US3727486A - Engine having improved performance characteristics - Google Patents

Engine having improved performance characteristics Download PDF

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Publication number
US3727486A
US3727486A US00114652A US3727486DA US3727486A US 3727486 A US3727486 A US 3727486A US 00114652 A US00114652 A US 00114652A US 3727486D A US3727486D A US 3727486DA US 3727486 A US3727486 A US 3727486A
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US
United States
Prior art keywords
fuelling
engine
fuel
power unit
transmission according
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
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US00114652A
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English (en)
Inventor
N Vulliamy
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Perkins Ltd
Original Assignee
Perkins Engines Ltd
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Publication date
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
    • B60W30/18—Propelling the vehicle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
    • B60W10/11—Stepped gearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
    • B60W30/18—Propelling the vehicle
    • B60W30/1819—Propulsion control with control means using analogue circuits, relays or mechanical links
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H2061/0015—Transmission control for optimising fuel consumptions

Definitions

  • This invention relates to a motor vehicle, wherein the power unit and transmission includes an internal combustion engine and change-speed gears.
  • a conventional internal combustion engine installed in a motor vehicle and loaded through change-speed gears develops an approximation to a constant max- .imum power curve when engine power and vehicle speed are plotted on a graph.
  • An object of the present invention is to provide a vehicle with good hill-climbing ability and improved characteristics in respect of economy of operation at higher speeds on level routes.
  • an internal combustion engine disposes of the energy given up by the burning fuel by mechanical means to the load or vehicle, by waste heat in the exhaust and by waste heat in the cooling medium and that a given power demand can be met by burning an excess of fuel which may lead to uneconomic fuel consumption.
  • a motor vehicle power unit and transmission comprising an internal combustion engine having a variable delivery fuelling device, change-speed gears incorporating gear-ratio selecting mechanism, and fuelling control means associated with the fuelling device and the said selecting mechanism and operative in response to selection of an intermediate gear ratioso as to adjust the fuelling device to be capable of delivering a predetermined increased maximum quantity of fuel.
  • a motor vehicle incorporating a power unit and transmission aforesaid.
  • FIG. 1 represents engine power (P) curves on the basis of vehicle speed (SV) for different transmission ratios
  • FIG. 2 represents engine torque (T) curves on the basis of vehicle speed (SV) for the transmission ratios in FIG. 1;
  • FIG. 3 shows in diagrammatic form, a motor vehicle power unit and transmission in accordance with the present invention
  • FIG. 4 shows one form of fuelling control in accordance with the present invention
  • FIG. 5 shows, in diagrammatic form, another form of fuelling control in accordance with the present invention.
  • FIG. 6 shows a further form of fuelling control in accordance with the present invention, basically similar to that of FIG. 5, but incorporating modifications.
  • the full lines 1 to 5 represent the power curves of a supercharged compression ignition engine driving a vehicle equipped with a change-speed gearbox having five forward ratios.
  • the peaks of the curves 1 to 5 are substantially at the same power level, this indicating that the maximum engine power available throughout the vehicle speed range is substantially constant.
  • the broken lines 6 to 8 show the power curves to be derived from an engine and transmission according to the present invention. It will be seen that the peaks of curves 6, 7 and 8 are substantially above the level of the peaks of curves 2, 3 and 4. The corresponding engine torque curves are marked 1' t0 5' and 6' to 8' in FIG. 2. This is achieved by modifying engine fuelling according to which gear ratio is selected.
  • gear ratio four When gear ratio four is chosen to negotiate a hill or part of a hill, engine fuelling is adjusted to give increased maximum power and torque at the expense of greater heat rejection and as a result of increased cylinder pressure. Successively, gear ratio three gives a higher maximum power still so that at about half the vehicle top speed the engine is made to deliver very much more power than at top speed. This manifests itself as a power bulge 10 and 10' in graphs of FIG. 1 and FIG. 2.
  • the engine will be very highly thermally loaded at this stage, but vehicle operation in intermediate ratios at full power would be effected for only a limited time so that the engine is capable of accepting this high thermal loading without sustaining damage.
  • the presence of supercharge enables the extra fuel to be burnt efficiently and assists to a considerable extent in reducing the thermal loading below what it would be otherwise.
  • a diesel engine 20 has an inlet manifold 21 connected to the outlet 23 of a compressor 25 and an exhaust manifold 22 connected to the inlet 24 of an exhaust gas turbine 26.
  • the turbine 26 is coupled to and normally drives the compressor 25.
  • a change-speed gearbox 29 having five forward ratios and having a gear selector lever 30 drives through a drive shaft 31 to a rear axle 32.
  • Fuelling control means consists of a sensor 33 on the gearbox 29 connected to an actuator unit 35 operable to vary the maximum output of the fuel pump.
  • Solenoids S2 and S3 each operate when energized to pull a plate 41 a predetermined distance towards itself.
  • Solenoid S4 operates to pull a similar plate 42 the same predetermined distance against a spring.
  • the plates 41 and 42 are mutually at right angles and the solenoids are placed accordingly.
  • the plates 41 and 42 are in line with the fuelling control rod 43 of the fuel pump and are allowed a degree of movement in the direction X X.
  • a fixed abutment is provided behind the plates 41 and 42. Both plates are spring loaded to the central position.
  • the plates have different thicknesses at T4, T3, T2 and TN.
  • FIG. 5 parts of a rotary distributor-type fuel injection pump are indicated by the prefix R.
  • Fuel from a tank 50 is pumped through a variable metering valve R51 by a transfer pump R52. Transfer pressure is regulated by means of a regulating valve R53.
  • Metered fuel is fed to injectors, one of which is shown at 54, by a rotary distributor R55 incorporating opposed high-pressure plungers R56 whose radial outer ends co-operate with an annular cam R57 having as many lobes as there are engine cylinders.
  • a five-forward-ratio transmission control unit 58 exercises hydraulic control of'transmission clutches or brakes 59 to 63 for first to fifth forward gear ratios respectively.
  • Fuelling control means consists of three twoposition, pilot-operated, springreturned valves 64, 65 and 66 which are associated with intermediate gear ratios two, three and four respectively.
  • the normally-open inlet port of each of valves 64 to 66 is connected to that conduit of the fuel injection pump containing fuel at metering pressure; the normally open outlets are commonly drained to a sump or reservoir.
  • Flow restrictors are incorporated or associated one in, or with, each of valves 64 to 66. ln order to obtain the characteristic of curve in FIG. 1, the restrictors of valves 64 and 66 would each be required to have a smaller orifice than that of the restrictor of valve 65.
  • the maximum quantity of fuel metered to the distributor R55 is increased over the maximum quantity metered in first and fifth ratios by a factor which is governed by the size of the flow restrictor which is, in effect, closed upon operation of any of the valves 64 to 66 by actuators such as pilots 64' to 66', respectively.
  • FIG. 6 parts corresponding with those in FIG. 5 are given the reference numerals used in FIG. 5.
  • sensing of ratio-selection is by means of pressure switches 67.
  • Each switch 67 is associated hydraulically with a different gear ratio, and electrically connected to an actuator, such as a variable orifice control, in a logic unit 68 adapted to select and bring into operation an escape-flow of fuel from the fuel metering conduit appropriate to the required predetermined performance characteristic.
  • Another aspect of the modifications in FIG. 6 is the inclusion of a two-ratio rear axle or final drive which is indicated at 69. Low" or High final drive ratio is selected according to whether a manual switch 70 is open or closed.
  • the logic unit 68 is provided with electrical gating for giving effect to fuelling control, in accordance with predetermined characteristics, depending, for example, upon whether any of the five ratios selected by unit 58 constitutes an intermediate ratio. Therefore, the logic unit 68 is electrically associated with the switch 70 so that in fifth ratio selection, for example, fuelling control is effected only when the low" final drive ratio is selected; the combination of low" final drive with selection of fifth gear ratio constituting an intermediate gear ratio.
  • a motor vehicle power unit and transmission comprising an internal combustion engine, a variable delivery fuelling device, change-speed gears, a gearratio selecting mechanism, an-intermediate portion of said selecting mechanism for selection of intermediate gear ratios only, and fuelling control means connected to said intermediate portion of said selecting mechanism and to said fuelling device to adjust the maximum deliverable quantity of fuel upward and allow greater quantities of fuel to said internal combustion engine for increased power when operating in an intermediate gear ratio over that when operating in either low or high gear ratiosv 2.
  • said engine is a compression ignition engine.
  • a power unit and transmission according to claim 1 including a supercharger supplying additional air over that otherwise available to enable more complete combustion of the additional fuel supplied by virtue of said fuelling control means adjusting said fuelling device.
  • said fuelling control means includes an actuator capable of adjusting the upper fuel flow limit of said fuelling device upward.
  • said fuelling control means further includes a sensor capable of sensing activation of said portion of said selecting mechanism upon selection of an intermediate gear ratio, said sensor signalling said actuator to cause activation of said fuelling device.
  • said fuelling control means includes a fuel injection pump, at least one valve on said pump for fuel flow control, and said actuator is a pilot on said valve, said pilot capable of shifting said valve causing increased flow of fuel to said engine over that otherwise provided by said pump.
  • said fuelling control means includes a fuel injection pump, a control rod on said pump for metering flow to said engine, and said sensor and actuator are an electrical switch and a solenoid, respectively, said solenoid capable of removing a mechanical constraint on said control rod to permit increased fuel flow to said

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Control Of Transmission Device (AREA)
  • Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Control Of Driving Devices And Active Controlling Of Vehicle (AREA)
US00114652A 1970-02-13 1971-02-11 Engine having improved performance characteristics Expired - Lifetime US3727486A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB701170 1970-02-13

Publications (1)

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US3727486A true US3727486A (en) 1973-04-17

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Country Status (6)

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US (1) US3727486A (enrdf_load_stackoverflow)
DE (1) DE2106060A1 (enrdf_load_stackoverflow)
ES (1) ES388209A1 (enrdf_load_stackoverflow)
FR (1) FR2078357A5 (enrdf_load_stackoverflow)
GB (1) GB1335828A (enrdf_load_stackoverflow)
SE (1) SE367968B (enrdf_load_stackoverflow)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4823642A (en) * 1986-04-30 1989-04-25 Mazda Motor Corporation Air-fuel ratio controlling apparatus of an engine with an automatic change gear of electronic control type
DE20014422U1 (de) 2000-08-18 2000-12-07 Meister, Helmut, 77833 Ottersweier Profilanordnung zur Verbindung von Trennwänden
US20150192073A1 (en) * 2014-01-06 2015-07-09 Rolls-Royce Controls And Data Services Limited Engine fuel control system

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1161526A (en) * 1980-03-31 1984-01-31 William J. Vukovich Throttle control system for an automatic shift countershaft transmission
US5569115A (en) * 1995-07-27 1996-10-29 Rockwell International Corporation Engine speed synchronization system for assisting in manual transmission shifting
US5582558A (en) * 1995-07-27 1996-12-10 Rockwell International Corporation Combined system for assisting shifting of manual transmission

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2355759A (en) * 1942-02-10 1944-08-15 H M Hobson Aircraft & Motor Co Exhaust-driven turbosupercharger for internal-combustion engines
US2719437A (en) * 1949-04-30 1955-10-04 Daimler Benz Ag Device for the control of vehicle engines
US2909078A (en) * 1954-11-02 1959-10-20 Daimler Benz Ag Method of controlling the operation of an automobile engine
US3448640A (en) * 1967-06-30 1969-06-10 Gen Motors Corp Electrical control for automatic transmission
US3487634A (en) * 1968-03-19 1970-01-06 Mack Trucks Constant horsepower internal combustion engines

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2355759A (en) * 1942-02-10 1944-08-15 H M Hobson Aircraft & Motor Co Exhaust-driven turbosupercharger for internal-combustion engines
US2719437A (en) * 1949-04-30 1955-10-04 Daimler Benz Ag Device for the control of vehicle engines
US2909078A (en) * 1954-11-02 1959-10-20 Daimler Benz Ag Method of controlling the operation of an automobile engine
US3448640A (en) * 1967-06-30 1969-06-10 Gen Motors Corp Electrical control for automatic transmission
US3487634A (en) * 1968-03-19 1970-01-06 Mack Trucks Constant horsepower internal combustion engines

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4823642A (en) * 1986-04-30 1989-04-25 Mazda Motor Corporation Air-fuel ratio controlling apparatus of an engine with an automatic change gear of electronic control type
DE20014422U1 (de) 2000-08-18 2000-12-07 Meister, Helmut, 77833 Ottersweier Profilanordnung zur Verbindung von Trennwänden
US20150192073A1 (en) * 2014-01-06 2015-07-09 Rolls-Royce Controls And Data Services Limited Engine fuel control system
US9739208B2 (en) * 2014-01-06 2017-08-22 Rolls-Royce Plc Engine fuel control system

Also Published As

Publication number Publication date
GB1335828A (en) 1973-10-31
ES388209A1 (es) 1974-02-16
SE367968B (enrdf_load_stackoverflow) 1974-06-17
FR2078357A5 (enrdf_load_stackoverflow) 1971-11-05
DE2106060A1 (de) 1971-08-19

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