EP0093732A1 - Dispositif pour un systeme de pression. - Google Patents

Dispositif pour un systeme de pression.

Info

Publication number
EP0093732A1
EP0093732A1 EP82903224A EP82903224A EP0093732A1 EP 0093732 A1 EP0093732 A1 EP 0093732A1 EP 82903224 A EP82903224 A EP 82903224A EP 82903224 A EP82903224 A EP 82903224A EP 0093732 A1 EP0093732 A1 EP 0093732A1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
pump
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.)
Granted
Application number
EP82903224A
Other languages
German (de)
English (en)
Other versions
EP0093732B1 (fr
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/fr
Application granted granted Critical
Publication of EP0093732B1 publication Critical patent/EP0093732B1/fr
Expired legal-status Critical Current

Links

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 an apparatus in a printing system, which preferably is a connected to a piston pump, a reciprocating piston having cylinder Kblbenanssen, an explosion engine, wherein the cylinder of the pump • via valves or slide with a Druck ⁇ memory and is connected to an essentially unpressurized storage container of the pressure medium.
  • Devices of this type are mostly used to convey pressure media from the storage container under pressure into the pressure accumulator, the pump being usually driven by an explosion motor.
  • the pump being usually driven by an explosion motor.
  • a pressure medium is applied to the cylinder-piston arrangement provided for driving the pump .
  • the piston of the pump is driven via an eccentric shaft and a connecting rod, the eccentric disk being operated via a crankshaft and Connecting rod and possibly a gear is driven by the piston of the cylinder-piston arrangement.
  • the valves of the pump are pressure-controlled or, as a rotary slide valve, are controlled as a function of the position of the piston of the pump.
  • the aim of the invention is now to propose a device of the type mentioned, which is characterized by a simple structure and which can be dispensed with in any case on a separate starting device.
  • the piston of the cylinder-piston arrangement is rigidly connected to at least one piston assigned to a pump and the valves of the pump, which are formed by slides, are positively controlled, the drive of the positive control of the valves being controlled by one of the Cylinder-piston arrangement independent independent motor.
  • valves or slide valves of the pump allows them to be used to start the explosion engine by controlling 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 motor if ignition occurs. by the effect of the explosion in the cylinder of the engine.
  • the pistons connected to one another are excited to an oscillation by the application of pressure medium to the pump and the control of the valves of the pump, the frequency of which is equal to the frequency of the positive control of the valves.
  • 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 a tappet controlled by this, which results in a very simple construction in which the mutual phase position of the valves always corresponds to the predetermined values corresponds.
  • this solution cannot change the phase position when the speed of the drive of the valve control changes, as is the case with separate and e.g. coupled via a belt or chain drive would be possible.
  • the piston of the cylinder-piston arrangement is connected to two pistons of two pumps via a straight rod, it being particularly advantageous when the pistons of the two pumps are connected to it by 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 catfish, as is common in internal combustion engines, the optimization of the piston vibration in a simple manner due to the constant frequency of the piston vibration Suction and gas exchange ratio is possible.
  • the gas change can also be supported by a fan.
  • the explosion can be brought about by " spark ignition as in the gasoline engine, by injecting fuel into the highly compressed air as in the diesel engine, or by blowing in combustible gas during the compression stroke and then igniting the combustible mixture formed in this way as a result of the high temperature arising during the compression .
  • a particularly preferred embodiment of a device according to the invention is characterized in that the slide for connecting the pistons serve enStangen in which enclose denFroundungen of which has auf ⁇ each one incorporated in the prepared holes, circumferential annular groove and an associated, radially extending and down spaced apart from the ring • nut 'axially in the direction to the pump bore pipe at a force , the given all opens into a further annular groove and that each rod with two axially spaced recesses, preferably circumferential. Grooves are provided which, at different positions of the piston of the cylinder-piston arrangement, 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.
  • 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 around the combustion chamber with the annular groove serving as a storage chamber connect the bore of the guide, from which the pressurized flammable gas located there flows into the combustion chamber and mixes with the air there.
  • the combustible gas flows through the top dead center of the piston of the explosion engine.
  • the combustible gas can with an appropriate valve, the pressure to be regulated to the inflowing amount and thus' to be able to adjust the power 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 thus remains essentially constant regardless of the pressure medium being removed from the pressure accumulator.
  • Either gaseous fuel or vaporized liquid fuel can be used as the combustible gas.
  • the evaporation of liquid fuel can take place either by utilizing the exhaust heat in a suitable, thermostatically controlled heat exchanger or by means of a whisk, which 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.
  • Figure 1 shows an embodiment with only one
  • Figure 2 one with two pumps per cylinder of an explosion engine.
  • the ' explosion engine 1 ' is designed as a two-stroke engine, in which the inlet opening 2 is connected, for example, to a carburetor, not shown.
  • fuel injection would also be possible, the injection being controlled as a function of the position of the piston 3 of the explosion engine, although the piston 3 is designed as a flat piston, a piston provided with a nose can, of course, also be used, and since this is not part of the invention, the usual piston rings are included the representation has been disregarded for the sake of simplicity.
  • the exhaust port 4 in the cylinder housing 5 is verbun ⁇ with conventional silencers or • pfen not shown 'Auspufft the.
  • the piston 7 'of which could possibly also be formed by the rod 6 or its free end face, there are two openings 12, 13 which can be closed by valves 10, 11 and which are connected by pipes 14, 15 10 are connected to a reservoir 16 for the pressure medium or a pressure accumulator 17. '
  • valves 10,11 are under bias of the springs 18, '19, which hold the valves in the closed position.
  • valve 20 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. Furthermore, 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 subsequent gas cushion which acts as a spring and is locked in by the compression of the gas cushion between the rear side 31 of the piston 3 and the end face of the cylinder housing 5 facing it, the pistons 3, 7 are again propelled forward, as a result of which the valve opens 10 pressure medium is sucked from the reservoir 16.
  • the fuel mixture sucked in by the piston driven back by the previous explosion is compressed again and then brought to ignition.
  • the piston 3 of the explosion motor 1 is rigidly connected to the pump pistons 2,2 'via the rods 6,6'. These piston Order is caused to oscillate 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 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 i.10 serving as valves 10, 10 'and the liquid is ejected.
  • the gas cushions in the cylinder space 71, 71 ' serve as springs and support the pistons 7, 7' of the pumps 8, 8 ', which are acted upon alternately.
  • the annular groove 83 which is 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 in the guide 101 of the rod 6 is formed and the flammable gas under pressure in the annular groove 83 flows through the annular groove 91 into the annular groove 100.
  • the annular groove temporarily connects the annular groove 100 serving as a storage chamber with the cylinder space 71 and the combustible 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 precompressed there. This gas mixture is further compressed by the piston 3 moving to the left, the connection between the annular groove 100 and the left cylinder chamber 71 being closed again by the rod 6 before the left extreme position is reached. • by the compression of the gas mixture in the left cylinder chamber 71 occurs in the region of the left extreme location of the piston assembly to explode the mixture.
  • the annular groove 83' connected to a fuel line 82 via a radially extending bore 81 ' is connected to the supply chamber by the annular groove 91' of the rod ' 6' which is formed by an annular groove 100 'of the guide 101' of the rod 6 1 and in the annular groove 83 'below. Flammable gas under pressure flows through the annular groove 91 'into the annular groove 100'. From there, when the piston 3 approaches its right extreme position, it reaches the cylinder space 71 'via the annular groove 111'.
  • 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, for which purpose a drive e.g. A whirl 200 provided with a hydraulic turbine 201 is provided, the evaporation being achieved by the mechanical energy introduced into the liquid and the throwing out of small liquid particles.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Une machine volumétrique, en particulier un moteur à explosion, comprend un piston oscillant relié à une pompe à piston. Le cylindre de la pompe est relié par l'intermédiaire de soupapes à un accumulateur de pression et à un réservoir essentiellement sans pression pour le gaz à comprimer. Le piston (3) du moteur (1) est solidaire d'au moins un piston (7) d'une pompe (8). Les soupapes (10, 11) de la pompe (8) qui sont constituées éventuellement de tiroirs, sont actionnées desmodromiquement par un moteur séparé (25) indépendant.
EP82903224A 1981-11-16 1982-11-10 Dispositif pour un systeme de pression Expired EP0093732B1 (fr)

Applications Claiming Priority (2)

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

Publications (2)

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

Family

ID=3570188

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82903224A Expired EP0093732B1 (fr) 1981-11-16 1982-11-10 Dispositif pour un systeme de pression

Country Status (10)

Country Link
US (1) US4620836A (fr)
EP (1) EP0093732B1 (fr)
JP (1) JPS58501954A (fr)
AT (1) AT384658B (fr)
BR (1) BR8207973A (fr)
CA (1) CA1208494A (fr)
DE (1) DE3270672D1 (fr)
ES (1) ES517380A0 (fr)
IT (2) IT1191228B (fr)
WO (1) WO1983001816A1 (fr)

Families Citing this family (14)

* 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
DE19613080C1 (de) * 1996-04-02 1997-01-23 Waldemar Reimann Pumpe für Flüssigkeiten
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
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
DE10026728A1 (de) 1999-11-24 2001-05-31 Mannesmann Rexroth Ag Freikolbenmotor
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
CN102971534B (zh) 2010-05-19 2015-12-16 格瑞克明尼苏达有限公司 用于可调节活塞泵的可移除垫片夹
WO2014100156A1 (fr) * 2012-12-18 2014-06-26 Emerson Climate Technologies, Inc. Compresseur à mouvement de va-et-vient avec système d'injection de vapeur
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 (fr) * 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

Non-Patent Citations (1)

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Title
See references of WO8301816A1 *

Also Published As

Publication number Publication date
IT1191228B (it) 1988-02-24
US4620836A (en) 1986-11-04
AT384658B (de) 1987-12-28
JPS58501954A (ja) 1983-11-17
ATA494581A (de) 1987-05-15
WO1983001816A1 (fr) 1983-05-26
ES8400803A1 (es) 1983-11-01
ES517380A0 (es) 1983-11-01
IT8253928V0 (it) 1982-11-15
IT8268335A0 (it) 1982-11-15
CA1208494A (fr) 1986-07-29
BR8207973A (pt) 1983-10-04
DE3270672D1 (en) 1986-05-22
EP0093732B1 (fr) 1986-04-16

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