EP0638707A1 - Brennkraftmaschine - Google Patents

Brennkraftmaschine Download PDF

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Publication number
EP0638707A1
EP0638707A1 EP94112110A EP94112110A EP0638707A1 EP 0638707 A1 EP0638707 A1 EP 0638707A1 EP 94112110 A EP94112110 A EP 94112110A EP 94112110 A EP94112110 A EP 94112110A EP 0638707 A1 EP0638707 A1 EP 0638707A1
Authority
EP
European Patent Office
Prior art keywords
exhaust
oil passage
engine
actuated
cylinder
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
Application number
EP94112110A
Other languages
English (en)
French (fr)
Other versions
EP0638707B1 (de
Inventor
Isao C/O Hino Jidosha Joko
Toshiaki C/O Hino Jidosha Kogyo K.K. Kakegawa
Seiji C/O Hino Jidosha Shundo
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hino Motors Ltd
Original Assignee
Hino Motors Ltd
Hino Jidosha Kogyo KK
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hino Motors Ltd, Hino Jidosha Kogyo KK filed Critical Hino Motors Ltd
Publication of EP0638707A1 publication Critical patent/EP0638707A1/de
Application granted granted Critical
Publication of EP0638707B1 publication Critical patent/EP0638707B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F01L13/065—Compression release engine retarders of the "Jacobs Manufacturing" type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0273—Multiple actuations of a valve within an engine cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/04—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation using engine as brake
    • 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/01—Internal exhaust gas recirculation, i.e. wherein the residual exhaust gases are trapped in the cylinder or pushed back from the intake or the exhaust manifold into the combustion chamber without the use of additional passages
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the present invention relates to an internal combustion engine in which a compression engine brake device, which serves during engine braking to ensure a braking force by opening an exhaust valve of a cylinder near a top dead center in a compression stroke to discharge the compressed air, is utilized for exhaust gas recirculation.
  • a master piston 2 for a cylinder 7 is actuated by a rocker arm 19 which in turn is actuated by a push rod 1 of another cylinder (not shown) to pressurize an oil having been supplied to an oil passage 5 from a rocker shaft bracket through solenoid and control valves 3 and 4. Due to the hydraulic pressure thus produced, an exhaust valve 8 of the cylinder 7 near a top dead center is opened via a slave piston 6 to discharge the compressed air through an exhaust port 9. As a result, force for pushing down the piston is prevented from generating and a braking force obtained in the compression stroke is effectively utilized with no loss.
  • An internal combustion engine having a conventional engine brake device described above may be effective for engine braking, but cannot attain recirculation of exhaust gases, failing to make improvement on the problems of NO x and of white smoke at engine starting. Particularly in a turbo-intercooled engine, exhaust gas recirculation is difficult to carry out.
  • the present invention is directed to an internal combustion engine wherein during engine braking, a master piston for a cylinder is actuated by a rocker arm which in turn is actuated by a push rod of another cylinder to pressurize an oil having been supplied to an oil passage, an exhaust valve of the one cylinder near a top dead center in a compression stroke being opened through a slave piston by the hydraulic pressure thus produced to discharge the compressed air through an exhaust port, characterized in that in addition to said engine-braking master piston actuated by the rocker arm which in turn is actuated by the push rod, an exhaust-gas-recirculation master piston is provided which is actuated by a rocker arm which in turn is actuated by a push rod of said another cylinder to open the exhaust valve in a suction stroke, thereby pressurizing said oil having been supplied to said oil passage, and that an oil passage selector valve is provided which selectively switches over the hydraulic pressures produced by said master pistons to said oil passage.
  • engine braking and exhaust gas recirculation can be selectively effected by switching over the hydraulic pressures produced by the engine-braking and exhaust-gas-recirculation master pistons by means of the oil passage selector valve.
  • reference numeral 5 represents an oil passage to which oil is supplied from a rocker shaft bracket through solenoid and control valves 3 and 4; 6, a slave piston which opens an exhaust valve 8 of a cylinder 7 depending upon pressure in the oil passage 5; and 10, an exhaust brake valve.
  • Reference numerals 1a and 1b designate inlet and exhaust push rods of another cylinder, respectively; and 2a and 2b, engine-braking and exhaust-gas-recirculation master pistons actuated by rocker arms 19a and 19b which in turn are actuated by the inlet and exhaust push rods 1a and 1b, respectively.
  • the master pistons 2a and 2b when actuated, pressurize the oil which has been supplied to the oil passage 5 of the cylinder 7.
  • Reference numeral 11 represents an oil passage selector valve which selectively switches over the hydraulic pressures produced by the master pistons 2a and 2b to the oil passage 5.
  • the selector valve 11 comprises a spool valve shaft 12 with a spool 12a for selectively communicating and cutting off an oil passage 5a for the engine-braking master piston 2a with and from the oil passage 5, a spool 12b for selectively communicating and cutting off an oil passage 5b for the exhaust-gas-recirculation master piston 2b with and from the oil passage 5 and a piston 12c.
  • a switching mechanism for the oil passage selector valve 11 is constructed such that a spring 14 is loaded on one end of the spool valve shaft 12, a pressure source being connected through an electromagnetic selector valve 16 to a chamber 15 on a top surface of the piston 12c at the other end of the shaft 12. Switching of the selector valve 16 causes the shaft 12 to be axially displaced for selective opening and closing of the passages 5a and 5b.
  • Reference numerals 13a and 13b represent discharge passages.
  • Fig. 2 exemplarily shows an application of the above embodiment to an in-line 6-cylindered engine where the exhaust valves 8 of the first, second and third cylinders #1(7), #2 and #3 are opening-controlled by the inlet and exhaust push rods 1a and 1b of the second, third and first cylinders #2, #3 and #1(7), respectively.
  • the engine-braking master piston 2a is actuated by the inlet push rod 1a of the second cylinder #2 in a suction stroke to pressurize the oil having been supplied to the oil passage 5 from the rocker shaft bracket through the solenoid and control valves 3 and 4. Due to the hydraulic pressure thus produced, the exhaust valve 8 of the cylinder 7 (the first cylinder #1) in an expansion stroke is opened through the slave piston 6 to discharge the compressed air through the exhaust port 9. As a result, force for pushing down the piston is prevented from generating and the braking force is effectively utilized with no loss.
  • EGR exhaust gas recirculation
  • the selector valve 16 is so switched that the pressure oil in the chamber 15 is discharged by resilient force of the spring 14.
  • the oil passage selector valve 11 is so switched that the oil passage 5a for the engine-braking master piston 2a is closed while the oil passage 5b for the exhaust-gas-recirculation master piston 2b is communicated with the oil passage 5.
  • the exhaust-gas-recirculation master piston 2b is actuated by the exhaust push rod 1b of the second cylinder #2 in exhaust stroke to pressurize the oil having been supplied to the oil passage 5 from the rocker shaft bracket through the solenoid and control valves 3 and 4. Due to the hydraulic pressure thus produced, the exhaust valve 8 of the cylinder 7 (the first cylinder #1) is opened at the end of the suction stroke via the slave piston 6.
  • the second cylinder #2 being in exhaust stroke and having high pressure in its exhaust pipe, part of the exhaust gases in the second cylinder #2 flow back to the cylinder 7 (the first cylinder #1) due to the pressure difference.
  • the exhaust gas recirculation is effected to reduce NO x and improves the problem of white smoke at engine starting.
  • This EGR is effective for turbo-intercooled engines in which exhaust manifold pressure pulsation owing to exhaust strokes of each cylinder is high.
  • Valve lift is shown in the order of ignition #1, #4, #2, #6, #3 and #5.
  • the exhaust valve of the first cylinder #1 is opening-controlled by the exhaust push rod of the second cylinder #2 and is opened near bottom dead center (BDC) of the first cylinder #1 to effect the exhaust gas recirculation (EGR).
  • the exhaust valve of the first cylinder #1 is opened near top dead center (TDC) in the compression stroke of the first cylinder #1 by means of the inlet push rod of the second cylinder #2 to discharge the compressed air.
  • BDC bottom dead center
  • TDC top dead center
  • Exhaust gas recirculation may be also effected during engine starting for the purpose of air warming.
  • Fig. 4 shows a further embodiment of the present invention where the same component as in Fig. 1 is referred to by the same reference numeral as in Fig. 1 and basic arrangement is the same as in Fig. 1.
  • the casing which forms the oil passage selector valve 11 is extended at its end and the spool valve shaft 12 is extended at its end closer to the spool 12a to have a piston 12d at its tip.
  • a chamber 15' Formed on a top surface of the piston 12d is a chamber 15' to which a pressure source is connected through an electromagnetic selector valve 16'.
  • EGR exhaust gas recirculation
  • the selector valve 16' is switched over to supply the pressure oil to the chamber 15' and the selector valve 16 is switched over to discharge the pressure oil in the chamber 15.
  • the oil passage selector valve 11 is so switched that the oil passage 5a for the engine-braking master piston 2a is closed while the oil passage 5b for the exhaust-gas-recirculation master piston 2b is communicated with the oil passage 5.
  • Fig. 5 shows a pattern of driving in the embodiment of Fig. 4.
  • the extent of pressing the accelerator pedal is detected by an accelerator sensor under the following three conditions: idling state (OFF) with the accelerator pedal being not pressed at all, low to moderate loading condition (ON; mild) with the accelerator pedal being pressed to some extent and high loading condition (ON; high) with the acceleration pedal being pressed strongly.
  • the oil passage selector valve 11 is switched over to EGR mode regardless of the extent at which the accelerator pedal is pressed. EGR is effected only when the engine is neither in idling nor in high loading condition, i.e., only when it is in the low to moderate loading condition. Engine braking by opening the exhaust valve 8 is not effected.
  • Figs. 6 and 7 shows an arrangement for eliminating such possible confusion in which a control signal 18 for switching over the solenoid valve 3 to relieve the pressure in the oil passage 5 is outputted from a controller 17 to the solenoid valve 3 when the condition of the driver's foot being detached from the accelerator pedal is changed into the low to moderate loading condition with the accelerator pedal being pressed to some extent, i.e., when the condition with the exhaust valve 8 being opened to effect engine braking is changed into the condition where engine braking mode is released and switched over to EGR mode.
  • the engine braking mode can be quickly switched over into the EGR mode to eliminate the driver's confusion by arranging such that the control signal 18 is outputted from the controller 17 to the solenoid valve 3 so as to switch over the solenoid valve 3 to relieve the pressure in the oil passage 5 when the condition of the driver's foot being detached from the accelerator pedal is changed into the low to moderate loading condition with the accelerator pedal being pressed to some extent, i.e., when the condition of the exhaust valve 8 being opened to effect engine braking is released and switched over to EGR mode.
  • an internal combustion engine of the present invention which has a compression engine brake device adapted to ensure a braking force by opening an exhaust valve of a cylinder near a top dead center in a compression stroke to discharge the compressed air
  • an oil passage selector valve is arranged for selectively switching over the hydraulic pressures produced by the engine-braking and exhaust-gas-recirculation master pistons. Therefore, in addition to engine braking, exhaust gas recirculation can be effected. Reduction of NO x and improvement of the problem of white smoke at engine starting are attained.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Valve Device For Special Equipments (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
EP94112110A 1993-08-04 1994-08-03 Brennkraftmaschine Expired - Lifetime EP0638707B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP211050/93 1993-08-04
JP21105093 1993-08-04
JP108406/94 1994-05-23
JP6108406A JP2872570B2 (ja) 1993-08-04 1994-05-23 内燃機関

Publications (2)

Publication Number Publication Date
EP0638707A1 true EP0638707A1 (de) 1995-02-15
EP0638707B1 EP0638707B1 (de) 1997-02-12

Family

ID=26448288

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94112110A Expired - Lifetime EP0638707B1 (de) 1993-08-04 1994-08-03 Brennkraftmaschine

Country Status (3)

Country Link
EP (1) EP0638707B1 (de)
JP (1) JP2872570B2 (de)
DE (1) DE69401729T2 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5794589A (en) * 1995-11-24 1998-08-18 Ab Volvo Exhaust valve mechanism in an internal combustion engine
EP1013913A1 (de) * 1997-01-29 2000-06-28 Hino Jidosha Kogyo Kabushiki Kaisha Abgasrückführungsvorrichtung
CN110998072A (zh) * 2017-08-03 2020-04-10 雅各布斯车辆系统公司 用于增强式内燃机制动中的逆流管理和阀运动排序的系统及方法
CN111212960A (zh) * 2017-10-13 2020-05-29 戴姆勒股份公司 用于机动车内燃机的气门传动机构

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6302084B1 (en) 1998-04-14 2001-10-16 Hitachi, Ltd. Method of controlling throttle valve of engine and controller
KR101865738B1 (ko) * 2016-12-09 2018-07-04 현대자동차 주식회사 가변 밸브 리프트 장치
JP2021025495A (ja) * 2019-08-07 2021-02-22 日野自動車株式会社 エンジンシステム
KR20210041332A (ko) 2019-10-07 2021-04-15 현대자동차주식회사 압축 완화형 엔진 브레이크의 소켓모듈 및 이를 이용한 엔진 브레이크의 작동 방법

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1269428A (fr) * 1960-08-18 1961-08-11 Système d'entraînement et de freinage pour véhicules
EP0167267A1 (de) * 1984-06-01 1986-01-08 The Jacobs Manufacturing Company Verfahren und System zur Motorbremsung durch Entspannung komprimierter Luft
US4936273A (en) * 1989-04-28 1990-06-26 Myers Vaughn D Decompression system for diesel engines

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1269428A (fr) * 1960-08-18 1961-08-11 Système d'entraînement et de freinage pour véhicules
EP0167267A1 (de) * 1984-06-01 1986-01-08 The Jacobs Manufacturing Company Verfahren und System zur Motorbremsung durch Entspannung komprimierter Luft
US4936273A (en) * 1989-04-28 1990-06-26 Myers Vaughn D Decompression system for diesel engines

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5794589A (en) * 1995-11-24 1998-08-18 Ab Volvo Exhaust valve mechanism in an internal combustion engine
EP1013913A1 (de) * 1997-01-29 2000-06-28 Hino Jidosha Kogyo Kabushiki Kaisha Abgasrückführungsvorrichtung
EP1013913A4 (de) * 1997-01-29 2003-05-07 Hino Motors Ltd Abgasrückführungsvorrichtung
CN110998072A (zh) * 2017-08-03 2020-04-10 雅各布斯车辆系统公司 用于增强式内燃机制动中的逆流管理和阀运动排序的系统及方法
CN110998072B (zh) * 2017-08-03 2021-11-09 雅各布斯车辆系统公司 用于增强式内燃机制动中的逆流管理和阀运动排序的系统及方法
CN111212960A (zh) * 2017-10-13 2020-05-29 戴姆勒股份公司 用于机动车内燃机的气门传动机构

Also Published As

Publication number Publication date
JPH0797959A (ja) 1995-04-11
EP0638707B1 (de) 1997-02-12
DE69401729T2 (de) 1997-08-21
JP2872570B2 (ja) 1999-03-17
DE69401729D1 (de) 1997-03-27

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