′の内部には緩衝突き棒63が軸方向摺動可能に案内
されている。緩衝突き棒63は調節ピストン51′の全長に
わたって延びていて、調節ピストン51′の両端面におい
て突出している。弁部材50とは反対側の端部に緩衝突き
棒63は支持プレート64を有しており、この支持プレート
には、ケーシング側において支持された緩衝ばね65が作
用する。緩衝ばね65のばね力は弁開放ばね52のばね力よ
りも小さく設定されている。弁部材50に向いている端部
で緩衝突き棒63は緩衝ばね65の作用下で弁部材50の圧着
プレート503に接触している。電磁弁36の入力時ひいて
は閉鎖時に緩衝突き棒63は弁部材50に向けられた端部で
所定の値だけ調節ピストン51′を越えて突出する。いま
や電磁弁36が遮断されて弁部材50が弁開放ばね52の作用
下で調節ピストン51′に向かって運動すると、弁部材50
は調節ピストン51′に当接する前にまず初め緩衝突き棒
63にぶつかる。これによって弁部材50の運動は前もって
制動される。その他の点では第3図に示された弁装置3
0′の全部材は第2図における弁装置30の部材と同一な
ので、等しい部材は等しい符号で示されている。FIG. 3 shows another embodiment of the electromagnetic valve device 30 shown in FIG. This embodiment is different from the electromagnetic valve device 30 shown in FIG.
The only difference is that a mechanical damping device is provided in order to prevent the valve member from bouncing or displacing in the event of a collision of the 37 with the adjusting piston 50 '. For this purpose, a damping push rod 63 is guided slidably in the axial direction inside the adjusting piston 51 '. The buffer rod 63 extends over the entire length of the adjusting piston 51 'and projects at both end faces of the adjusting piston 51'. At the end opposite to the valve member 50, the shock-absorbing rod 63 has a support plate 64, on which a shock-absorbing spring 65 supported on the casing side acts. The spring force of the buffer spring 65 is set smaller than the spring force of the valve opening spring 52. At the end facing the valve member 50, the buffer push bar 63 contacts the pressure plate 503 of the valve member 50 under the action of a buffer spring 65. When the solenoid valve 36 is turned on and therefore closed, the damping push rod 63 projects beyond the adjusting piston 51 'by a predetermined value at the end facing the valve member 50. Now, when the solenoid valve 36 is shut off and the valve member 50 moves toward the adjusting piston 51 'under the action of the valve opening spring 52, the valve member 50
Is a shock-absorbing rod before contacting the adjusting piston 51 '.
Hit 63. As a result, the movement of the valve member 50 is damped in advance. Otherwise, the valve device 3 shown in FIG.
Since all the components of 0 'are the same as those of the valve device 30 in FIG. 2, the same components are denoted by the same reference numerals.
第1図における電磁式の弁装置30のさらに別の実施例
は第4図に符号30″で示されている。この弁装置30″は
第2図における弁装置30′及び第3図における弁装置3
0″と調節マグネット37の調節ピストン51″の構成にお
いて異なっているだけであり、従って等しい部材は等し
い符号で示されている。A further embodiment of the electromagnetic valve device 30 in FIG. 1 is designated by the reference numeral 30 "in FIG. 4. The valve device 30" is a valve device 30 'in FIG. 2 and a valve in FIG. Device 3
The only difference is in the configuration of the adjusting piston 51 "of the adjusting magnet 37 and 0", so that identical parts are denoted by the same reference numerals.
ガイドブシュ49内においてガイド区分511,512で軸方
向摺動可能な調節ピストン51″は2つのピストン区分66
と67とに分割されており、この場合一方のピストン区分
66はガイド区分511と圧着プレート513とを有し、他方の
ピストン区分67はガイド区分512を有している。両ピス
トン区分66,67の間にはピストンばね68が支持されてお
り、従ってこのピストンばね68はピストン区分66を可動
子45に向かって、ピストン区分67を弁部材50に向かって
負荷している。ガイドブシュ49は半径方向内側に向かっ
て突出しているストッパ肩部69を有しており、このスト
ッパ肩部69にはピストン区分67のガイド区分512がピス
トンばね68の作用下で接触している。この位置において
両ピストン区分66,67は互いの間に間隔hAを有してい
る。ピストンばね68のばね力は弁開放ばね52のばね力よ
りも大きく設定されているので、弁部材50はピストン区
分67によって弁開放ばね52の力に抗して押される。ガイ
ドブシュ49におけるストッパ肩部69は、ストッパ肩部69
に接触しているピストン区分67が弁部材50を、弁部材50
の行程hVが小さな値h2に調節されるように移動させるよ
うな位置を占めている。調節マグネット37が給電される
と、ピストン区分67はピストン区分66によってストッパ
肩部67に固定され、これによってピストンばね68は無効
になる。In the guide bush 49, the adjusting piston 51 ″ slidable axially in the guide sections 511, 512 comprises two piston sections 66.
And 67, in this case one piston section
66 has a guide section 511 and a pressure plate 513, while the other piston section 67 has a guide section 512. A piston spring 68 is supported between the two piston sections 66, 67 and thus loads the piston section 66 towards the armature 45 and the piston section 67 towards the valve member 50. . The guide bush 49 has a stop shoulder 69 projecting radially inward, with which the guide section 512 of the piston section 67 contacts under the action of the piston spring 68. Both pistons division 66 and 67 in this position is at a distance h A therebetween. Since the spring force of the piston spring 68 is set to be greater than the spring force of the valve opening spring 52, the valve member 50 is pushed by the piston section 67 against the force of the valve opening spring 52. The stopper shoulder 69 of the guide bush 49 is
Piston section 67 in contact with the valve member 50, the valve member 50
Stroke h V of accounts for position is moved so as to be adjusted to a small value h 2. When the adjusting magnet 37 is energized, the piston section 67 is fixed to the stop shoulder 67 by the piston section 66, whereby the piston spring 68 is deactivated.
電磁式の弁装置30″の作用形式は弁装置30の作用形式
とほとんど同じであり、第6図に示された線図を用いて
難なく説明することができる。第6における個々の線図
a〜gの意味は第5図における各線図a〜gと同一であ
る。また、電磁弁36もしくはその調節部材50の開放行程
hVの時間的な経過を示す線図d以外のすべての線図は一
致している。調節ピストン51″の構成が異なっているこ
とに基づいて調節マグネット37及びマグネット弁36の励
磁前に調節部材50の行程は既に小さな値h2に調節されて
いる。電磁弁36が励磁されると、弁部材50は電磁弁36と
閉鎖するためにこの小さな行程距離h2だけ移動すればよ
いので、電磁弁の閉鎖時により短い切換え時間が得られ
る。調節マグネット37の給電によって可動子45が引き付
けられ、可動子45はピストン区分66を移動させてこのピ
ストン区分66と共にピストン区分67をストッパ肩部69に
しっかりと固定する。従って時点t2における電磁弁36の
第1の開放時には弁部材50の開放行程hVは小さな値h2に
制限されている。時点t3において調節マグネット37が遮
断され、調節ピストン51″は第4図に示された位置を占
める。時点t4における電磁弁36の第2の開放時にピスト
ンばね68のばね力はポンプ作業室19における高い圧力に
基づいて克服され、この結果弁部材50は最大開放行程h1
=h2+hAを行う。ポンプ作業室における圧力pの低下後
に調節部材50はピストンばね68によってピストン区分67
を介して再び押し戻され、電磁弁の閉鎖時に弁部材50に
よって行われる行程hVは開放行程の小さな値h2に相当す
る。The mode of operation of the electromagnetic valve device 30 "is almost the same as the mode of operation of the valve device 30 and can be explained without difficulty using the diagram shown in Fig. 6. The individual diagram a in Fig. 6 The meaning of .about.g is the same as each diagram a.g in FIG. 5. The opening stroke of the solenoid valve 36 or its adjusting member 50 is also described.
All diagrams other than diagrams d indicating the time elapsed h V is consistent. Stroke of the adjustment member 50 prior to the excitation of the adjusting piston 51 adjusting magnet 37 and the magnet valve 36 constructed in accordance with that are different for "is adjusted already to a small value h 2. When the solenoid valve 36 is energized , the valve member 50 since it is sufficient move only the small stroke distance h 2 to close the solenoid valve 36, the movable element 45 is attracted by the power supply. regulatory magnet 37 short switching time by the time the closing of the solenoid valve is obtained is, the mover 45 moves the piston segment 66 the piston segment 67 together with the piston segment 66 firmly fixed to the stopper shoulder 69. during the first opening of the solenoid valve 36 at time t 2 Thus the valve member 50 opening stroke h V Controlled magnet 37 at. the time t 3 when being limited to a small value h 2 is cut off, adjusting piston 51 'occupies the position shown in Figure 4. The spring force of the piston spring 68 when the second opening of the solenoid valve 36 is overcome on the basis of the higher pressure in the pump working chamber 19 at time t 4, as a result the valve member 50 is the maximum opening stroke h 1
= Perform h 2 + h A. After the pressure p has dropped in the pump working chamber, the adjusting element 50 is moved by the piston spring 68 into the piston section 67.
Again through the pushed back, stroke h V made by the valve member 50 when closing of the solenoid valve corresponds to a value h 2 of the opening stroke.
第7図には第1図における切換え信号発信器32のブロ
ック回路図が示されている。電磁弁36のための制御信号
は計算器70によって、記憶された特性線領域から算出さ
れる。この特性線領域は制御信号φmを制御角の形で
(m=1,2,3,4)機関回転数n、負荷d、燃料温度Tの
関数として有している。さらに、例えばプランジャ16の
上死点に関連している基準マークBZが考慮される。補足
的に別の計算器71においてノズルニードルhDの所望の経
過の特性線領域が上記パラメータの関数として記憶され
ている。各噴射ノズル10にはセンサ72(第1図参照)が
配置されていて、このセンサはノズルニードル行程の実
際の経過をとらえて電気信号として切換え信号発信器32
に供給し、ここでこれらの切換え信号はタイムマルチプ
レックスにおいて比較器73に供給される。ノズルニード
ル行程の実際の経過と記憶された特性線領域によるノズ
ルニードル行程の所望の経過との間における調整差は制
御信号φmの修正のために計算器70に供給される。計算
器70の特性線領域から取り出される制御値はこの際に、
調整差が可能な限り小さくなるように変えられる。制御
信号φmは、電磁弁36のマグネットコイル40に励磁電流
(この励磁電流の経過は第5図及び第6図の線図gに示
されている)を供給する電流調整器74に供給される。FIG. 7 shows a block circuit diagram of the switching signal generator 32 in FIG. The control signal for the solenoid valve 36 is calculated by the calculator 70 from the stored characteristic line area. This characteristic line region has the control signal φ m in the form of a control angle (m = 1, 2, 3, 4) as a function of the engine speed n, the load d and the fuel temperature T. Furthermore, reference marks BZ, for example, which relate to the top dead center of the plunger 16, are taken into account. Characteristic line region of the desired course of the nozzle needle h D are stored as a function of the parameters in another calculator 71 supplementary. Each injection nozzle 10 is provided with a sensor 72 (see FIG. 1) which detects the actual course of the nozzle needle stroke and switches it as an electrical signal to a switching signal transmitter 32.
Where these switching signals are provided to a comparator 73 in a time multiplex. Adjusting difference between the desired course of the nozzle needle stroke by actual elapsed and the stored characteristic line region of the nozzle needle stroke is supplied to the calculator 70 for control signals phi m modification. At this time, the control value extracted from the characteristic line area of the calculator 70 is
The adjustment difference is changed to be as small as possible. The control signal φ m is supplied to a current regulator 74 which supplies an exciting current to the magnet coil 40 of the solenoid valve 36 (the course of this exciting current is shown in the diagrams g of FIGS. 5 and 6). You.
制御信号の別の修正可能性はポンプ作業室19における
吐出圧pを検出することによって行うことができる。例
えば時点t2における圧力高さ(第5b図及び第6b図参照)
に基づいて噴射ノズル間の噴射量のばらつきを推論する
ことが可能であり、この噴射量のばらつきは電磁弁36の
切換え時点t2の相応な変化によって補償することができ
る。さらに、吐出圧の上昇からカムもしくはプランジャ
16の吐出行程の正確な開始を規定するという利点が得ら
れる。従って調整誤差は特性線領域の自動的な後調節に
よって補正することができる。このことは特に直接噴射
式の分配形噴射ポンプにおいて有利である。それという
のはこの場合には、小さな誤調整でさえも大きな噴射量
のばらつきを惹起する極めて急勾配のカムが使用される
からである。Another possibility of correcting the control signal can be achieved by detecting the discharge pressure p in the pump working chamber 19. For example the pressure level at the time point t 2 (see FIG. 5b and Figure 6b)
The it is possible to infer the variations in the injection quantity between the injection nozzle based, variation in the injection quantity can be compensated for by a corresponding change in the switching time point t 2 of the solenoid valve 36. In addition, the cam or plunger
The advantage is obtained of defining the exact start of the 16 discharge strokes. The adjustment error can therefore be corrected by automatic post-adjustment of the characteristic line area. This is particularly advantageous for direct injection dispensing injection pumps. This is because in this case very steep cams are used, which cause large injection quantity variations even with small misadjustments.
第8図には燃料噴射装置の別の実施例が略示されてい
る。燃料タンクは符号80で、燃料フィードポンプは符号
81で、燃料分配形噴射ポンプは符号82で示されている分
配形噴射ポンプ82は第1図に示されかつ記載された分配
形噴射ポンプ13と同一に構成されている。分配形噴射ポ
ンプ82は同様の形式で戻し導管83を介して燃料タンク80
とかつ噴射導管84を介して複数の噴射ノズル85と接続さ
れている。第1図におけると同様、分配形噴射ポンプ82
には電磁制御式の弁装置87が接続されており、この弁装
置は一方では分配形噴射ポンプ82のポンプ作業室にかつ
他方では放圧導管86に接続されていて、ポンプ作業室を
放圧導管86と接続し、かつ吐出時間中はポンプ作業を放
圧導管86から切り離す。FIG. 8 schematically shows another embodiment of the fuel injection device. The fuel tank is code 80, the fuel feed pump is code 80
At 81, the fuel dispensing injection pump is designated by the reference numeral 82. The dispensing injection pump 82 is constructed identically to the distributing injection pump 13 shown and described in FIG. The dispensing injection pump 82 is connected in a similar manner to the fuel tank 80 via the return line 83.
And a plurality of injection nozzles 85 via an injection conduit 84. As in FIG. 1, the dispensing injection pump 82
Is connected to an electromagnetically controlled valve device 87, which is connected on the one hand to the pump working chamber of the dispensing injection pump 82 and on the other hand to a pressure relief conduit 86, for discharging the pump working chamber. Connects to conduit 86 and disconnects pumping from pressure relief conduit 86 during the discharge time.
第1図に示された燃料噴射装置におけるように、この
場合においても、分配形噴射ポンプ82の吐出時間中に噴
射ノズル85を介してディーゼル機関のシリンダにそれぞ
れ噴射される燃料量は、時間的に連続して噴射される前
噴射量と主噴射量とに分けられる。このために弁装置87
は互いに並列に接続された2つの電磁弁88,89を有して
おり、両電磁弁の弁開口は異なった開口横断面を有して
いる。この場合電磁弁88は小さな弁開口横断面を有して
おり、これは電磁弁88の貫通孔における絞りによって示
されている。両電磁弁88,89のマグネットコイル90,91は
同様に切換え信号発信器(図面をわかりやすくするため
に図示せず)と接続されている。As in the fuel injection device shown in FIG. 1, in this case as well, the amount of fuel respectively injected into the cylinder of the diesel engine via the injection nozzle 85 during the discharge time of the distribution type injection pump 82 is temporally different. And the main injection amount. For this purpose the valve device 87
Has two solenoid valves 88, 89 connected in parallel to one another, the valve openings of both solenoid valves having different opening cross sections. In this case, the solenoid valve 88 has a small valve opening cross section, which is indicated by a restriction in the through hole of the solenoid valve 88. The magnet coils 90, 91 of both solenoid valves 88, 89 are likewise connected to a switching signal transmitter (not shown for clarity).
弁装置87と接続されている分配形噴射ポンプ82の作用
形式は第9図に示された線図から知ることができる。第
5図及び第6図におけるようにこれらの線図はそれぞれ
時間を関数としてカム行程hN(a)、ポンプ作業室にお
ける圧力p(b)、噴射ノズルにおけるノズルニードル
行程hD(c)、電磁弁88における切換えパルス(e)及
び電磁弁89における切換えパルス(f)を示している。
線図a〜fは第5図及び第6図における線図と同じに示
されている。The mode of operation of the dispensing injection pump 82 connected to the valve device 87 can be seen from the diagram shown in FIG. As in FIGS. 5 and 6, these diagrams respectively show the cam stroke h N (a), the pressure p (b) in the pump working chamber, the nozzle needle stroke h D (c) in the injection nozzle as a function of time, The switching pulse (e) at the solenoid valve 88 and the switching pulse (f) at the solenoid valve 89 are shown.
The diagrams a to f are shown the same as the diagrams in FIGS. 5 and 6.
時点t1において両電磁弁88,89が入力されて閉じら
れ、時点tNにおけるカム吐出行程の開始と共に分配形噴
射ポンプ82のポンプ作業室における圧力pが上昇する
(第9図のb参照)。ノズル開放圧pDの超過後にノ
ズルニードルがノズル開口から持ち上がり、前噴射が始
まる。Both solenoid valves 88 and 89 are closed is input at time t 1, the pressure p in the pump working chamber of the distributor-type injection pump 82 is increased with the start of the cam discharge stroke at time t N (see b of FIG. 9) . Nozzle needle after excess of the nozzle opening pressure p D is lifted from the nozzle opening, before the injection begins.
時点t2において小さな弁開口横断面を備えた電磁弁8
が遮断される。電磁弁88の開放運動中、分配形噴射ポン
プ82のポンプ作業室における圧力pは迅速に降下する。
圧力降下は弁行程の終了後に遅くなる。Electromagnetic valve with a small valve opening cross section at time t 2 8
Is shut off. During the opening movement of the solenoid valve 88, the pressure p in the pump working chamber of the dispensing injection pump 82 drops quickly.
The pressure drop slows after the end of the valve stroke.
時点t3において電磁弁88は再び励磁されて閉鎖する。
ポンプ作業室における吐出圧pが上昇し、ノズルニード
ル開放圧ppDの超過後に主噴射が始まる。Solenoid valve 88 at time t 3 is closed is again energized.
Discharge pressure p rises in the pump work chamber, the main injection after the excess of the nozzle needle opening pressure pp D begins.
時点t4において両電磁弁88,89が遮断されて開放され
る。吐出圧pの圧力降下制御のためにいまや大きな流過
横断面が利用される。吐出圧は急激に低下し、噴射ノズ
ル85のノズルニードルは戻ってノズル開口を閉鎖し、こ
れによって主噴射が終了する。Both solenoid valves 88 and 89 is opened is cut off at time t 4. A large flow cross section is now used for pressure drop control of the discharge pressure p. The discharge pressure drops sharply, the nozzle needle of the injection nozzle 85 returns and closes the nozzle opening, thereby ending the main injection.
第1図はディーゼル機関のための燃料噴射装置を部分的
に示す図、第2図、第3図及び第4図は第1図に示され
た燃料噴射装置の電磁式の弁装置の異なった3つの実施
例を示す図、第5図及び第6図は、第1図及び第2図も
しくは第1図及び第4図に示された燃料噴射装置におけ
る種々異なったパラメータの時間的な経過を示す線図、
第7図は第1図に示された燃料噴射装置の弁装置のため
の切換え信号発信器のブロック回路図、第8図は別の実
施例による燃料噴射装置を示す概略図、第9図は第8図
に示された燃料噴射装置における種々異なったパラメー
タの時間的な経過を示す線図である。 10……噴射ノズル、11……噴射導管、12……接続管片、
13……分配形噴射ポンプ、14……ケーシング、15……バ
レル、16……プランジャ、17……カム駆動装置、18……
軸、19……ポンプ作業室、20……供給通路、21……吸込
み室、22……中心孔、23……分配孔、24……吐出孔、25
……縦溝、26……フィードポンプ、27……燃料タンク、
28……調圧弁、29……戻し導管、30,30′,30″……弁装
置、31……接続端子、32……切換え信号発信器、33……
流入孔、34……放圧通路、35……弁ケーシング、36……
電磁弁、37……調節マグネット、38,39……コア、40,41
……マグネットコイル、42,43……プレート、44,45……
可動子、46,47……空隙、48,49……ガイドブシュ、50…
…弁部材、51,51′,51″……調節ピストン、52……弁開
放ばね、53……戻しばね、54……弁座、55……弁開口、
56……弁座体、57……中空体、58……流出孔、59……環
状室、60……接続孔、61,62……ストッパ、63……緩衝
突き棒、64……支持プレート、65……緩衝ばね、66,67
……ピストン区分、68……ピストンばね、69……ストッ
パ肩部、70,71……計算器、72……センサ、73……比較
器、74……電流調整器、80……燃料タンク、81……フィ
ードポンプ、82……分配形噴射ポンプ、83……戻し導
管、84……噴射導管、85……噴射ノズル、86……放圧導
管、87……弁装置、88,89……電磁弁、90,91……マグネ
ットコイルFIG. 1 is a partial view of a fuel injection device for a diesel engine, and FIGS. 2, 3, and 4 show different types of electromagnetic valve devices of the fuel injection device shown in FIG. FIGS. 5 and 6 show three embodiments, which show the time course of different parameters in the fuel injection system shown in FIGS. 1 and 2 or FIGS. 1 and 4. FIG. Diagram,
FIG. 7 is a block circuit diagram of a switching signal transmitter for the valve device of the fuel injection device shown in FIG. 1, FIG. 8 is a schematic diagram showing a fuel injection device according to another embodiment, and FIG. FIG. 9 is a diagram showing the time course of various parameters in the fuel injection device shown in FIG. 8; 10 ... injection nozzle, 11 ... injection conduit, 12 ... connecting pipe piece,
13 ... distributing type injection pump, 14 ... casing, 15 ... barrel, 16 ... plunger, 17 ... cam drive device, 18 ...
Shaft, 19: Pump working chamber, 20: Supply passage, 21: Suction chamber, 22: Center hole, 23: Distributing hole, 24: Discharge hole, 25
…… Vertical groove, 26 …… Feed pump, 27 …… Fuel tank,
28 ... pressure regulating valve, 29 ... return conduit, 30, 30 ', 30 "... valve device, 31 ... connection terminal, 32 ... switching signal transmitter, 33 ...
Inlet, 34 …… Pressure release passage, 35 …… Valve casing, 36 ……
Solenoid valve, 37 Adjustment magnet, 38, 39 Core, 40, 41
…… Magnet coil, 42,43 …… Plate, 44,45 ……
Movable element, 46,47 …… Gap, 48,49 …… Guide bush, 50…
... Valve member, 51, 51 ', 51 "... Adjusting piston, 52 ... Valve opening spring, 53 ... Return spring, 54 ... Valve seat, 55 ... Valve opening,
56 ... valve seat, 57 ... hollow body, 58 ... outlet hole, 59 ... annular chamber, 60 ... connection hole, 61, 62 ... stopper, 63 ... buffer rod, 64 ... support plate , 65 ... cushioning spring, 66, 67
…… Piston section, 68… Piston spring, 69… Stopper shoulder, 70,71… Calculator, 72… Sensor, 73… Comparator, 74… Current regulator, 80… Fuel tank, 81… Feed pump, 82… Distribution type injection pump, 83 …… Return conduit, 84 …… Injection conduit, 85 …… Injection nozzle, 86 …… Pressure release conduit, 87 …… Valve device, 88,89 …… Solenoid valve, 90,91 ... Magnet coil
───────────────────────────────────────────────────── フロントページの続き (72)発明者 ヴアルター・テーゲン ドイツ連邦共和国ヴアイプリンゲン7・ イム・ライスガー 4 (56)参考文献 特開 昭60−125754(JP,A) ──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Walter Tegen Vaipuringen 7, Im Reisgar 4 Germany (56) References JP-A-60-125754 (JP, A)
Claims (11)
の噴射ノズルと、連続的に各噴射ノズルに燃料噴射量を
吐出する分配形噴射ポンプとが設けられていて、この場
合噴射量が相前後して噴射される前噴射量と主噴射量と
に分けられるようになっており、さらに、分配形噴射ポ
ンプのポンプ作業室と放圧導管との間を開閉制御する電
磁制御式の弁装置が設けられていて、該弁装置が、前噴
射時及び主噴射時にはポンプ作業室を放圧導管に対して
閉鎖し、吐出終了時における圧力降下制御のためには放
圧導管への所定の流過横断面を開制御する形式のものに
おいて、弁装置(30;30′;30″;87)の流過横断面が少
なくとも2つの段階に調節可能に構成されており、弁装
置(30;30′;30″;87)が吐出時間中に、吐出終了時に
完全に開放される流過横断面に比べて減じられた流過横
断面を短時間開制御するように構成されていることを特
徴とする、内燃機関用の燃料噴射装置。1. A fuel injection device for an internal combustion engine, comprising: a plurality of injection nozzles; and a distribution type injection pump for continuously discharging a fuel injection amount to each of the injection nozzles. Are divided into a pre-injection amount and a main injection amount that are injected one after another, and furthermore, an electromagnetic control type that controls opening and closing between a pump working chamber of a distribution type injection pump and a pressure relief conduit. A valve device is provided, which closes the pump working chamber with the pressure relief conduit during pre-injection and main injection and provides a predetermined pressure to the pressure relief conduit for pressure drop control at the end of discharge. Of the valve device (30; 30 '; 30 "; 87), wherein the flow cross section of the valve device (30; 30';30"; 87) is adjustable in at least two stages. ; 30 '; 30 "; 87) is a flow cross section that is completely opened at the end of discharge during the discharge time A fuel injection device for an internal combustion engine, characterized in that it is configured to open-control a flow passage cross section reduced in a short time as compared with the above.
を取り囲んでいる弁座(54)と該弁座と協働する軸方向
移動可能な弁部材(50)とを備えていて分配形噴射ポン
プ(13)のポンプ作業室(19)と放圧導管(34)との間
に配置された電磁弁(36)と、弁部材(50)の移動距離
を少なくとも2つの異なった大きさの行程距離(h1,
h2)に調節するための制御可能なストッパ(51)とを有
しており、該ストッパ(51)が、分配形噴射ポンプ(1
5)の吐出時間中には弁部材(50)の小さな行程距離(h
2)がかつ吐出終了時には大きな行程距離(h1)が調節
されるように、制御されている、特許請求の範囲第1項
記載の燃料噴射装置。2. The valve device (30; 30 '; 30 ") having a valve opening (55).
A pump working chamber (19) of a dispensing injection pump (13) and a pressure relief conduit, comprising a valve seat (54) surrounding the valve seat and an axially movable valve member (50) cooperating therewith. (34) and a moving distance of the valve member (50) by at least two different stroke distances (h 1 ,
h 2) has a controllable stop for adjusting (51), the said stopper (51) is distributed type injection pump (1
During the discharge time of 5), the small stroke distance (h) of the valve member (50)
2) and such a large stroke distance at the discharge ends (h 1) is adjusted and controlled, the fuel injection device as set forth in claim 1, wherein the appended claims.
ト(37)の可動子(45)と連結されている、特許請求の
範囲第2項記載の燃料噴射装置。3. The fuel injection device according to claim 2, wherein the controllable stopper (51) is connected to the mover (45) of the adjusting magnet (37).
電磁弁(36)の可動子(44)に接触していて、該可動子
が電磁弁(36)の電磁石(40)の給電時に、弁部材(5
0)の大きな行程距離(h1)に相当する調節距離だけ進
むようになっており、ストッパを形成している移動可能
な調節ピストン(51)が戻しばね(53)を用いて調節マ
グネット(37)の可動子(45)に接触していて、該可動
子が調節マグネット(37)の給電時に規定された調節距
離(ha)だけ進むようになっており、調節ピストン(5
1)が電磁弁(36)の可動子(44)を貫いて弁部材(5
0)の弁閉鎖運動方向で該弁部材に係合するようになっ
ており、調節ピストン(51)の規定された調節距離
(ha)が弁部材(50)の大きな行程距離(h1)と小さな
行程距離(h2)との間の差に等しく設定されている、特
許請求の範囲第3項記載の燃料噴射装置。4. A valve member (50) is in contact with a movable element (44) of a solenoid valve (36) using a valve opening spring (52), and the movable element is connected to an electromagnet (40) of the solenoid valve (36). ), The valve member (5
The movable adjustment piston (51) forming a stopper is moved by an adjustment distance corresponding to a large stroke distance (h 1 ) of the adjustment magnet (37) using a return spring (53). ) in contact to the movable member (45), the movable element has so advanced by adjustment path defined during feeding the adjusting magnet (37) (h a), adjusting piston (5
1) penetrates the mover (44) of the solenoid valve (36) and the valve member (5)
A valve closing motion direction of 0) is adapted to engage the valve member, a defined adjustment path of the adjusting piston (51) (h a) the valve large stroke distance member (50) (h 1) a small stroke distance (h 2) the difference equally set, patent fuel injectors ranging third claim of claim between.
調節ピストンの全長を越えて延在している緩衝突き棒
(63)が軸方向移動可能に案内されており、該緩衝突き
棒がケーシング側に支持された緩衝ばね(65)の作用下
で調節ピストン(51′)の一方の端部に接触していて、
この位置において弁部材(50)に向けられた他方の端部
が規定の値だけ突出しており、緩衝ばね(65)のばね力
が弁開放ばね(52)のばね力よりも小さく設定されてい
る、特許請求の範囲第4項記載の燃料噴射装置。5. Inside the adjusting piston (51 '), a damping rod (63) extending over the entire length of the adjusting piston is guided so as to be movable in the axial direction. Contacting one end of the adjusting piston (51 ') under the action of a buffer spring (65) supported on the casing side,
In this position, the other end facing the valve member (50) projects by a predetermined value, and the spring force of the buffer spring (65) is set to be smaller than the spring force of the valve opening spring (52). The fuel injection device according to claim 4, wherein:
分(66)と第2のピストン区分(67)とに分割されてい
て、両ピストン区分(66,67)の間には該ピストン区分
に支持されたピストンばね(68)が配置されていて、該
ピストンのばねのばね力が弁開放ばね(52)のばね力よ
りも大きく設定されており、ピストンばね(68)を用い
て第1のピストン区分(66)が調節マグネット(37)の
可動子(45)にかつ第2のピストン区分(67)が弁部材
(50)の方向でケーシングに対して不動のストッパ肩部
(69)に接触しており、調節マグネット(37)の給電時
に第2のピストン区分(67)が第1のピストン区分(6
6)によってストッパ肩部(69)に固定されている、特
許請求の範囲第4項記載の燃料噴射装置。6. An adjusting piston (51 ") is divided into a first piston section (66) and a second piston section (67), said piston section being located between said piston sections (66, 67). A piston spring (68) supported by the section is disposed, and the spring force of the piston spring is set to be greater than the spring force of the valve opening spring (52). The first piston section (66) is on the armature (45) of the adjusting magnet (37) and the second piston section (67) is on the stopper shoulder (69) immovable with respect to the casing in the direction of the valve member (50). The second piston section (67) is in contact with the first piston section (6) when the adjusting magnet (37) is energized.
5. The fuel injection device according to claim 4, wherein the fuel injection device is fixed to the stopper shoulder (69) by 6).
吐出開始時における電磁弁(36)の第1の閉鎖と共に入
力され、吐出時間中における電磁弁(36)の第2の閉鎖
と共に再び遮断される、特許請求の範囲第3項から第6
項までのいずれか1項記載の燃料噴射装置。7. An exciting current is input to the adjusting magnet (87) together with the first closing of the solenoid valve (36) at the start of discharge, and is shut off again with the second closing of the solenoid valve (36) during the discharging time. Claims 3 to 6
The fuel injection device according to any one of the preceding items.
鎖のために入力され、開放のためには遮断されるように
なっており、励磁電流(i)が閉鎖後に保持電流
(iH1)にまで減じられ、開放後に迅速に消滅させられ
て再び保持電流(iH2)にまで持ち上げられるようにな
っている、特許請求の範囲第3項から第7項までのいず
れか1項記載の燃料噴射装置。8. An exciting current (i) for the solenoid valve (36) is input for closing and is cut off for opening, and the exciting current (i) is maintained after closing. 8. The method according to claim 3, wherein the current is reduced to (i H1 ), is quickly extinguished after opening, and is raised again to the holding current (i H2 ). Item 13. The fuel injection device according to Item 1.
つの電磁弁(88,89)を有しており、両電磁弁の弁開口
が異なった開口横断面を有していて、それぞれ分配形噴
射ポンプ(82)のポンプ作業室を放圧導管(86)と接続
しており、横断面の小さな弁開口を備えた電磁弁(88)
が吐出時間中に短時間開放され、少なくとも横断面の大
きな弁開口を備えた電磁弁(89)が吐出終了時に開放さ
れるようになっている、特許請求の範囲第1項記載の燃
料噴射装置。9. A two-piece valve device (87) connected in parallel with each other.
Two solenoid valves (88, 89), the valve openings of both solenoid valves having different opening cross sections, each of which connects the pump working chamber of the dispensing injection pump (82) with a pressure relief conduit (86). ) And a solenoid valve with a small cross-section valve opening (88)
2. The fuel injection device according to claim 1, wherein the valve is opened for a short time during the discharge time, and a solenoid valve (89) having a valve opening having at least a large cross section is opened at the end of the discharge. .
のための制御信号(φm)が記憶された特性線領域から
導き出されており、該特性線領域が制御信号(φm)を
内燃機関の回転数(n)及び負荷(α)、燃料温度
(T)並びに基準マーク(BZ)に関連して生ぜしめる、
特許請求の範囲第1項から第9項までのいずれか1項記
載の燃料噴射装置。10. A control signal (φ m ) for inputting and shutting off the valve device (30; 30 ′; 30 ″) is derived from a stored characteristic line region, and the characteristic line region corresponds to the control signal (φ m ). φ m ) in relation to the speed (n) and load (α) of the internal combustion engine, the fuel temperature (T) and the reference mark (BZ).
The fuel injection device according to any one of claims 1 to 9, wherein:
線領域において内燃機関の回転数(n)及び負荷
(α)、燃料温度(T)並びに基準マーク(BZ)の関数
として記憶されており、ノズルニードル行程(hD)の実
際値がセンサ(72)によってとらえられるようになって
おり、ノズルニードル行程(hD)の実際の経過と特性線
領域から取り出されたノズルニードル行程(hD)の経過
との間の調整誤差によって、特性線領域から取り出され
た制御信号(φm)が修正されるようになっている、特
許請求の範囲第10項記載の燃料噴射装置。11. The course of the nozzle needle stroke (h D ) is stored as a function of the engine speed (n) and load (α), the fuel temperature (T) and the reference mark (BZ) in the characteristic line range. cage, the nozzle needle stroke (h D) of the actual value are adapted to be captured by the sensor (72), the nozzle needle stroke (h D) of the actual elapsed and the nozzle needle stroke taken from the characteristic line region (h 11. The fuel injection device according to claim 10, wherein the control signal ([phi] m ) extracted from the characteristic line region is modified by an adjustment error during the course of D ).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3601710A DE3601710C2 (en) | 1986-01-22 | 1986-01-22 | Fuel injection device for internal combustion engines |
DE3601710.8 | 1986-01-22 |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS62170766A JPS62170766A (en) | 1987-07-27 |
JP2587047B2 true JP2587047B2 (en) | 1997-03-05 |
Family
ID=6292319
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP62011506A Expired - Lifetime JP2587047B2 (en) | 1986-01-22 | 1987-01-22 | Fuel injection device for internal combustion engines |
Country Status (2)
Country | Link |
---|---|
JP (1) | JP2587047B2 (en) |
DE (1) | DE3601710C2 (en) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3735750A1 (en) * | 1987-10-22 | 1989-05-03 | Kloeckner Humboldt Deutz Ag | Fuel injection device |
DE4018320C2 (en) * | 1990-06-08 | 2002-06-27 | Bosch Gmbh Robert | Control circuit for an electromagnetic consumer |
US5325837A (en) * | 1992-11-19 | 1994-07-05 | Robert Bosch Gmbh | Fuel injection apparatus for internal combustion engines |
JPH0777124A (en) * | 1993-09-09 | 1995-03-20 | Zexel Corp | Pilot injection controller |
JPH07145750A (en) * | 1993-11-25 | 1995-06-06 | Zexel Corp | Fuel injection control device |
DE4415826C2 (en) * | 1994-05-05 | 2000-07-13 | Deutz Ag | Air compressing internal combustion engine |
WO1997001031A1 (en) * | 1995-06-23 | 1997-01-09 | Diesel Technology Company | Fuel pump and method of operating same |
DE19639117A1 (en) * | 1996-09-24 | 1998-03-26 | Bosch Gmbh Robert | Fuel injector |
DE19801169C1 (en) * | 1998-01-15 | 1999-08-12 | Daimler Chrysler Ag | Fuel injection system for internal combustion engines |
JP2005307747A (en) * | 2004-04-16 | 2005-11-04 | Mitsubishi Electric Corp | Fuel supply device for internal combustion engine |
DE102017201581A1 (en) * | 2017-02-01 | 2018-08-02 | Robert Bosch Gmbh | Solenoid valve arrangement for a fuel injector for injecting liquid and / or gaseous fuel |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4579096A (en) * | 1983-12-08 | 1986-04-01 | Toyota Jidosha Kabushiki Kaisha | Diesel fuel injection pump with electromagnetic fuel spilling valve having pilot valve providing high responsiveness |
JPS60125754A (en) * | 1983-12-08 | 1985-07-05 | Toyota Motor Corp | Fuel injection pump for use in diesel engine |
-
1986
- 1986-01-22 DE DE3601710A patent/DE3601710C2/en not_active Expired - Fee Related
-
1987
- 1987-01-22 JP JP62011506A patent/JP2587047B2/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
DE3601710A1 (en) | 1987-07-23 |
JPS62170766A (en) | 1987-07-27 |
DE3601710C2 (en) | 1998-07-02 |
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