WO1992009792A1 - Internal combustion engine with compressor function - Google Patents

Internal combustion engine with compressor function Download PDF

Info

Publication number
WO1992009792A1
WO1992009792A1 PCT/SE1991/000791 SE9100791W WO9209792A1 WO 1992009792 A1 WO1992009792 A1 WO 1992009792A1 SE 9100791 W SE9100791 W SE 9100791W WO 9209792 A1 WO9209792 A1 WO 9209792A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
valve
internal combustion
combustion engine
extra
Prior art date
Application number
PCT/SE1991/000791
Other languages
French (fr)
Inventor
Mats SABELSTRÖM
Lars Tenglud
Original Assignee
Ab Volvo
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
Priority to US08/064,135 priority Critical patent/US5315974A/en
Application filed by Ab Volvo filed Critical Ab Volvo
Priority to DE69110054T priority patent/DE69110054T2/en
Priority to EP91920619A priority patent/EP0558585B1/en
Priority to JP50010292A priority patent/JP3326173B2/en
Publication of WO1992009792A1 publication Critical patent/WO1992009792A1/en

Links

Classifications

    • 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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0696—W-piston bowl, i.e. the combustion space having a central projection pointing towards the cylinder head and the surrounding wall being inclined towards the cylinder wall
    • 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
    • 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
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • 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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0645—Details related to the fuel injector or the fuel spray
    • F02B23/066—Details related to the fuel injector or the fuel spray the injector being located substantially off-set from the cylinder centre axis
    • 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
    • F02D13/06—Cutting-out cylinders
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/14—Direct injection into combustion chamber
    • 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
    • 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
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to an internal combustion engine with compressor function comprising, in addition to intake and exhaust valves for each cylinder, an extra exhaust valve in at least one cylinder, which extra exhaust valve, in its open position, puts the cylinder chamber in communication with valve means containing an exhaust duct and disposed to permit exhausting of intake air to a pneumatic system but prevent intake of air to the cylinder chamber via said ex ⁇ haust duct.
  • Such a compressor arrangement can, inter alia, be designed to supplement the ordinary air compressor, which normally supplies the vehicle pneumatic system, when the capacity of this normal compressor for some reason is not
  • a diesel engine with compressor function of the above-mentio ⁇ ned type is shown and described in US-A-2 005 536.
  • the engine 25 is provided with a mechanical injection system having a conventional multiple cylinder injection pump. Via a system of cam shafts with cams controlling shunt valves, the fuel supply to the compressor cylinder in question is interrupted at the same time as the extra exhaust valve is opened under i 30 the influence of additional cams on the cam shafts.
  • This f r known installation is complicated in its mechanical design and increases, inter alia due to the presence of the shunt valves on the high pressure side of the injection system, the susceptibility of the injection system to disruption.
  • the purpose of the present invention is to achieve an in ⁇ ternal combustion engine of the type described by way of introduction in which the supply of fuel to a cylinder ser ⁇ ving as a compressor cylinder can be interrupted without the need to supplement the engine injection system with complica ⁇ ted specially designed equipment.
  • the engine has a fuel injection system with a unit injector with an electrically operated spill valve for each cylinder and that means are arranged which can keep the spill valve of the cylinder provided with the extra exhaust valve open at the same time as the extra exhaust valve is open.
  • an elec ⁇ tronic control unit is coupled to a solenoid valve in each injector.
  • This valve determines, in response to signals from the control unit, when the injection to each cylinder is to be initiated and terminated.
  • the valve closes, the pump piston integrated in the unit injector builds up a pressure and the injection is initiated when this pressure exceeds the opening pressure of the injection nozzle.
  • the solenoid valve is opened and the pressure drops below the opening pressure of the injection nozzle. The supply of fuel to a particular cylinder can thus be entirely cut off simply by a control unit signal to open the spill valve of the associated unit injector, when the cylinder is to function as a compressor cylinder.
  • the engine is a direct injection diesel and has a piston 3 with a depression 4 forming a combustion chamber. It has a fuel injection system with so-called unit injectors 5, i.e. injectors each provided with an individually integrated piston driven by a cam shaft 6 via a rocker arm 7 and a spill valve (only in ⁇ dicated here) operated by an electrical magnet 8 for control ⁇ ling the period of injection.
  • unit injectors i.e. injectors each provided with an individually integrated piston driven by a cam shaft 6 via a rocker arm 7 and a spill valve (only in ⁇ dicated here) operated by an electrical magnet 8 for control ⁇ ling the period of injection.
  • the cylinder shown in the Figure has a bore 10 in its cylin ⁇ der head 2, in which a spindel 11 to a valve disc 12 is displaceably mounted.
  • the bore 10 has a shoulder 13.
  • a heli ⁇ cal spring 14 is tensioned between the shoulder 13 and a sleeve 15 fixed at the end of the spindel 11 and biases the valve disc 12 towards a valve seat 16 at the edge of a wide ⁇ ned portion 17 of the bore 10.
  • a duct 18 extends out through the cylinder head.
  • the control unit 20 in the Figure designates the electronic control unit of the fuel injection system, into which, in a known manner, signals are fed representing throttle opening, engine tempe ⁇ rature etc. for controlling the injection.
  • the control unit cooperates in accordance with the invention with the portion 10a of the bore 10 above the valve spindel.
  • a command represented by the arrow "a" in the Figure
  • the bore 10a above the spindel 11 is put under pressure at the same time as current to the electromagnet 8 is cut off.
  • the valve disc 12 is displaced to its open position at the same time as the spill valve 9 of the injector 5 is moved to its open position, thus returning the fuel to a return line 23 via a channel 22.
  • the command to the control unit can be given manually via a manual switch (not shown) or automatically, for example via a pressure sensor in a pneumatic system coupled to the cylinder duct 18.
  • a manual switch not shown
  • a pressure sensor in a pneumatic system coupled to the cylinder duct 18.
  • one or more cylinders can be made in the manner described above.
  • the use of an electronically controlled unit injector system makes it possible in a simple manner to engage the compressor function and to determine how many cylinders are to work as compressor at each occasion.

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)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Abstract

The invention relates to an internal combustion engine with compressor function. One or more of the cylinders of the engine has an extra exhaust valve (11, 12) in the cylinder head. The engine has a fuel injection system with electric unit injectors (5), and the control system (20) of the system cooperates with a pressure means (21) which controls the extra exhaust valve. When a cylinder is to work as a compressor, a command is sent to the control unit to cut off the supply of fuel to the cylinder at the same time as a piston element (15) connected to the extra valve is subjected to pressure to open the valve.

Description

INTERNAL COMBUSTION ENGINE WITH COMPRESSOR FUNCTION
The present invention relates to an internal combustion engine with compressor function comprising, in addition to intake and exhaust valves for each cylinder, an extra exhaust valve in at least one cylinder, which extra exhaust valve, in its open position, puts the cylinder chamber in communication with valve means containing an exhaust duct and disposed to permit exhausting of intake air to a pneumatic system but prevent intake of air to the cylinder chamber via said ex¬ haust duct.
10
It is previously known to use one or more cylinders in a diesel engine as compressor cylinders by providing the cylin¬ ders with an extra exhaust valve and equipping the injection system of the engine with devices through which the supply of
15 fuel to the cylinder serving as compressor cylinders can be interrupted. Such a compressor arrangement can, inter alia, be designed to supplement the ordinary air compressor, which normally supplies the vehicle pneumatic system, when the capacity of this normal compressor for some reason is not
20 sufficient, or alternatively it can be designed as the sole compressed air source for the vehicle.
A diesel engine with compressor function of the above-mentio¬ ned type is shown and described in US-A-2 005 536. The engine 25 is provided with a mechanical injection system having a conventional multiple cylinder injection pump. Via a system of cam shafts with cams controlling shunt valves, the fuel supply to the compressor cylinder in question is interrupted at the same time as the extra exhaust valve is opened under i 30 the influence of additional cams on the cam shafts. This f r known installation is complicated in its mechanical design and increases, inter alia due to the presence of the shunt valves on the high pressure side of the injection system, the susceptibility of the injection system to disruption. 35 The purpose of the present invention is to achieve an in¬ ternal combustion engine of the type described by way of introduction in which the supply of fuel to a cylinder ser¬ ving as a compressor cylinder can be interrupted without the need to supplement the engine injection system with complica¬ ted specially designed equipment.
This is achieved according to the invention by virtue of the fact that the engine has a fuel injection system with a unit injector with an electrically operated spill valve for each cylinder and that means are arranged which can keep the spill valve of the cylinder provided with the extra exhaust valve open at the same time as the extra exhaust valve is open.
In injection systems with electric unit injectors, an elec¬ tronic control unit is coupled to a solenoid valve in each injector. This valve determines, in response to signals from the control unit, when the injection to each cylinder is to be initiated and terminated. When the valve closes, the pump piston integrated in the unit injector builds up a pressure and the injection is initiated when this pressure exceeds the opening pressure of the injection nozzle. When the injection is to be terminated, the solenoid valve is opened and the pressure drops below the opening pressure of the injection nozzle. The supply of fuel to a particular cylinder can thus be entirely cut off simply by a control unit signal to open the spill valve of the associated unit injector, when the cylinder is to function as a compressor cylinder.
The invention is described in more detail with reference to an example shown in the accompanying drawing, where the Figure shows a cross-section through a schematically repre¬ sented cylinder with associated portion of the cylinder head in the diesel engine.
In the Figure, 1 designates a portion of a cylinder block and 2 designates a portion of a cylinder head. Details such as intake and exhaust ducts with associated valves and other details which are not directly pertinent to the invention have been left out for the sake of clarity. The engine is a direct injection diesel and has a piston 3 with a depression 4 forming a combustion chamber. It has a fuel injection system with so-called unit injectors 5, i.e. injectors each provided with an individually integrated piston driven by a cam shaft 6 via a rocker arm 7 and a spill valve (only in¬ dicated here) operated by an electrical magnet 8 for control¬ ling the period of injection.
The cylinder shown in the Figure has a bore 10 in its cylin¬ der head 2, in which a spindel 11 to a valve disc 12 is displaceably mounted. The bore 10 has a shoulder 13. A heli¬ cal spring 14 is tensioned between the shoulder 13 and a sleeve 15 fixed at the end of the spindel 11 and biases the valve disc 12 towards a valve seat 16 at the edge of a wide¬ ned portion 17 of the bore 10. From the widened portion 17 of the bore, a duct 18 extends out through the cylinder head. When the valve disc 12 has been lifted from its seat (dash and dot lines), the piston 3 during its compression stroke can press air out of the cylinder chamber to a compressed air system via the channel 18. A non-return valve 19 prevents air from being sucked in via the duct 18 when the piston begans its intake stroke.
20 in the Figure designates the electronic control unit of the fuel injection system, into which, in a known manner, signals are fed representing throttle opening, engine tempe¬ rature etc. for controlling the injection. The control unit cooperates in accordance with the invention with the portion 10a of the bore 10 above the valve spindel. When a command, represented by the arrow "a" in the Figure, is given to the control unit 20 that the cylinder is to work as a compressor, the bore 10a above the spindel 11 is put under pressure at the same time as current to the electromagnet 8 is cut off. Thus, the valve disc 12 is displaced to its open position at the same time as the spill valve 9 of the injector 5 is moved to its open position, thus returning the fuel to a return line 23 via a channel 22. The command to the control unit can be given manually via a manual switch (not shown) or automatically, for example via a pressure sensor in a pneumatic system coupled to the cylinder duct 18. In a multiple cylinder engine, one or more cylinders can be made in the manner described above. The use of an electronically controlled unit injector system makes it possible in a simple manner to engage the compressor function and to determine how many cylinders are to work as compressor at each occasion.

Claims

1. Internal combustion engine with compressor function, comprising, in addition to intake and exhaust valves for each cylinder, an extra exhaust valve in at least one cylinder, which extra exhaust valve in its open position puts the cylinder chamber in communication with valve means containing an exhaust duct and disposed to permit exhausting of intake air to a pneumatic system but prevent intake of air to the cylinder chamber via said exhaust duct, c h a r a c t e r¬ i z e d in that the engine has a fuel injection system with a unit injector (5) with an electrically operated spill valve (9) for each cylinder and that means (8, 20) are arranged which can keep the spill valve of the cylinder provided with the extra exhaust valve (11, 12) open at the same time as the extra exhaust valve is open.
2. Internal combustion engine according to Claim 1, c h a r¬ a c t e r i z e d in that the extra exhaust valve has a valve disc with a spindel (11), which cooperates with spring elements (14), biasing the valve towards a closed position, and that means (21) are arranged to keep the valve constantly open when the piston (3) in the associated cylinder is to work as a compressor piston.
3. Internal combustion engine according to Claim 2, c h a r- a c t e r i z e d in that the spindel (11) is mounted in a bore (10) with a portion formed as a cylinder (10a) and has a portion (15) functioning as a piston, that the cylinder (10a) has an intake for a pressure medium and that the piston portion (15) when pressure medium is supplied to the cylinder loads the valve (12) towards its open position.
PCT/SE1991/000791 1990-11-23 1991-11-21 Internal combustion engine with compressor function WO1992009792A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US08/064,135 US5315974A (en) 1990-11-23 1990-11-23 Internal combustion engine with compressor function
DE69110054T DE69110054T2 (en) 1990-11-23 1991-11-21 INTERNAL COMBUSTION ENGINE WITH COMPRESSION FUNCTION.
EP91920619A EP0558585B1 (en) 1990-11-23 1991-11-21 Internal combustion engine with compressor function
JP50010292A JP3326173B2 (en) 1990-11-23 1991-11-21 Internal combustion engine with compressor function

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9003735-9 1990-11-23
SE9003735A SE467503B (en) 1990-11-23 1990-11-23 COMBUSTOR FUNCTION ENGINE

Publications (1)

Publication Number Publication Date
WO1992009792A1 true WO1992009792A1 (en) 1992-06-11

Family

ID=20380992

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1991/000791 WO1992009792A1 (en) 1990-11-23 1991-11-21 Internal combustion engine with compressor function

Country Status (6)

Country Link
US (1) US5315974A (en)
EP (1) EP0558585B1 (en)
JP (1) JP3326173B2 (en)
DE (1) DE69110054T2 (en)
SE (1) SE467503B (en)
WO (1) WO1992009792A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998055746A1 (en) * 1997-06-04 1998-12-10 Volvo Lastvagnar Ab Internal combustion engine with at regulator
WO1999010631A1 (en) * 1997-08-26 1999-03-04 Volvo Lastvagnar Ab Internal combustion engine with compressor function

Families Citing this family (14)

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DE4309860C1 (en) * 1993-03-26 1994-06-09 Daimler Benz Ag Device for control of compressed air in cylinder of IC engine - involves control valve with switch valve down stream from which air is controllable in conduit connected to accumulator or exhaust gas conduit
US5540201A (en) * 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
DE4433258C1 (en) * 1994-09-19 1996-03-07 Daimler Benz Ag Engine brake for a diesel engine
DE19514116A1 (en) * 1995-04-14 1996-10-17 Daimler Benz Ag Device for controlling air compressed in a cylinder of an internal combustion engine
US5507261A (en) * 1995-05-12 1996-04-16 Caterpillar Inc. Four cycle engine with two cycle compression braking system
SE512556C2 (en) * 1995-12-22 2000-04-03 Volvo Ab Method for reducing vibration in a vehicle and device for carrying out the method
US5735242A (en) * 1996-04-17 1998-04-07 Cummins Engine Company, Inc. Fuel pressure activated engine compression braking system
US5876526A (en) * 1996-06-07 1999-03-02 Quantum Electronics, Inc. Automotive flat tire repair system improvement
US5806499A (en) * 1997-03-18 1998-09-15 Cummins Engine Company, Inc. Dedicated overhead cam shaft for unit injector
US5758620A (en) * 1997-03-21 1998-06-02 Detroit Diesel Corporation Engine compression brake system
US6216667B1 (en) 1999-11-12 2001-04-17 Frank J. Pekar Method and device for a supercharged engine brake
GB2405178A (en) * 2003-08-16 2005-02-23 Gordon Joseph Snadden Wilson Engine fuel economy system with cylinder deactivation
US8752519B2 (en) * 2009-12-15 2014-06-17 GM Global Technology Operations LLC Air assist start stop methods and systems
US10641140B2 (en) * 2017-05-12 2020-05-05 Caterpillar Inc. Hydraulic early engine exhaust valve opening system

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US2005536A (en) * 1933-03-24 1935-06-18 Westinghouse Electric & Mfg Co Auxiliary air arrangement for diesel locomotives

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US4557232A (en) * 1982-06-01 1985-12-10 Delorean John Z Swash plate engine
ES8601390A1 (en) * 1984-10-22 1985-10-16 Ruiz Guinea Jose M Kinetic energy utilization system for use with vehicles with internal combustion engine
US4706624A (en) * 1986-06-10 1987-11-17 The Jacobs Manufacturing Company Compression release retarder with valve motion modifier
JPH02123250A (en) * 1988-10-31 1990-05-10 Isuzu Motors Ltd Turbo-retarder
DE3839452A1 (en) * 1988-11-23 1990-05-31 Daimler Benz Ag ENGINE BRAKE DEVICE FOR AN INTERNAL COMBUSTION ENGINE
US5195489A (en) * 1992-01-03 1993-03-23 Jacobs Brake Technology Corporation Push rods for pistons in compression release engine retarders

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Publication number Priority date Publication date Assignee Title
US2005536A (en) * 1933-03-24 1935-06-18 Westinghouse Electric & Mfg Co Auxiliary air arrangement for diesel locomotives

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998055746A1 (en) * 1997-06-04 1998-12-10 Volvo Lastvagnar Ab Internal combustion engine with at regulator
US6314734B1 (en) 1997-06-04 2001-11-13 Volvo Lastvagnar Ab Internal combustion engine with AT regulator
WO1999010631A1 (en) * 1997-08-26 1999-03-04 Volvo Lastvagnar Ab Internal combustion engine with compressor function
US6269792B1 (en) 1997-08-26 2001-08-07 Volvo Lastvagnar Ab Internal combustion engine with compressor function

Also Published As

Publication number Publication date
EP0558585A1 (en) 1993-09-08
JP3326173B2 (en) 2002-09-17
SE9003735D0 (en) 1990-11-23
SE9003735L (en) 1992-05-24
JPH06503139A (en) 1994-04-07
SE467503B (en) 1992-07-27
DE69110054D1 (en) 1995-06-29
US5315974A (en) 1994-05-31
EP0558585B1 (en) 1995-05-24
DE69110054T2 (en) 1995-10-19

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