EP0093732B1 - Einrichtung in einem drucksystem - Google Patents

Einrichtung in einem drucksystem Download PDF

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Publication number
EP0093732B1
EP0093732B1 EP82903224A EP82903224A EP0093732B1 EP 0093732 B1 EP0093732 B1 EP 0093732B1 EP 82903224 A EP82903224 A EP 82903224A EP 82903224 A EP82903224 A EP 82903224A EP 0093732 B1 EP0093732 B1 EP 0093732B1
Authority
EP
European Patent Office
Prior art keywords
piston
pump
cylinder unit
valves
annular groove
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
Application number
EP82903224A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0093732A1 (de
Inventor
Gerhard Brandl
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
Publication of EP0093732A1 publication Critical patent/EP0093732A1/de
Application granted granted Critical
Publication of EP0093732B1 publication Critical patent/EP0093732B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/05—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by internal-combustion engines
    • 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 invention relates to a device in a pressure system which has a cylinder-piston arrangement which is connected to a piston pump and has an oscillating piston, the cylinder of the pump being connected to a pressure accumulator and a substantially pressure-free reservoir of the pressure medium via positive-controlled valves, and the piston of the cylinder-piston arrangement is rigidly connected to at least one piston assigned to a pump.
  • Devices of this type are mostly used to convey pressure media from the storage container under pressure into the pressure accumulator, the pump usually being driven by an explosion motor.
  • the pump usually being driven by an explosion motor.
  • special cases e.g. B. if pressure from a pressure system is to be built up in another pressure system without there being a transfer of the pressure medium, it also happens that the cylinder-piston arrangement provided for driving the pump is acted upon by a pressure medium.
  • a device of the type mentioned was z. B. proposed by FR-A-2 306 384.
  • two pumps are controlled via a rotary slide valve which is driven by a hydraulic motor which acts as a metering device for metering the supply of pressure medium to the pumps, synchronization between the hydraulic motor, the rotary slide valve and the motor / pump system being provided.
  • a check valve is arranged in the line leading from the pumps to the pressure vessel, which prevents flow from the pressure vessel to the pumps.
  • DE-A-26 48 958 has disclosed a device in which one pump piston is rigidly connected to a piston of an explosion motor and each pump via a valve controlled by a regulator, which is controlled as a function of the conditions in the explosion motor, can be connected to a pressure vessel or can be shut off from it. Furthermore, each pump is connected to a high pressure tank via a check valve, which prevents flow from the high pressure tank to the pump. A throttle is still arranged in each connecting line of the pump.
  • the pistons of two pumps are acted upon by a pressure medium and drive the two pistons of the explosion motor against one another in order to achieve the corresponding compression.
  • the valve is switched over and the pump is separated from the pressure vessel.
  • the pistons of the pump are driven against their rest position and push out the pressure medium, which reaches the high pressure tank via the throttles and the check valve.
  • the aim of the invention is now to propose a device of the type mentioned at the outset which is distinguished by a simple structure and in which a separate starting device can nevertheless be dispensed with.
  • this is achieved in that the piston of each cylinder-piston arrangement is resiliently supported in both directions of movement to form an oscillatory system and the valves of the pump are controlled by a separate motor independently of the position of the piston relative to the associated cylinder of the cylinder-piston arrangement , wherein there is also no functional connection between the cylinder-piston arrangement and the engine and the valves of the pump are connected to the pressure accumulator or to the essentially pressure-free reservoir of the pressure medium by means of connections which can be flowed through in both flow directions.
  • valves or slide valves of the pump allows them to be used to start the explosion motor by actuating the valves in the same way as in normal operation and thus applying pressure medium coming from the pressure accumulator to the piston of the pump.
  • the pressure medium is pushed out of the pump cylinder by the spring action of the gas cushion compressed in the cylinder of the explosion engine, if an ignition occurs, by the action of the explosion in the cylinder of the engine.
  • the pistons are connected to each other by the application of pressure medium to the pump and the control of the valves the pump is excited to oscillate, the frequency of which is equal to the frequency of the positive control of the valves.
  • the z. B. can be formed by an explosion motor, when moving to a dead center to give energy to the spring, which may preferably be formed by a gas cushion, the piston is after reaching its dead center from the energy stored in the spring first in the accelerates in the opposite direction, so that, in contrast to the known solutions, there is an oscillatable system in which, since a flow from and to the pressure accumulator and to the pump is possible in both directions, a constant energy exchange between the pump and the single pressure accumulator is also possible. This ensures that the energy required to compress the explosion motor can be taken from the pressure accumulator and that the energy released by the explosion in the motor can be introduced into the pressure accumulator.
  • the ignition in the explosion engine can be carried out in the usual way either by auto-ignition when the critical pressure is reached or by spark ignition, the latter taking place in a known manner depending on the position of the piston.
  • valves are designed as rotary valves which are driven by a separate motor via a toothed belt drive or a toothed wheel gear.
  • the control of the valves of the pump takes place via a common cam disk and the tappet controlled by this, resulting in a very simple construction in which the mutual phase position of the valves always corresponds to the predetermined values.
  • this solution cannot lead to changes in the phase position when the speed of the drive of the valve control changes, as is the case with separate and, for. B. coupled via a belt or chain drive cam discs.
  • the piston of the cylinder-piston arrangement is connected to two pistons of two pumps via a straight rod, it being particularly advantageous if the pistons of the two pumps are connected to it by means of straight rods of the same design and projecting from both end faces of the piston of the cylinder-piston arrangement, and the inlet and outlet openings of the cylinder housing of the cylinder-piston arrangement are arranged in the central region thereof.
  • the gas exchange in the cylinder-piston arrangement designed as an explosion engine takes place by utilizing the gas vibrations in the intake and exhaust pipes in the manner that is customary in internal combustion engines, the intake and gas exchange ratios being able to be optimized in a simple manner due to the constant frequency of the piston oscillation is.
  • the gas exchange can also be supported by a blower.
  • the explosion can be caused by spark ignition, such as in a gasoline engine, by injecting fuel into the highly compressed air, such as in a diesel engine, or by blowing in combustible gas during the compression stroke and then igniting the combustible mixture thus formed as a result of the high temperature which arises during the compression.
  • a particularly preferred embodiment of a device according to the invention is characterized in that the rods serving to connect the pistons slide into the enclosing guides, each of which has a circumferential annular groove machined into its bore and a radially extending and axially annular groove connected to a fuel line has in the direction of the pump spaced bore, which optionally opens into a further annular groove and that each rod is provided with two axially spaced recesses, preferably circumferential grooves, which produce the connection from the annular groove to the combustion chamber of the cylinder-piston arrangement or from the annular groove to the bore connected to the fuel line at different positions of the piston of the cylinder-piston arrangement.
  • combustible gas can flow in through an annular gap which is formed by the annular groove of the rod connecting the pistons closer to the cylinder of the explosion motor, and opens briefly during the compression stroke in order to close the combustion chamber with the annular groove serving as the storage chamber to the bore of the guide connect, from which the flammable gas under pressure flows into the combustion chamber and mixes with the air there.
  • the combustible gas flows at the top dead center of the piston of the explosion motor through a second annular gap formed by the second annular groove of the piston rod into the annular groove of the bore in the guide.
  • the pressure of the combustible gas can be regulated with a suitable valve in order to be able to adapt the inflowing quantity and thus the output to the requirements.
  • the output can be regulated as a function of the pressure in the pressure accumulator in such a way that it increases as the pressure in the pressure accumulator falls and the pressure therefore remains essentially constant regardless of the removal of the pressure medium from the pressure accumulator.
  • Either gaseous fuel or vaporized liquid fuel can be used as the combustible gas.
  • the evaporation of liquid fuel can either be done by using the exhaust heat in a suitable, thermostatically controlled heat exchanger or by means of a whisk that converts mechanical energy into heat in a small chamber and thereby evaporates the fuel.
  • the whisk can expediently be driven by means of a hydraulic motor or a small turbine acted upon by the pressure accumulator.
  • the explosion engine 1 is designed as a two-stroke engine, in which the inlet opening 2 z. B. is connected to a carburetor, not shown.
  • a carburetor not shown.
  • an injection of fuel would also be possible, with the control of the injection taking place as a function of the position of the piston 3 of the explosion engine.
  • the piston 3 is designed as a flat piston, but a piston provided with a nose can of course also be used.
  • the usual piston rings have not been taken into account in the illustration for reasons of simplicity.
  • the exhaust opening 4 in the cylinder housing 5 is connected to conventional silencers or mufflers, not shown.
  • the piston 3 of the explosion motor 1 is connected by means of the rod 6 to the piston 7 of the pump 8, the cylinder housing 9 of which is axially aligned with the cylinder housing 5 of the explosion motor 1 and connected to the latter, possibly also being formed in one piece with respect to the housing halves.
  • the piston 7 of which could possibly also be formed by the rod 6 or its free end face two openings 12, 13 which can be closed by valves 10, 11 are arranged, which are connected via pipes 14, 15 to a reservoir 16 for the pressure medium or a pressure accumulator 17 are connected.
  • valves 10, 11 are pretensioned by the springs 18, 19 which hold the valves in the closed position.
  • the valves are controlled by means of the plungers 20, 21 which are held in contact with the cam disk 24 by the springs 22, 23, which in turn is driven by the motor 25.
  • the motor 25, which is preferably designed as an electric motor, has a device, not shown, which ensures that it comes to a standstill only in a certain position of the cam disk 24, in which the valve 11 is securely closed and the valve 10 is kept open.
  • a valve 26 is arranged in the pipeline 15, which closes as soon as the power supply to the motor 25 is interrupted.
  • a vent hole 26 is provided in the cylinder housing.
  • the pistons 3 and 7 are driven back very quickly and before the valve 11 is closed, as a result of which the medium in the cylinder housing 9 is pushed out via the valve 11 to the pressure accumulator 17.
  • the pistons 3, 7 are again driven forward, whereby pressure medium from the open valve 10 Storage container 16 is sucked.
  • the fuel mixture sucked in by the piston driven back by the previous explosion is compressed again and then brought to ignition.
  • a spring 27 is provided which urges the piston 7 to the right, so that it can in no case remain in the left extreme position, in which an automatic start using the print medium would be impossible.
  • a spring-loaded safety valve 28 is provided, which allows the pressure medium to flow off if, for example, B. comes to an explosion of fuel mixture in the cylinder housing 5 with simultaneously closed valves 10 and 11 of the pump 8.
  • the piston 3 of the explosion motor 1 is rigidly connected to the pump pistons 7, 7 'via the rods 6, 6'.
  • This piston arrangement is set in vibration by the pressure oil from the pressure container 17, since this flows into the cylinder housings 9, 9 'via the valves 11, 11', which are designed as rotary slide valves and are driven by a separate motor, not shown, and alternately onto the pump pistons 7, 7 'presses.
  • the cylinder housings 9, 9 ' are connected to the essentially unpressurized storage container 16 via the rotary slide valves which serve as valves 10, 10' and the liquid is ejected.
  • the gas cushions in the cylinder space 71, 71 ' serve as springs and support the alternately loaded pistons 7, 7' of the pumps 8, 8 '.
  • the annular groove 83 connected to a fuel line 82 via a radially extending bore 81 is connected through the annular groove 91 of the rod 6 to a storage chamber which is formed by an annular groove 100 of the guide 101 of the rod 6 and the combustible gas under pressure in the annular groove 83 flows through the annular groove 91 into the annular groove 100.
  • the annular groove 111 briefly connects the annular groove 100 serving as a storage chamber to the cylinder space 71 and the combustion Bare gas flows into this cylinder space 71 and mixes there with the combustion air. This gas mixture is now compressed and ignited.
  • the annular groove 111 After passing through a certain distance to the left, the annular groove 111 briefly connects the annular groove 100 of the guide 101 of the rod 6 serving as a storage chamber to the cylinder space 71 and the combustible gas flows into the latter and mixes with the combustion air pre-compressed there. This gas mixture is compressed further by the piston 3 moving to the left, the connection between the annular groove 100 and the left cylinder space 71 being closed again by the rod 6 before the left extreme position is reached. The compression of the gas mixture in the left cylinder chamber 71 leads to an explosion of the mixture in the area of the left extreme position of the piston arrangement.
  • the pressure of the combustible gas in the annular groove 83 is set with the regulating valve 130.
  • the combustible gas is produced by vaporizing liquid fuel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP82903224A 1981-11-16 1982-11-10 Einrichtung in einem drucksystem Expired EP0093732B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0494581A AT384658B (de) 1981-11-16 1981-11-16 Einrichtung in einem drucksystem
AT4945/81 1981-11-16

Publications (2)

Publication Number Publication Date
EP0093732A1 EP0093732A1 (de) 1983-11-16
EP0093732B1 true EP0093732B1 (de) 1986-04-16

Family

ID=3570188

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82903224A Expired EP0093732B1 (de) 1981-11-16 1982-11-10 Einrichtung in einem drucksystem

Country Status (10)

Country Link
US (1) US4620836A (it)
EP (1) EP0093732B1 (it)
JP (1) JPS58501954A (it)
AT (1) AT384658B (it)
BR (1) BR8207973A (it)
CA (1) CA1208494A (it)
DE (1) DE3270672D1 (it)
ES (1) ES517380A0 (it)
IT (2) IT8253928V0 (it)
WO (1) WO1983001816A1 (it)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19613080C1 (de) * 1996-04-02 1997-01-23 Waldemar Reimann Pumpe für Flüssigkeiten

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH659107A5 (de) * 1985-11-21 1986-12-31 Ernst Marcus Freikolben-brennkraftmaschine.
US5464331A (en) * 1993-11-09 1995-11-07 Sawyer; James K. Engine and power output
US5785505A (en) * 1996-10-21 1998-07-28 Caterpillar Inc. Integral fluid pump and internal combustion engine
DE59709502D1 (de) * 1997-06-03 2003-04-17 Thomas Handtmann Kolbenpumpe
US6314924B1 (en) 1999-02-22 2001-11-13 Caterpillar Inc. Method of operating a free piston internal combustion engine with a short bore/stroke ratio
DE10026728A1 (de) 1999-11-24 2001-05-31 Mannesmann Rexroth Ag Freikolbenmotor
JP2003524727A (ja) * 1999-11-24 2003-08-19 マネスマン レクソロート アクチェンゲゼルシャフト フリーピストン機関
US6461117B2 (en) * 2001-02-27 2002-10-08 International Truck Intellectual Property Company, L.L.C. Reversible volume oil pump
DE202005005916U1 (de) * 2005-04-12 2005-06-16 Lincoln Gmbh & Co. Kg Einleitungsschmiereinrichtung
US7740455B1 (en) * 2007-07-09 2010-06-22 Brian Nissen Pumping system with hydraulic pump
BR112012029260B1 (pt) * 2010-05-19 2021-02-02 Graco Minnesota Inc. montagem de bomba e método para ajuste do deslocamento de fluido de uma bomba de pistão
ES2721012T3 (es) 2012-12-18 2019-07-26 Emerson Climate Technologies Compresor alternativo con sistema de inyección de vapor
US20170130748A1 (en) * 2015-11-05 2017-05-11 Borgwarner Inc. Multi-output charging device

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USRE20254E (en) * 1937-01-26 h robertson
GB190900506A (en) * 1908-01-10 1909-06-03 Dagobert Timar Improvements in and relating to Apparatus for Supplying Gas and Liquids.
GB191109543A (en) * 1910-05-10 1912-03-28 Louis Francois Bellot Improvements in or connected with Piston Pumps.
GB277121A (en) * 1924-05-20 1927-09-12 Axel Uno Sture Danielsson Improvements in or relating to fuel distributing devices for multi-cylinder engines
US2454138A (en) * 1944-10-25 1948-11-16 Delzer Reinhold Engine driven pump
FR993920A (fr) * 1944-11-13 1951-11-08 Système de transmission de puissance à partir de mouvement à course rectilligne alternative
US2754654A (en) * 1951-12-28 1956-07-17 Alan Muntz & Co Ltd Starting of internal-combustion-operated free-piston engines
US2914909A (en) * 1957-03-18 1959-12-01 John T Kubik Pump and turbine hydraulic transmission driven by an internal combustion engine having starter means therefor
US3024591A (en) * 1958-12-23 1962-03-13 American Mach & Foundry Bounce compensator for free piston engines
FR1222707A (fr) * 1959-01-19 1960-06-13 Système de distribution pour pompe à pistons
CH400777A (de) * 1960-08-12 1965-10-15 Breinlich Richard Dr Pumpvorrichtung mit Brennkraftantrieb zur Förderung eines hydraulischen Fluidums
US3065703A (en) * 1960-11-03 1962-11-27 Int Harvester Co Free piston engine pump
CH430626A (de) * 1964-05-21 1967-02-15 Thum Helmut Regelbarer Hydraulik-Axialkolbenmotor
BE672028A (it) * 1964-11-25
US3995974A (en) * 1974-09-18 1976-12-07 Herron Allen R Internal combustion assisted hydraulic engine
IL46964A (en) * 1975-03-30 1977-06-30 Technion Res & Dev Foundation Hydrostatic relay system
DE2648958C2 (de) * 1976-10-28 1983-02-17 Karl-Heinz 8722 Sennfeld Fengler Hydraulische Kolbenpumpe mit Antrieb durch Freikolben-Verbrennungskraftmaschine
DE2849048A1 (de) * 1978-11-11 1980-05-14 Gutehoffnungshuette Sterkrade Zwangssteuerungssystem fuer kolbenverdichter-ventile

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19613080C1 (de) * 1996-04-02 1997-01-23 Waldemar Reimann Pumpe für Flüssigkeiten

Also Published As

Publication number Publication date
ES8400803A1 (es) 1983-11-01
IT1191228B (it) 1988-02-24
BR8207973A (pt) 1983-10-04
JPS58501954A (ja) 1983-11-17
IT8268335A0 (it) 1982-11-15
ES517380A0 (es) 1983-11-01
IT8253928V0 (it) 1982-11-15
US4620836A (en) 1986-11-04
ATA494581A (de) 1987-05-15
CA1208494A (en) 1986-07-29
EP0093732A1 (de) 1983-11-16
AT384658B (de) 1987-12-28
WO1983001816A1 (en) 1983-05-26
DE3270672D1 (en) 1986-05-22

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