US3712280A - Admission circuits of diesel engines - Google Patents

Admission circuits of diesel engines Download PDF

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Publication number
US3712280A
US3712280A US00086229A US3712280DA US3712280A US 3712280 A US3712280 A US 3712280A US 00086229 A US00086229 A US 00086229A US 3712280D A US3712280D A US 3712280DA US 3712280 A US3712280 A US 3712280A
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United States
Prior art keywords
engine
circuit
compressor
admission
fuel
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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
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US00086229A
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English (en)
Inventor
M Brille
Y Baguelin
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Individual
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Individual
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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
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/02—Drives of pumps; Varying pump drive gear ratio
    • F02B39/04—Mechanical drives; Variable-gear-ratio drives
    • 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
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/44—Passages conducting the charge from the pump to the engine inlet, e.g. reservoirs
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/14—Control of the alternation between or the operation of exhaust drive and other drive of a pump, e.g. dependent on speed
    • 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

  • ABSTRACT An improved Diesel engine supercharged by a turbocompressor and corrected by a volumetric compressor corr ecter device dnven from the engine crank shaft at a speed ratio which increases as the pressure delivered by the centrifugal compressor diminishes, in which an exchanger of heat with the cooling liquid of the engine is provided between the turbo-compressor and the volumetric corrector device, and in which the portion of the admission circuit comprised between the heat exchanger and the engine is provided with a heat and sound-insulation system.
  • the first of these Patent Applications relates to a Diesel engine supercharged by a turbocompressor with a volumetric corrector interposed between the turbo-compressor and the engine, this corrector, of the gear compressor type, being driven from the engine crank shaft with a variable speed ratio in order that the volumetric compressor may give a higher delivery pressure as the pressure given by the turbo compressor diminishes.
  • this corrector of the gear compressor type, being driven from the engine crank shaft with a variable speed ratio in order that the volumetric compressor may give a higher delivery pressure as the pressure given by the turbo compressor diminishes.
  • an exchanger of heat with the cooling liquid of the engine which in all cases maintains the temperature of the air at a value close to that of the cooling circuit.
  • the second Patent Application referred to concerns the same engine completed by a fumigation circuit which introduces, at low loads and low speeds, a certain quantity of fuel into the admission of the volumetric corrector compressor.
  • the starting up of the engine constitutes a special limiting case of low loads and low speeds.
  • the cooling circuit of the engine is at ambient temperature and cannot therefore serve to heat the mixture; on the other hand, at this speed of the engine, the volumetric compressor is subject to considerable leakages in relative value and cannot immediately give large pressures and adequate temperatures.
  • the fumigation system combined with the introduction of a small quantity of oil enables these leakages to be reduced so as to obtain on the downstream side of the compressor, a slight over pressure and a slight increase in temperature.
  • the main object of the present invention consists of giving a cumulative effect to this increase in temperature by preventing the temperature increases obtained at each revolution of the volumetric compressor from being dissipated by radiation, which is effected by heat insulating the whole circuit comprised between the heat exchanger and the engine admission, namely:
  • This arrangement is all the more useful as the external temperature is lower.
  • a second characteristic feature of the invention consists of choosing the lagging material in such manner that it combines a sound insulating effect with the heat insulation effect.
  • a third characteristic feature of the invention is to effect this insulation by projection, spraying, spreading with a paint or hand brush an adhesive plastified product comprising a certain proportion of heat and sound insulating material, such as mica, asbestos, etc.
  • the heat insulation according to the invention has the effect of maintaining not only the air but also the fumigation liquids at the outlet temperature of the volumetric compressor. It is for this reason that the recycling circuit of the fuel is also insulated.
  • means is provided to prevent the fuel from being introduced directly into the engine in a liquid state.
  • This means resides in the particular structure of the manifold which will be described in more detail in the general description which follows.
  • FIG. 1 is a general diagram of the installation showing the heat insulated portion in the general circuit.
  • FIG. 2 shows a cross -section taken along the line a a of the volumetric compressor
  • FIG. 3 shows a transverse section taken along the line b b of the admission manifold of the engine.
  • the exhaust of the Diesel engine 1 is effected by the pipe 2 through the turbine 3 which drives the centrifugal compressor 4, the latter compressing the air in the pipe 5 which passes through the exchanger 6 comprising the liquid inlet and outlet 7 and 8.
  • the compressed air from the pipe 5 passes through the pipe 9 into the volumetric compressor 10, the delivery of which is effected into the manifold 11.
  • the compressor 10 is driven at a speed which is variable with respect to that of the crank shaft 13 by means of the extensible pulley 12 with displaceable flanges; the speed variation is obtained by varying the distance between centers of the two pulleys, i.e., by displacement of the support 41 under the opposite effects of the spring 15 and the cylinder 16, subjected directly or indirectly through the intermediary of the piping 17, to the pressure created in the pipe 5 by the centrifugal compressor.
  • the distance between centers of the two pulleys and therefore the ratio of the respective speeds of the com pressor and the engine increases when the pressure falls in the pipe 5, Le, the volumetric compressor increases its compressive action as the compression of the centrifugal compressor is reduced.
  • the fins are replaced by necessary stiffening ribs, but which do not serve in any way for cooling purposes due to the existence of the lagging.
  • This lagging is carried out in the manner indicated in the preamble.
  • the exterior of the deposited layer is coated with a paint or with an insulating product which prevents the lagging from being impregnated with water, fuel or any liquid product, which would be liable to destroy it or to render it ineffective or dangerous.
  • This protective layer is shown in the drawings in dotted line enclosing the hatched portions.
  • FIG. 3 there will be observed the position of the end connectors 18 with respect to the engine, the presence of the connection fillets 19 and the provision of a partition 20 over the length of the manifold and compelling the combustion supporting air and when so required the fumigation mixture to pass over a baffle which facilitates the segregation of the liquid.
  • a few holes 21 of small diameter at the lower portion of the partition enable them to be collected from the bottom portion.
  • the extremity 22 (see FIG. 1) of the sheet metal on the side of the compressor is rolled in such manner that the output of the compressor only passes into the lower section of the manifold.
  • rocker arm cover 23 is also isolated in the same way as the parts previously described. This is justified by the-noise factor. as described below:
  • the admission and exhaust noises are filtered by the turbo-machine which in particular clamps the pulsations of the engine at the exhaust and of the volumetric compressor at the admission; the exchanger with its baffles also contributes to the damping of the noise.
  • the mechanical noise of the valve rocker arm becomes predominant, and it is in order to avoid this that the invention also comprises the sound insulation 55 of the rocker arm cover 23.
  • the control of the admission air temperature is assigned to the exchanger 6 and the compressor 10.
  • the control of the oil temperature is assigned to the oil water exchanger (not shown), it bein understood that the cooling liquid of these two exc angers is itself controlled from the radiator by thermostat at one or more levels of temperature, corresponding to the requirements of the circuit.
  • a Diesel engine as claimed in claim I in which said insulation consists of a layer of a plastified product comprising a high proportion of an insulating product such as mica and/or asbestos.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Supercharger (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US00086229A 1969-10-31 1970-11-02 Admission circuits of diesel engines Expired - Lifetime US3712280A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR6937527A FR2063795A5 (ja) 1969-10-31 1969-10-31

Publications (1)

Publication Number Publication Date
US3712280A true US3712280A (en) 1973-01-23

Family

ID=9042421

Family Applications (1)

Application Number Title Priority Date Filing Date
US00086229A Expired - Lifetime US3712280A (en) 1969-10-31 1970-11-02 Admission circuits of diesel engines

Country Status (5)

Country Link
US (1) US3712280A (ja)
JP (1) JPS5014282B1 (ja)
DE (1) DE2052501A1 (ja)
FR (1) FR2063795A5 (ja)
GB (1) GB1318800A (ja)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3795231A (en) * 1971-05-25 1974-03-05 Vehicyles Ind D Equipments Mec Cold starting devices for diesel engines with compensated supercharging
US3951114A (en) * 1974-03-22 1976-04-20 Hans List Cooling of internal combustion engines with sound-proof encasings
US4738110A (en) * 1986-03-29 1988-04-19 Toyota Jidosha Kabushiki Kaisha Diesel engine equipped with a mechanically driven charger
US4875454A (en) * 1987-02-17 1989-10-24 Mazda Motor Corporation Supercharging apparatus for an internal combustion engine
US5335500A (en) * 1992-03-27 1994-08-09 Mercedes-Benz Ag Internal combustion engine with combined pressure charging
US5870893A (en) * 1994-03-28 1999-02-16 Starodetko; Evgeny Alexandrovich Method of carrying out a cycle in a piston internal combustion engine and a piston internal combustion engine
US6185939B1 (en) 1999-03-22 2001-02-13 Caterpillar Inc. Exhaust gas recirculation system
US6192686B1 (en) 1999-03-22 2001-02-27 Caterpillar Inc. Exhaust gas recirculation system
US6205775B1 (en) 1999-03-22 2001-03-27 Caterpillar Inc. Exhaust gas recirculation control system
US6230695B1 (en) 1999-03-22 2001-05-15 Caterpillar Inc. Exhaust gas recirculation system
US20080110170A1 (en) * 2005-01-28 2008-05-15 Florian Noodt Dual-Charged Internal Combustion Engine and Method for Operating the Same

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2491132A1 (fr) * 1980-09-29 1982-04-02 Kronogard Sven Olof Installation de propulsion de vehicule comprenant plusieurs cylindres de puissance differente
DE3538790A1 (de) * 1985-10-31 1987-05-07 Gutehoffnungshuette Man Abgasschraubenlader
DE4433285A1 (de) * 1994-09-19 1996-03-21 Motoren Werke Mannheim Ag Verbrennungsluftleitung einer Brennkraftmaschine
US10662903B2 (en) * 2015-02-27 2020-05-26 Avl Powertrain Engineering, Inc. Waste heat recovery and boost systems including variable drive mechanisms

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1898460A (en) * 1928-04-26 1933-02-21 Edward C Newcomb Two-cycle engine
GB465365A (en) * 1935-12-23 1937-05-06 George Mcstay Silencer for internal combustion engines
US2201014A (en) * 1937-06-09 1940-05-14 Daimler Benz Ag Arrangement for drawing fuel out of the induction conduit of internal combustion engines
US2417604A (en) * 1943-03-06 1947-03-18 Stewart Warner Corp Heater having means for diverting and igniting a fuel-air mixture
US2962051A (en) * 1959-02-27 1960-11-29 Phillips Petroleum Co Insulated blast tube and method of forming
US3235003A (en) * 1963-06-04 1966-02-15 Cloyd D Smith Spiral flow baffle system
US3355879A (en) * 1963-07-04 1967-12-05 Sir W G Armstrong & Company En Turbocharged two-stroke cycle internal combustion engines
US3395775A (en) * 1965-11-12 1968-08-06 Solar A Division Of Internat H Vibration damping composite
US3534828A (en) * 1967-11-10 1970-10-20 Gen Electric & English Electri Reduction of noise emitted by machines
US3540425A (en) * 1967-08-21 1970-11-17 List Hans Internal combustion engine with soundproofing cowling

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1898460A (en) * 1928-04-26 1933-02-21 Edward C Newcomb Two-cycle engine
GB465365A (en) * 1935-12-23 1937-05-06 George Mcstay Silencer for internal combustion engines
US2201014A (en) * 1937-06-09 1940-05-14 Daimler Benz Ag Arrangement for drawing fuel out of the induction conduit of internal combustion engines
US2417604A (en) * 1943-03-06 1947-03-18 Stewart Warner Corp Heater having means for diverting and igniting a fuel-air mixture
US2962051A (en) * 1959-02-27 1960-11-29 Phillips Petroleum Co Insulated blast tube and method of forming
US3235003A (en) * 1963-06-04 1966-02-15 Cloyd D Smith Spiral flow baffle system
US3355879A (en) * 1963-07-04 1967-12-05 Sir W G Armstrong & Company En Turbocharged two-stroke cycle internal combustion engines
US3395775A (en) * 1965-11-12 1968-08-06 Solar A Division Of Internat H Vibration damping composite
US3540425A (en) * 1967-08-21 1970-11-17 List Hans Internal combustion engine with soundproofing cowling
US3534828A (en) * 1967-11-10 1970-10-20 Gen Electric & English Electri Reduction of noise emitted by machines

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3795231A (en) * 1971-05-25 1974-03-05 Vehicyles Ind D Equipments Mec Cold starting devices for diesel engines with compensated supercharging
US3951114A (en) * 1974-03-22 1976-04-20 Hans List Cooling of internal combustion engines with sound-proof encasings
US4738110A (en) * 1986-03-29 1988-04-19 Toyota Jidosha Kabushiki Kaisha Diesel engine equipped with a mechanically driven charger
US4875454A (en) * 1987-02-17 1989-10-24 Mazda Motor Corporation Supercharging apparatus for an internal combustion engine
US5335500A (en) * 1992-03-27 1994-08-09 Mercedes-Benz Ag Internal combustion engine with combined pressure charging
US5870893A (en) * 1994-03-28 1999-02-16 Starodetko; Evgeny Alexandrovich Method of carrying out a cycle in a piston internal combustion engine and a piston internal combustion engine
US6185939B1 (en) 1999-03-22 2001-02-13 Caterpillar Inc. Exhaust gas recirculation system
US6192686B1 (en) 1999-03-22 2001-02-27 Caterpillar Inc. Exhaust gas recirculation system
US6205775B1 (en) 1999-03-22 2001-03-27 Caterpillar Inc. Exhaust gas recirculation control system
US6230695B1 (en) 1999-03-22 2001-05-15 Caterpillar Inc. Exhaust gas recirculation system
US20080110170A1 (en) * 2005-01-28 2008-05-15 Florian Noodt Dual-Charged Internal Combustion Engine and Method for Operating the Same
US7810329B2 (en) * 2005-01-28 2010-10-12 Volkswagen Ag Dual-charged internal combustion engine and method for operating the same

Also Published As

Publication number Publication date
JPS5014282B1 (ja) 1975-05-27
DE2052501A1 (de) 1971-05-06
GB1318800A (en) 1973-05-31
FR2063795A5 (ja) 1971-07-09

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