EP0057300A1 - Brennkraftmaschine mit innerer Verbrennung - Google Patents

Brennkraftmaschine mit innerer Verbrennung Download PDF

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Publication number
EP0057300A1
EP0057300A1 EP81300343A EP81300343A EP0057300A1 EP 0057300 A1 EP0057300 A1 EP 0057300A1 EP 81300343 A EP81300343 A EP 81300343A EP 81300343 A EP81300343 A EP 81300343A EP 0057300 A1 EP0057300 A1 EP 0057300A1
Authority
EP
European Patent Office
Prior art keywords
fluid
piston
pistons
cylinder
cylinders
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.)
Withdrawn
Application number
EP81300343A
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English (en)
French (fr)
Inventor
John Harbidge
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to EP81300343A priority Critical patent/EP0057300A1/de
Publication of EP0057300A1 publication Critical patent/EP0057300A1/de
Withdrawn legal-status Critical Current

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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
    • F02B71/00—Free-piston engines; Engines without rotary main shaft
    • F02B71/04—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby
    • F02B71/045—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby with hydrostatic transmission
    • 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
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two

Definitions

  • the object of this invention is to provide an internal combustion engine arrangement of the reciprocating piston type in which the power output is provided in the form of fluid under pressure such as pressurised hydraulic fluid.
  • an internal combustion engine arrangement of the reciprocating piston type is characterised by the or each piston of the engine being connected to a corresponding piston of a cylinder for receiving fluid from a source of supply of the latter whereby on a power stroke of the engine piston, the piston connected thereto is operated to expel fluid under pressure from its associated cylinder for power output use, driven valve means and metering means being provided for receiving and directing only a necessary amount of said output fluid under pressure sufficient to effect fluid pressure operated return of the connected pistons for a compression stroke of the or each engine piston.
  • the engine may consist of one or more cylinder units 1 and in the example shown in FIGURE 1, five cylinder units 1 are em- ' ployed, each of which advantageously consists of an opposed piston arrangement (see FIGURE 2) although a piston and cylinder head arrangement may be employed if desired.
  • Each engine piston 2 in its cylinder 3 is directly connected by a connecting rod 4 with a piston 5 of a hydraulic cylinder 6 which in turn communicates via a non-return valve 7 with a high pressure output manifold 8 for the supply of fluid under pressure for any required purpose such as the operation of one or more hydraulic motors and/or rams.
  • Each opposed piston cylinder unit 1 operates on a two-stroke cycle with preferably compression ignition in which fuel is injected at the appropriate time between the engine pistons 2 prior to their power stroke movement apart and operation of the hydraulic pistons 5 in expelling fluid from the hydraulic cylinders 6 to the output manifold 8.
  • the engine cylinder 3 is shown finned at 13 for air cooling but may be liquid cooled and the inlet and exhaust manifolds are indicated at 9, 10 respectively.
  • Exhaust gas output is arranged to operate a turbo-charger 11 (FIGURE 1) for admitting a forced air supply to the inlet manifold 9.
  • Other suitable air charging means may be employed.
  • each piston is shown connected at 35 to a corresponding rack 33 (FIGURE 2) meshing with a common pinion 34 so that relative movement of the pistons 3 is maintained in a positive manner.
  • a supply of fluid at high or working pressure is taken from the output manifolds 8 (which are inter-connected) and admitted at 210 into the high pressure section HP of the chamber 21 of the distributor 20 containing a rotary valve member 22 (see FIGURE 5).
  • the rotary valve member 22 is driven by a hydraulic motor 12 (FIGURE 1) via a toothed belt drive 14 and coupling 15 (FIGURE 3), the hydraulic motor 12 being continuously driven by a tapped off high pressure fluid supply from the output manifolds 8..
  • valve member 22 On rotation of the valve member 22 (i.e. in a clockwise direction in FIGURE 5), fluid from the high pressure section HP is passed to a port A which communicates with one end of a bore 32 of metering means 30 containing a piston 31 (FIGURE 4) and moves the piston 31 axially to the right, which expels fluid from the bore 32 to the port B and from thence to the compression pressure section CP of the valve member 22.
  • fluid is also drawn into the hydraulic cylinder 6 from a fluid input manifold 18 via a non-return valve 17.
  • Each fluid input manifold 18 is shown adjacent to, but separate from, an output manifold 8 and both input manifolds 18 communicate with the fluid supply reservoir.
  • non-return valves 16 and 17 are shown conveniently embodied in the same assembly and in a relatively slidable manner, the assembly incorporating a single compression spring 19 loading both valves 16, 17.
  • the high pressure section HP is communicated with port B which acts on the piston 31 to move it in the opposite direction (i.e. to the left in FIGURE 4) which, in a similar manner, expels a quantity of fluid under pressure via the port A to the compression pressure section CP of the valve member 22 from where it passes to a further outlet connection 25 to the hydraulic cylinders 6 of another cylinder unit 1.
  • the distributor 20 has three outlet connections 25 for use with three cylinder units 1 but can be developed in a similar manner for any practical number of cylinder units such as the five unit arrangement shown in FIGURE 1.
  • the recessing or pocketing of the rotary valve member 22 is arranged in a symmetrical manner for balanced operation.
  • An adjustable stop 36 is shown provided for the piston 31 whereby its.extent of axial movement can be pre-set according to requirements, i.e. as determined by the amount of fluid pressure energy passed to a hydraulic cylinder 6 which is sufficient to effect required compression return movement of the associated engine piston 2.
  • the stop 36 is shown in the form of a screw and is set for causing only a necessary amount of fluid pressure energy to be passed for compression purposes so that a minimum of such energy is taken from the fluid pressure output energy of the engine.
  • the stop 36 may be arranged for manual adjustment (i.e. as indicated in FIGURE 4) and/or it may be adjustable in response to the speed of rotation of the distributor 20 and/or output pressure and/or operation of fuel injection means to the engine cylinders 3 in obtaining a required metering action.
  • An innermost part 222 of the valve member 22 in the low pressure section LP has a port 228 co-operating with fixed ports 28 for effecting operation of a fuel injector unit 50.
  • fluid from the high pressure section HP of the distributor chamber 21 is supplied via a radial passageway 27 to the supply port 228 which is in turn, by the action of the innermost part 222 of the rotary valve member 22 communicated by a port 28 with means for actuating a corresponding plunger or piston 51 of the fuel injector unit 50 (FIGURE 3) for the supply of a required quantity of fuel to the injector of a cylinder 3 of the appropriate engine cylinder unit 1.
  • fluid is passed by an appropriate port 28 via a corresponding passageway 48 in a body 40 to a bore 42 which contains a piston 41 which in turn acts on the associated spring loaded plunger 51 of the injector unit 50, the number of injectors depending on the number of engine cylinder units 1 employed e.g. three in the. case of the distributor unit 20 shown in FIGURES 3 to 5.
  • the valve member 22 rotates,fluid is able to exhaust from the passageway 48 and corresponding port 28 to the low pressure section or pocket LP of the valve member 22 and from thence to the reservoir via the radial passageway 29.
  • each injector piston or plunger 51 can be limited or pre-set by axial adjustment of a spring loaded stop member 52 i.e. by means of a cam 53 acting on the outer end of a piston 54 connected to or integral with the stop member 52.
  • a spring loaded stop member 52 i.e. by means of a cam 53 acting on the outer end of a piston 54 connected to or integral with the stop member 52.
  • the body or block 40 carrying the injector unit 50 is angularly adjustable relative to the body of the distributor 20 for obtaining appropriate timing of fuel injection. Angular adjustment of the block 40 for such timing purposes may be automatically effected such as by controlled operation from the rack pinion 34 or by electronic means.
  • the output manifolds 8 are shown communicated with a vessel or an accumulator 60 for storing hydraulic fluid under pressure in not only catering for variation in demand for the fluid under pressure and thus maintaining proper operation of the engine, but also providing a supply of such fluid for starting purposes.
  • a hydraulic pump or the hydraulic motor 12 operating as a pump may be driven by an electric motor to build up sufficient pressure in the output manifolds 8 for obtaining effective compression stroke operation of the engine pistons 2.
  • the engine pistons 2 should be first thrust apart e.g. by admission of air under pressure into each cylinder 3 between the pistons 2 therein. Resulting displacement of hydraulic fluid towards the output manifolds 8 may be temporarily accommodated in a reservoir arranged for communication with the manifolds 8 or directly with the hydraulic cylinders 6.
  • a generator or alternator 70 may be driven from the hydraulic motor 12 and also a fan or blower 80 for obtaining cooling of the cylinder units 1, the blower 80 operating in conjunction with an air cooling outlet indicated at 81.
  • FIGURE 6 Referring to the diagrammatic layout of FIGURE 6 in which corresponding reference numerals are employed,a modified arrangement is shown whereby the number of non-return valves is reduced per cylinder unit 1.
  • the hydraulic cylinders 6 are connected via a single non-return valve 7 to the fluid pressure output 8, the accumulator 60 communicating with the output 8.
  • the distributor valve 20 is generally of similar construction and operation to that already described with reference to FIGURES 4 to 5 and likewise the metering means 30.
  • a supply of fluid under pressure from the output 8 is admitted at 210 into the high pressure section of the distributor 20, output from the port A or B of the latter being directed to an appropriate end of the bore 32 of the metering means 30 and containing the piston 31.
  • Hydraulic fluid returned by the 20 action of the piston 31 to the distributort is passed via the latter to the outlet 25 and from thence via pipework 26 containing a single non-return valve 16 in order to effect return operation of the pistons 5 in the hydraulic cylinders 6 for compression stroke operation of the engine pistons 2.
  • fluid is also drawn into the cylinders 6 from a fluid input 18 via a single non-return valve 17, the fluid input 18 communicating with a fluid supply reservoir.
  • Communication of the low pressure section of the distributor valve 20 with the fluid input 18 is indicated at 29.
  • Such fluid flow from the input 18 to the cylinders 6 may be assisted by a continuously operating pump incorporating a relief valve and driven for example by the same motor drive 12 to the distributor 20.
  • the plunger 51 of the fuel injector unit 50 may be operated by the distributor valve 20 in the manner already described or operation of the plunger 51 may be triggered by piston movement of the engine either by a piston actuated switch controlling a solenoid operating the plunger 51 or by a hydraulic switch similarly actuated in a fluid pressure supply arranged to effect operation of the plunger 51.
  • Fuel supply to a cylinder 55 containing the fuel injection plunger 51 is indicated at 56 and includes a non-return valve 57.
  • FIGURE 7 a development is shown incorporated in a further modified arrangement of FIGURE 6 for providing more direct hydraulic return operation of the pistons 5 in the cylinders 6 for compression stroke return of the engine pistons 2.
  • a generally similar but simplified distributor 200 having a driven rotary valve member 220 is arranged to supply fluid to a timing valve 90 and modified metering means 300.
  • a single acting metering piston 31 in the bore 32 of the metering means 300 is positioned at or near one end of the bore 32, viz: at the right hand end in the diagram and is continuously subject to fluid at working high pressure from the output 8.
  • high pressure fluid HP being passed from the distributor 200 to a piston 91 connected to the valve member 92 of the timing valve 90, the valve member 92 is lifted.
  • the action of the working high fluid pressure on the piston 31 is such as to move it rapidly to the left and thus expel fluid at high pressure from the bore 32 and past the lifted valve member 92 directly to the cylinders 6 via the pipework 26 or other suitable passageway means.
  • a by-pass 37 to the metering means 300 is maintained at low pressure LP from the distributor 200, i.e. up to the non-return valve 39 in order to ensure that high pressure fluid does not py-pass the metering means 300 at this stage.
  • the distributor 200 operates to admit fluid at working pressure HP from the output 8 to both ends of the bore 32 of the metering means 300 via the by-pass pipe 37 in order to equalize pressure on the piston 31 and enable it to be returned to its initial position,(i.e. to the right hand end) in the bore 32 by the spring 38 ready for further operation on opening of the timing valve 90 again.
  • the non-return valve 39 in the by-pass 37 prevents fluid expelled from the bore 32 on operative movement of the piston 31, being returned to the distributor 200.
  • the extent of movement of the piston 31 should be adjustable by stop screw or other means.
  • the pipework 26 or similar passageway means serves not only to supply fluid under pressure to the cylinders 6 for compression return movement of the pistons 5 and 2 but also to pass fluid from the cylinders 6 to the working fluid pressure output 8 on power stroke operation of the pistons 2 and 5.
  • a single distributor 200 can be employed for directing return of output fluid under pressure in turn to the cylinders 6 of each cylinder unit 1.
  • a metering unit 300 and timing valve 90 would be provided one to each cylinder unit 1.
  • Any suitable driven distributor valve 200 may be employed and may be electrically driven including electrical operation of its valve member or members.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
EP81300343A 1981-01-26 1981-01-26 Brennkraftmaschine mit innerer Verbrennung Withdrawn EP0057300A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP81300343A EP0057300A1 (de) 1981-01-26 1981-01-26 Brennkraftmaschine mit innerer Verbrennung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP81300343A EP0057300A1 (de) 1981-01-26 1981-01-26 Brennkraftmaschine mit innerer Verbrennung

Publications (1)

Publication Number Publication Date
EP0057300A1 true EP0057300A1 (de) 1982-08-11

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EP81300343A Withdrawn EP0057300A1 (de) 1981-01-26 1981-01-26 Brennkraftmaschine mit innerer Verbrennung

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EP (1) EP0057300A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1007186A4 (fr) * 1993-06-24 1995-04-18 Balachoff Dimitri Moteur automobile de type ecologique avec pistons a courses variables.
WO1996033343A1 (en) * 1995-04-20 1996-10-24 Split Cycle Technology Limited Free piston engine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2541464A (en) * 1944-11-28 1951-02-13 Parker Appliance Co Fluid throttling valve
US2583115A (en) * 1950-05-24 1952-01-22 Baldwin Lima Hamilton Corp Control for free piston engines
DE909402C (de) * 1950-08-15 1954-04-15 Gerhard Michel Brennkraftmaschine mit stufen- und getriebeloser Kraftuebertragung mittels eines Flugkolben-Brennkraftverdichters eines Druckluftsammlers und einer angetriebenen Kreiselmaschine
US2849995A (en) * 1955-10-04 1958-09-02 Frank M Lewis Free piston machine operation
US2978986A (en) * 1956-09-28 1961-04-11 American Mach & Foundry Free piston engine
US3024591A (en) * 1958-12-23 1962-03-13 American Mach & Foundry Bounce compensator for free piston engines
US3119230A (en) * 1961-05-10 1964-01-28 Kosoff Harold Free piston engine system

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2541464A (en) * 1944-11-28 1951-02-13 Parker Appliance Co Fluid throttling valve
US2583115A (en) * 1950-05-24 1952-01-22 Baldwin Lima Hamilton Corp Control for free piston engines
DE909402C (de) * 1950-08-15 1954-04-15 Gerhard Michel Brennkraftmaschine mit stufen- und getriebeloser Kraftuebertragung mittels eines Flugkolben-Brennkraftverdichters eines Druckluftsammlers und einer angetriebenen Kreiselmaschine
US2849995A (en) * 1955-10-04 1958-09-02 Frank M Lewis Free piston machine operation
US2978986A (en) * 1956-09-28 1961-04-11 American Mach & Foundry Free piston engine
US3024591A (en) * 1958-12-23 1962-03-13 American Mach & Foundry Bounce compensator for free piston engines
US3119230A (en) * 1961-05-10 1964-01-28 Kosoff Harold Free piston engine system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE1007186A4 (fr) * 1993-06-24 1995-04-18 Balachoff Dimitri Moteur automobile de type ecologique avec pistons a courses variables.
WO1996033343A1 (en) * 1995-04-20 1996-10-24 Split Cycle Technology Limited Free piston engine
US6029616A (en) * 1995-04-20 2000-02-29 Split Cycle Technology Limited Free piston engine

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