EP2602470A2 - Internal combustion engine with a fuel system - Google Patents
Internal combustion engine with a fuel system Download PDFInfo
- Publication number
- EP2602470A2 EP2602470A2 EP12008126.0A EP12008126A EP2602470A2 EP 2602470 A2 EP2602470 A2 EP 2602470A2 EP 12008126 A EP12008126 A EP 12008126A EP 2602470 A2 EP2602470 A2 EP 2602470A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel
- valve
- internal combustion
- combustion engine
- pressure
- 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
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 213
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 73
- 239000002828 fuel tank Substances 0.000 claims abstract description 23
- 238000013016 damping Methods 0.000 description 8
- 238000011144 upstream manufacturing Methods 0.000 description 7
- 230000015572 biosynthetic process Effects 0.000 description 6
- 239000007789 gas Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000005086 pumping Methods 0.000 description 4
- 238000011010 flushing procedure Methods 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 239000012528 membrane Substances 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000010926 purge Methods 0.000 description 2
- 230000036962 time dependent Effects 0.000 description 2
- 230000003213 activating effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
Images
Classifications
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- 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
- F02B15/00—Engines characterised by the method of introducing liquid fuel into cylinders and not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M1/00—Carburettors with means for facilitating engine's starting or its idling below operational temperatures
- F02M1/16—Other means for enriching fuel-air mixture during starting; Priming cups; using different fuels for starting and normal operation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
- F02M37/0023—Valves in the fuel supply and return system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
- F02M37/0023—Valves in the fuel supply and return system
- F02M37/0029—Pressure regulator in the low pressure fuel system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0047—Layout or arrangement of systems for feeding fuel
- F02M37/007—Layout or arrangement of systems for feeding fuel characterised by its use in vehicles, in stationary plants or in small engines, e.g. hand held tools
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/04—Feeding by means of driven pumps
- F02M37/16—Feeding by means of driven pumps characterised by provision of personally-, e.g. manually-, operated pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/04—Feeding by means of driven pumps
- F02M37/18—Feeding by means of driven pumps characterised by provision of main and auxiliary pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/20—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines characterised by means for preventing vapour lock
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
- F02M69/10—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel peculiar to scavenged two-stroke engines, e.g. injecting into crankcase-pump chamber
Definitions
- the invention relates to an internal combustion engine with a fuel system of the type specified in the preamble of claim 1.
- the invention has for its object to provide an internal combustion engine with a fuel system of the generic type, in which a good starting of the internal combustion engine is achieved.
- vapor bubbles in fuel systems with a fuel valve, the formation of vapor bubbles in the fuel system and in the injection valve can make it very difficult or impossible to start the internal combustion engine.
- the formation of vapor bubbles is particularly problematic in fuel systems that operate at very low pressure, which may for example be only one or more tenths bar or a few bar above the ambient pressure.
- the pressure in such a fuel system may be, for example, about 100 mbar above ambient pressure. If the fuel valve heats up too much, vapor bubbles may form in the fuel valve.
- the formation of vapor bubbles is particularly problematic when the engine is turned off and nachloomt, since then no promotion of cooling air more.
- the feed pump is arranged in a supply line to the fuel chamber of the fuel valve and promotes the fuel into the fuel chamber of the fuel valve.
- the fuel space is connected to a relief line in which a first valve is arranged. The fact that the fuel space of the fuel valve is purged, it is ensured that steam bubbles are flushed out in the fuel valve. At the same time, flushing the fuel valve with fuel easily achieves effective cooling of the fuel valve which prevents re-vaporization.
- a desired pressure in the fuel system can be maintained via the first valve, which is arranged in the discharge line.
- a purging of the fuel chamber in the injection valve can be provided at a considerably higher pressure than the operating pressure in the fuel system.
- an effective rinsing of possibly present in the fuel chamber gas bubbles is possible and a new vapor bubble formation can be prevented.
- a simple structure results when the supply line in which the feed pump is arranged in the flow path from a pump chamber of the fuel pump to the fuel chamber.
- the feed pump can therefore be arranged in an already existing supply line of the fuel system.
- a pressure regulator is arranged downstream of the fuel pump.
- the supply line, in which the feed pump is arranged connects a control chamber of the pressure regulator with the fuel chamber.
- the pressure regulator for limiting the pressure applied to the pump for flushing the fuel valve pressure does not limit, so that via the feed pump, a significantly higher fuel pressure can be generated in the fuel system than the usually prevailing in operation fuel pressure.
- the supply line is a bypass line to the fuel pump and connects the fuel tank with the fuel chamber. Due to the arrangement of the fuel pump in a bypass line to the fuel pump, the spatial arrangement of the feed pump relative to the fuel pump and the internal combustion engine can be chosen relatively freely.
- the first valve is actuated in response to a pressure, so it is opened or closed depending on the pressure.
- the pressure above which the first valve opens is advantageously higher than the operating pressure in the fuel system.
- a limited overpressure in the fuel system relative to the normal operating pressure can be established via the feed pump. This prevents a new vapor bubble formation in the fuel valve or fuel system.
- the valve can open in particular as a function of the pressure in the fuel chamber or as a function of the differential pressure between the fuel chamber and the fuel tank.
- the valve is actuated as a function of a temperature.
- the temperature may be, for example, a temperature of the fuel valve or the internal combustion engine.
- the valve opens or closes as a function of the rotational speed of the internal combustion engine. It is particularly provided that the valve is closed above a predetermined speed, so that the first valve is closed in normal operation and is open only during the startup process. It may also be provided that the first valve is detected at the first Combustion is closed. The first combustion can be detected, for example, based on the rotational speed of the internal combustion engine. The speed at which the valve is closed may be a speed that is reached as soon as the engine is started, but which is below the idle speed of the engine. Alternatively or additionally, it may be provided that the valve is actuated in a time-controlled manner.
- the first valve closes advantageous after the expiration of a predetermined period of time, which may for example correspond to the time for one or more Anwerfhübe. This flushes the fuel system during the startup process.
- a predetermined period of time which may for example correspond to the time for one or more Anwerfhübe. This flushes the fuel system during the startup process.
- the different parameters for actuating the first valve can be suitably combined.
- valve is a pressure relief valve opening in the relief direction.
- the pressure-holding valve operates mechanically, so that no further devices are necessary for controlling the pressure-holding valve.
- the first valve opens only in the discharge direction and in the opposite direction to the discharge direction, ie in the flow direction from the fuel tank to the fuel chamber, opening in the opposite direction is prevented, for example, when in the fuel tank, a higher pressure than in the fuel chamber. This is particularly the case with fuel systems in which the fuel tank is pressurized.
- the first valve is an electrically operated valve.
- the internal combustion engine has in particular a control device which actuates the first valve.
- a second valve is arranged in a bypass line to the first valve.
- the second valve is a pressure-holding valve, while the first valve is an electrically operated valve. Via the pressure-maintaining valve arranged in the bypass line, it is possible to ensure that the pressure in the fuel system does not increase inadmissibly, independently of the parameters used to actuate the first valve.
- the feed pump can be manually driven, mechanically driven, electrically driven or pneumatically driven.
- the mechanical drive is advantageously via the internal combustion engine.
- the pneumatic drive is advantageously carried out via the fluctuating pressure in the internal combustion engine, in particular in a crankcase of the internal combustion engine.
- Fig. 1 shows an embodiment of a hand-held implement a cut-off machine 1.
- the fuel system according to the invention in other hand-held implements such as brushcutters, chainsaws, blowers or the like. Can be used.
- the cut-off machine 1 has a housing 2, in which an internal combustion engine 12 is arranged. On the housing 2, a boom 3 is set, at the free end of a blade 4 is mounted. The cutting disc 4 is partially covered by a protective cover 5. The cutting disk 4 is driven in rotation by the internal combustion engine 12.
- An upper handle 6 and a handle tube 7 are used to guide the abrasive cutter 1.
- the handle tube 7 engages over the housing 2 on the front side facing the cutting disc 4.
- the upper handle 6 is formed on a hood 8 of the housing 2.
- a throttle lever 10 and a throttle lock 11 are pivotally mounted.
- an air filter cover 9 is arranged.
- the abrasive grinder 1 has a plurality of feet 13, with which the grinder 1 can be placed on a base.
- Fig. 2 shows the internal combustion engine 12 in detail.
- the internal combustion engine 12 is a single-cylinder engine and designed in the embodiment as a two-stroke engine.
- the internal combustion engine 12 has a crankcase 14, in which a crankshaft 80 is rotatably mounted about an axis of rotation 15.
- a cylinder 16 is fixed, in which a in Fig. 2 schematically shown piston 21 is reciprocally mounted in the direction of a cylinder longitudinal axis 29.
- the piston 21 rotatably drives the crankshaft 80 via a connecting rod, not shown.
- the piston 21 defines a combustion chamber 22 formed in the cylinder 16.
- the internal combustion engine 12 has an intake passage 30, which opens with an inlet 17 on the cylinder 16.
- the inlet 17 is slit-controlled by the piston 21 and opened in the region of the top dead center of the piston 21 to the crankcase interior 31. To the combustion chamber 22, the inlet 17 is always closed. A portion of the intake passage 30 is guided in a throttle body 27, in which a throttle element, in the embodiment, a pivotally mounted throttle valve 28, is arranged. The throttle valve 28 is actuated by the throttle lever 10 and serves to control the amount of supplied combustion air.
- a holder 24 is fixed, which has a receptacle 25 for the in Fig. 5 shown fuel valve 26 has.
- the holder 24 has a fuel channel 61, via which the fuel metered by the fuel valve 26 is supplied to the crankcase interior 31.
- the holder 24 is partially enclosed by an air guide member 83 which directs air from a fan housing to the holder 24 and so to cool the fuel valve 26 contributes.
- the crankcase 14 also has a mounting opening 23, in which a sensor, in particular a pressure sensor, a temperature sensor or a combined pressure-temperature sensor can be arranged.
- the crankcase interior 31 is connected to the combustion chamber 22 in the region of the bottom dead center of the piston 21 via at least one overflow channel 19.
- a single overflow 19 is provided, which is divided into several branches and opens with several overflow windows 20 into the combustion chamber 22.
- the transfer ports 20 are slit-controlled by the piston 21 and opened in the region of the bottom dead center of the piston 21. From the combustion chamber 22, an outlet 18, likewise slit-controlled by the piston 21, leads.
- combustion air is supplied into the crankcase interior 31 via the intake passage 30.
- the fuel / air mixture formed in the crankcase interior 31 flows in the region of the bottom dead center of the piston 21 via the or the overflow 19 in the combustion chamber 22 a.
- the fuel / air mixture is compressed in the combustion chamber 22 and ignited in the region of top dead center of the piston 21 by a spark plug, not shown. Due to the combustion in the combustion chamber 22, the piston 21 is accelerated in the direction of its bottom dead center.
- the outlet 18 is opened by the piston 21, the exhaust gases flow out of the combustion chamber 22 via the outlet 18.
- fresh air / fuel mixture flows out of the crankcase interior 31 via the overflow windows 20.
- FIG. 3 an exhaust muffler 82 is arranged on the internal combustion engine 12 into which the exhaust gases flow via the outlet 18.
- Fig. 3 also shows the arrangement of the air guide member 83 on the crankcase 14.
- the air guide member 83 is disposed immediately below an inlet stub 84 of the engine 12. In the inlet port of the intake passage 30 is guided to the inlet 17.
- Fig. 3 Also shows, has the power grinder 1 a tank housing 81, which is separated from the engine 12 via a vibration gap 85.
- the oscillation gap 85 is from an in Fig. 3 not shown elastic intake manifold bridged, in which the intake passage 30 is guided over the vibration gap 30.
- the vibration gap 85 is also bridged by a plurality of anti-vibration elements, which are also not shown.
- a fuel tank 32 is formed in the tank housing 81 a fuel tank 32 is formed.
- a pump housing 51 of a fuel pump 34 (FIG. Fig. 4 ) held.
- a feed pump 69 is integrated, which is designed as a manual feed pump and which has a pump bellows 77 which is to be operated by the operator.
- the pumping bellows 77 protrudes from the housing 2 so that it is easily accessible by the operator.
- the engine 12 has a controller 78 which controls the fuel valve 26, namely, the amount of fuel to be supplied and the timing when the amount of fuel is to be supplied.
- the controller 78 also controls the ignition timing.
- Other electrical components of the abrasive grinder 1 can be controlled by the controller 78.
- Fig. 4 schematically shows the fuel system of the internal combustion engine 12.
- a suction head 33 which is connected via a fuel line 68 with the fuel pump 34 formed in the pump housing 51.
- the fuel pump 34 sucks fuel via a suction valve 37 into a pump chamber 38.
- the pump chamber 38 is delimited by a pump diaphragm 39 whose rear side is connected to the crankcase interior 31 via an impulse line 40. Due to the fluctuating pressure in the crankcase interior 31, which results from the reciprocating motion of the piston 21, the pump diaphragm 39 is moved, thereby delivering fuel to a pressure valve 41.
- the suction valve 37 and the pressure valve 41 are formed as check valves.
- the fuel passes into a storage space 52, which is connected via an inlet valve 42 to a control chamber 43 of a pressure regulator 35.
- the pressure regulator 35 is formed in the pump housing 51. However, it may also be provided a separate housing for the pressure regulator 35.
- the inlet valve 42 has a valve needle 86, which via a lever 45 with a control chamber 43 limiting Regulating membrane 44 is connected.
- a rear space 47 is formed on the side of the control diaphragm 44 facing away from the control chamber 43.
- the control membrane 44 may, as shown in the embodiment, be biased by a spring 46.
- the spring 46 is advantageously designed as a compression spring and arranged in the rear space 47.
- the rear space 47 is advantageously acted upon via an opening 48 with a reference pressure.
- the reference pressure is advantageously the ambient pressure. If the pressure in the control chamber 43 is lower than the desired pressure of the fuel system, the control diaphragm 44 is deflected in the direction of the control chamber 43 and thereby opens via the lever 45, the inlet valve 42. The pressure rises to the on the spring stiffness of the control diaphragm 44th and the spring 46 set pressure of the fuel system, the control diaphragm 44 is returned to its initial position, thereby closing the inlet valve 42.
- the control chamber 43 is connected via a feed line 50 with a damping chamber 53 of a pressure damper 36.
- the control chamber 43 may also be connected via the supply line 50 directly to the fuel valve 26.
- the fuel enters via a arranged in the control chamber 43 fuel strainer 49 in the supply line 50 a.
- the pressure damper 36 has a damping diaphragm 54, which limits the damping chamber 53.
- a rear space 56 is formed, in which a spring 55 is arranged.
- the spring 55 biases the damping membrane 54 in the desired position.
- the damping diaphragm 54 can also be held in the desired position due to its inherent elasticity.
- the rear space 56 is acted upon via an opening 57 with a reference pressure.
- the reference pressure is advantageously the ambient pressure.
- the supply line 50 passes through the pressure damper 36 to the fuel valve 26th
- the fuel valve 26 is connected to the fuel tank 32 via a relief line 58.
- a first valve 73 is arranged, which is formed in the embodiment as a mechanically acting pressure relief valve.
- the first valve 73 has a valve member which is acted upon by a spring. If the pressure upstream of the first valve 73 increases above a predetermined pressure, this opens first valve 73.
- the first valve 73 opens when the pressure difference between the fuel valve 26 and the fuel tank 32 exceeds a constructively predetermined value, which is defined by the spring of the first valve 73. If the pressure in the fuel tank 32 is greater than the pressure in the fuel valve 26, the first valve 73 remains closed. This may be the case when the fuel tank 32 is pressurized.
- the first valve 73 thus blocks in the flow direction from the fuel tank 32 to the fuel valve 26. A flow of fuel from the fuel tank 32 to the fuel valve 26 is thereby prevented.
- the fuel system has the feed pump 69, which is arranged in the feed line 50 downstream of the control chamber 43 and upstream of the pressure damper 36.
- the terms “downstream” and “upstream” refer to the flow direction of the fuel in the fuel system.
- the feed pump 69 is manually operated by the operator.
- the feed pump 69 has the in Fig. 3
- the interior of the pumping bellows 77 is connected to the supply line 50 via an inlet valve 74.
- the pump bellows 77 can also be connected directly to the control chamber 43 via the inlet valve 74.
- the inlet valve 74 opens in the flow direction to the pump bellows.
- the feed pump 69 has an outlet valve 75, which is arranged between the pump bellows 77 and the feed line 50 and which opens in the flow direction from the pump bellows to the feed line 50.
- the flow path in which the inlet valve 74 is arranged branches off from the supply line 50 upstream of a check valve 76, and the flow path in which the outlet valve 75 is arranged opens into the supply line 50 downstream of the check valve 76.
- the pump bellows 77 thereby bypasses
- the nonreturn valve 76 opens in the flow direction from the control chamber 43 to the pressure damper 36.
- the check valve 76 ensures that pumped via the feed pump 69, pressurized fuel from the supply line 50 can not flow back into the control chamber 43.
- Fig. 5 shows the configuration of the holder 24, the pressure damper 36 and the fuel valve 26 in detail.
- the supply line 50 is partially bounded by the damping diaphragm 54 of the pressure damper 36.
- the rear space 56 of the pressure damper 36th has one or more connection openings 63 which connect different areas of the rear space 56 with each other.
- the opening 57 is covered by a cover 64, which is designed to be permeable to air.
- the cover 64 is advantageously a screen, in particular a sintered metal screen.
- the fuel valve 26 has a housing 67 in which a fuel chamber 62 is formed.
- the fuel chamber 62 has a metering orifice 87, which is opened and closed by the fuel valve 26, which is designed as an electromagnetic valve, and which connects the fuel chamber 62 with the fuel channel 61 in the holder 24, which opens into the crankcase interior 31.
- the holder 24 has a seal 65 which seals the holder 24 relative to the crankcase 14.
- the fuel passes through an inlet opening 66 in the fuel chamber 62 in the housing 67.
- the inlet opening 66 is located in front of the cutting plane in Fig. 5 and is therefore shown in dashed lines.
- the connection opening of the fuel chamber 62 with the discharge line 58 is not in the cutting plane. This connection opening is not shown.
- the pump 69 Before starting the internal combustion engine 12, the pump 69 is advantageously actuated by the operator by compressing the pump bellows 77 several times. As a result, the feed pump 69 presses fuel via the supply line 50 into the fuel chamber 62 of the fuel valve 26. As soon as the pressure difference upstream from the first valve 73 and upstream of the valve 73, ie between the fuel chamber 62 and the fuel tank 32, is reached, the valve 73 and opens The fuel flows via the discharge line 58 back into the fuel tank 32. The feed pump 69 sucks fuel via the control chamber 43 of the pressure regulator 35 and the fuel pump 34 from the fuel tank 32 at. The funded via the feed pump 69 fuel flushes the fuel system.
- the fuel pump 34 and the pressure regulator 35 are, like the Fig. 3 shows, arranged at a relatively great distance from the engine 12, so that excessive heating and thus vapor bubble formation is avoided in these components.
- Fig. 6 shows an embodiment of a fuel system in which instead of the manually operated feed pump 69, an electrically operated feed pump 59 is provided.
- the feed pump 59 is connected to a power source 88, which may be, for example, a battery or a rechargeable battery of the cutting grinder 1, a generator driven by the internal combustion engine 12, or another source of power supplied by the engine 12.
- the feed pump 59 is controlled by the control device 78 of the internal combustion engine 12.
- the control device 78 can control the operation of the feed pump 59, for example as a function of a pressure or a pressure difference, depending on a temperature, for example the temperature of the fuel valve 26 or the internal combustion engine 12, depending on the rotational speed of the engine 12 or time-dependent so that the feed pump 59 over a predetermined period of time from the startup of the engine 12 is running. It can be provided that the delivery pump 59 reacts to a pressure or a temperature in a time-dependent manner. A combination of the mentioned parameters can be used to control the feed pump 59. In normal operation, ie after the starting process, after the warm-up of the internal combustion engine 12, after a predetermined operating time or the like., The first valve 60 is advantageously closed. The first valve 60 can also be closed, for example, when the first combustion of the internal combustion engine 12 is detected after the start, for example by evaluating the speed curve of the internal combustion engine 12.
- a first valve 60 which is an electrically operated valve.
- the valve 60 is advantageously also controlled by the control device 78.
- the valve 60 can be controlled as a function of a pressure, in particular as a function of the pressure in the fuel chamber 62 or in the feed line 50.
- the valve 60 may also be controlled as a function of the pressure difference between the fuel chamber 62 and the fuel chamber 32.
- the first valve 60 advantageously opens when a predetermined pressure or a predetermined pressure difference is exceeded, so that the fuel pressure in the fuel system is limited.
- a control in dependence of a temperature, in particular the temperature of the fuel valve 26 can be provided.
- valve 60 closes when the fuel valve 26 has fallen below a predetermined temperature. This may be the case, for example, if the fuel valve 26 has been sufficiently cooled by flushing with fuel. It can also be provided to close or open the valve 60 as a function of the rotational speed of the internal combustion engine and / or time-controlled.
- the feed pump 59 advantageously operates when the internal combustion engine 12 is put into operation, that is to say when starting, in order to remove vapor bubbles formed in the fuel system, in particular in the fuel chamber 62 of the fuel valve 26. When starting while the feed pump 59 is advantageously in operation and the first valve 60 is open. In operation, the feed pump 59 is then turned off and the first valve 60 is closed.
- the feed pump 59 and the valve 60 can also be used to flush the fuel valve 26 during operation.
- the valve 60 is advantageously opened so that the fuel system is flushed with the fuel pumped by the fuel pump 34.
- the feed pump 59 may additionally be put into operation to assist the fluctuating crankcase pressure driven fuel pump 34 when the fuel flow rate through the valve 60 exceeds the delivery rate of the fuel pump 34.
- Fig. 7 are also an electrically actuated feed pump 59 and an electrically operated first valve 60 is provided.
- the feed pump 59 and the valve 60 may, as in Fig. 6 shown by the in Fig. 7 Control device 78, not shown, may be controlled.
- the feed pump 59 is in the embodiment according to Fig. 7 arranged in a supply line 72 which connects the fuel tank 32 with the fuel chamber 62 in the fuel valve 26.
- the supply line 72 thus represents a bypass line to the fuel pump 34 and the pressure regulator 35.
- a check valve 90 may be provided upstream of the mouth of the supply line 72 into the supply line 50. The check valve 90 prevents the feed pump 59 can promote fuel in the control chamber 43.
- the supply line 72 may also be connected directly to the fuel chamber 62.
- Fig. 8 is in the supply line 50 from the control chamber 43 to the fuel chamber 62 of the fuel valve 26 ( Fig. 5 ) arranged a feed pump 79 which acts pneumatically.
- the feed pump 79 is formed in correspondence to the manual feed pump 69 and has an inlet valve 74, an outlet valve 75 and a check valve 76.
- a diaphragm 91 is provided, the rear side of which is connected to the crankcase interior 31 and thereby pressurized with the crankcase the diaphragm 91 is moved as a function of the fluctuating pressure in the crankcase interior 31, thus conveying fuel to the fuel valve 26.
- a bypass line 70 is provided to the first valve 60 in the discharge line 58.
- a second valve 71 is arranged, which is formed in the embodiment as a mechanically acting pressure relief valve.
- the first valve 60 is advantageously used by the control device 78 (FIG. Fig. 3 ). Regardless of the driving of the first valve 60, the second valve 71 opens when the pressure difference between the fuel valve 26 and the fuel tank 32 exceeds a predetermined value. As a result, an impermissible pressure on the fuel valve 26 can be prevented.
- a manually operated feed pump 69 is arranged, the in Fig. 4 shown delivery pump 69 corresponds.
- a first, controlled by a control device 78 valve 60 is arranged.
- the internal combustion engine 12 is started up, that is to say during the starting process, it is possible to ensure via the first valve 60 that the fuel valve 26 is flushed. This is advantageously done by the operator activating the feed pump 69. Should the operator not operate the feed pump 69, the fuel is delivered by the fuel pump 34.
- starting of the internal combustion engine 12 can be made possible even in the case of a faulty operation, that is to say when the delivery pump 69 is not actuated by the operator.
- more time is needed in a misoperation to start because the purging of the fuel system and the fuel valve 26 takes more time.
- a delivery pump 89 is provided in the supply line 50, which is mechanically driven by the crankshaft 80 of the internal combustion engine 12.
- the feed pump 89 has, like the manual feed pump 69, an inlet valve 74, an outlet valve 75 and a check valve 76.
- a piston 92 is provided, which is reciprocated by the crankshaft 80. This can be done for example via a cam control.
- the coupling of the rotational movement of the crankshaft 80 to the reciprocating motion of the piston 92 may be accomplished in any known manner.
- the rotational movement of the crankshaft 80 is coupled via a coupling to the piston 92, so that the feed pump 89 can be taken out of operation by opening the clutch.
- a valve 73 which is a mechanical pressure relief valve.
- the pressure in the fuel system downstream of the fuel pump is advantageous in all embodiments low and is only a few bar or one or more tenths bar above ambient pressure.
- the pressure is in the order of about 100 mbar above ambient pressure.
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Abstract
Description
Die Erfindung betrifft einen Verbrennungsmotor mit einem Kraftstoffsystem der im Oberbegriff des Anspruchs 1 angegebenen Gattung.The invention relates to an internal combustion engine with a fuel system of the type specified in the preamble of claim 1.
Es ist bekannt, bei mit Vergaser arbeitenden Kraftstoffsystemen eine Förderpumpe vorzusehen, die manuell zu bedienen ist und über die das Kraftstoffsystem vor dem Starten des Verbrennungsmotors, beispielsweise nach längerem Stillstand, gespült werden kann. Solche Systeme arbeiten üblicherweise saugend. Dabei wird der Kraftstoff durch die Regelkammer des Vergasers von der stromab des Vergasers angeordneten Förderpumpe angesaugt. Ein solches System ist beispielsweise aus der
Auch bei Kraftstoffsystemen, die ein Kraftstoffventil umfassen, kann vorgesehen sein, das Kraftstoffsystem vor Inbetriebnahme des Motors zu spülen. Ein solches Kraftstoffsystem ist aus der
Der Erfindung liegt die Aufgabe zugrunde, einen Verbrennungsmotor mit einem Kraftstoffsystem der gattungsgemäßen Art zu schaffen, bei dem ein gutes Starten des Verbrennungsmotors erreicht wird.The invention has for its object to provide an internal combustion engine with a fuel system of the generic type, in which a good starting of the internal combustion engine is achieved.
Diese Aufgabe wird durch einen Verbrennungsmotor mit einem Kraftstoffsystem mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by an internal combustion engine with a fuel system having the features of claim 1.
Es hat sich gezeigt, dass in Kraftstoffsystemen mit Kraftstoffventil die Dampfblasenbildung im Kraftstoffsystem und im Einspritzventil ein Starten des Verbrennungsmotors sehr erschweren oder verhindern kann. Die Dampfblasenbildung ist vor allem bei Kraftstoffsystemen problematisch, die mit sehr geringem Druck arbeiten, der beispielsweise nur ein oder mehrere Zehntel Bar oder wenige Bar oberhalb des Umgebungsdrucks liegen kann. Der Druck in einem solchen Kraftstoffsystem kann beispielsweise etwa 100 mbar über dem Umgebungsdruck liegen. Erwärmt sich das Kraftstoffventil zu stark, so können sich im Kraftstoffventil Dampfblasen bilden. Die Dampfblasenbildung ist insbesondere auch problematisch, wenn der Verbrennungsmotor abgestellt ist und nachheizt, da dann keine Förderung von Kühlluft mehr erfolgt.It has been shown that in fuel systems with a fuel valve, the formation of vapor bubbles in the fuel system and in the injection valve can make it very difficult or impossible to start the internal combustion engine. The formation of vapor bubbles is particularly problematic in fuel systems that operate at very low pressure, which may for example be only one or more tenths bar or a few bar above the ambient pressure. The pressure in such a fuel system may be, for example, about 100 mbar above ambient pressure. If the fuel valve heats up too much, vapor bubbles may form in the fuel valve. The formation of vapor bubbles is particularly problematic when the engine is turned off and nachheizt, since then no promotion of cooling air more.
Um im Kraftstoffsystem gebildete Dampfblasen auszuspülen, ist vorgesehen, dass die Förderpumpe in einer Zuleitung zum Kraftstoffraum des Kraftstoffventils angeordnet ist und den Kraftstoff bis in den Kraftstoffraum des Kraftstoffventils fördert. Der Kraftstoffraum ist mit einer Entlastungsleitung verbunden, in der ein erstes Ventil angeordnet ist. Dadurch, dass der Kraftstoffraum des Kraftstoffventils gespült wird, ist sichergestellt, dass Dampfblasen im Kraftstoffventil ausgespült werden. Gleichzeitig wird durch das Spülen des Kraftstoffventils mit Kraftstoff auf einfache Weise eine effektive Kühlung des Kraftstoffventils erreicht, die eine erneute Dampfblasenbildung verhindert. Über das erste Ventil, das in der Entlastungsleitung angeordnet ist, kann im Betrieb ein gewünschter Druck im Kraftstoffsystem aufrechterhalten werden. Je nach Ansteuerung und Auslegung des ersten Ventils kann ein Spülen des Kraftstoffraums im Einspritzventil mit erheblich höherem Druck als dem Betriebsdruck im Kraftstoffsystem vorgesehen werden. Dadurch ist ein effektives Ausspülen von eventuell im Kraftstoffraum vorhandenen Gasblasen möglich und eine erneute Dampfblasenbildung kann verhindert werden.To rinse out vapor bubbles formed in the fuel system, it is provided that the feed pump is arranged in a supply line to the fuel chamber of the fuel valve and promotes the fuel into the fuel chamber of the fuel valve. The fuel space is connected to a relief line in which a first valve is arranged. The fact that the fuel space of the fuel valve is purged, it is ensured that steam bubbles are flushed out in the fuel valve. At the same time, flushing the fuel valve with fuel easily achieves effective cooling of the fuel valve which prevents re-vaporization. During operation, a desired pressure in the fuel system can be maintained via the first valve, which is arranged in the discharge line. Depending on the control and design of the first valve, a purging of the fuel chamber in the injection valve can be provided at a considerably higher pressure than the operating pressure in the fuel system. As a result, an effective rinsing of possibly present in the fuel chamber gas bubbles is possible and a new vapor bubble formation can be prevented.
Ein einfacher Aufbau ergibt sich, wenn die Zuleitung, in der die Förderpumpe angeordnet ist, im Strömungsweg von einem Pumpenraum der Kraftstoffpumpe zu dem Kraftstoffraum liegt. Die Förderpumpe kann demnach in einer ohnehin vorhandenen Zuleitung des Kraftstoffsystems angeordnet werden. Vorteilhaft ist stromab der Kraftstoffpumpe ein Druckregler angeordnet. Die Zuleitung, in der die Förderpumpe angeordnet ist, verbindet eine Regelkammer des Druckreglers mit dem Kraftstoffraum. Dadurch, dass die Kraftstoffpumpe stromab des Druckreglers angeordnet ist, wirkt der Druckregler für den mit der Förderpumpe zum Spülen des Kraftstoffventils aufgebrachten Druck nicht begrenzend, so dass über die Förderpumpe ein deutlich höherer Kraftstoffdruck im Kraftstoffsystem erzeugt werden kann als der üblicherweise im Betrieb herrschende Kraftstoffdruck. Es kann jedoch auch vorgesehen sein, dass die Zuleitung eine Bypassleitung zur Kraftstoffpumpe ist und den Kraftstofftank mit dem Kraftstoffraum verbindet. Aufgrund der Anordnung der Kraftstoffpumpe in einer Bypassleitung zur Kraftstoffpumpe kann die räumliche Anordnung der Förderpumpe bezogen auf die Kraftstoffpumpe und den Verbrennungsmotor vergleichsweise frei gewählt werden.A simple structure results when the supply line in which the feed pump is arranged in the flow path from a pump chamber of the fuel pump to the fuel chamber. The feed pump can therefore be arranged in an already existing supply line of the fuel system. Advantageously, a pressure regulator is arranged downstream of the fuel pump. The supply line, in which the feed pump is arranged, connects a control chamber of the pressure regulator with the fuel chamber. Characterized in that the fuel pump is arranged downstream of the pressure regulator, the pressure regulator for limiting the pressure applied to the pump for flushing the fuel valve pressure does not limit, so that via the feed pump, a significantly higher fuel pressure can be generated in the fuel system than the usually prevailing in operation fuel pressure. However, it can also be provided that the supply line is a bypass line to the fuel pump and connects the fuel tank with the fuel chamber. Due to the arrangement of the fuel pump in a bypass line to the fuel pump, the spatial arrangement of the feed pump relative to the fuel pump and the internal combustion engine can be chosen relatively freely.
Vorteilhaft ist das erste Ventil in Abhängigkeit eines Drucks betätigt, wird also druckabhängig geöffnet bzw. geschlossen. Der Druck, bei dessen Überschreitung das erste Ventil öffnet, ist dabei vorteilhaft höher als der Betriebsdruck im Kraftstoffsystem. Dadurch kann über die Förderpumpe ein begrenzter Überdruck im Kraftstoffsystem gegenüber dem normalen Betriebsdruck aufgebaut werden. Dadurch wird eine erneute Dampfblasenbildung im Kraftstoffventil oder Kraftstoffsystem verhindert. Das Ventil kann dabei insbesondere in Abhängigkeit des Drucks im Kraftstoffraum oder in Abhängigkeit des Differenzdrucks zwischen Kraftstoffraum und Kraftstofftank öffnen. Alternativ oder zusätzlich kann vorgesehen sein, dass das Ventil in Abhängigkeit einer Temperatur betätigt ist. Die Temperatur kann beispielsweise eine Temperatur des Kraftstoffventils oder des Verbrennungsmotors sein. Es kann auch vorgesehen sein, dass das Ventil in Abhängigkeit der Drehzahl des Verbrennungsmotors öffnet bzw. schließt. Dabei ist insbesondere vorgesehen, dass das Ventil oberhalb einer vorgegebenen Drehzahl geschlossen ist, so dass das erste Ventil im üblichen Betrieb geschlossen ist und nur während des Startvorgangs geöffnet ist. Es kann auch vorgesehen sein, dass das erste Ventil bei der ersten erkannten Verbrennung geschlossen wird. Die erste Verbrennung kann beispielsweise anhand der Drehzahl des Verbrennungsmotors erkannt werden. Die Drehzahl, bei der das Ventil geschlossen wird, kann eine Drehzahl sein, die erreicht wird, sobald der Verbrennungsmotor gestartet ist, die jedoch unter der Leerlaufdrehzahl des Verbrennungsmotors liegt. Alternativ oder zusätzlich kann vorgesehen sein, dass das Ventil zeitgesteuert betätigt wird. Das erste Ventil schließt dabei vorteilhaft nach dem Ablauf einer vorgegebenen Zeitspanne, die beispielsweise der Zeit für einen oder mehrere Anwerfhübe entsprechen kann. Dadurch wird das Kraftstoffsystem während des Anwerfvorgangs gespült. Die unterschiedlichen Parameter zur Betätigung des ersten Ventils können in geeigneter Weise kombiniert werden.Advantageously, the first valve is actuated in response to a pressure, so it is opened or closed depending on the pressure. The pressure above which the first valve opens is advantageously higher than the operating pressure in the fuel system. As a result, a limited overpressure in the fuel system relative to the normal operating pressure can be established via the feed pump. This prevents a new vapor bubble formation in the fuel valve or fuel system. The valve can open in particular as a function of the pressure in the fuel chamber or as a function of the differential pressure between the fuel chamber and the fuel tank. Alternatively or additionally, it can be provided that the valve is actuated as a function of a temperature. The temperature may be, for example, a temperature of the fuel valve or the internal combustion engine. It can also be provided that the valve opens or closes as a function of the rotational speed of the internal combustion engine. It is particularly provided that the valve is closed above a predetermined speed, so that the first valve is closed in normal operation and is open only during the startup process. It may also be provided that the first valve is detected at the first Combustion is closed. The first combustion can be detected, for example, based on the rotational speed of the internal combustion engine. The speed at which the valve is closed may be a speed that is reached as soon as the engine is started, but which is below the idle speed of the engine. Alternatively or additionally, it may be provided that the valve is actuated in a time-controlled manner. The first valve closes advantageous after the expiration of a predetermined period of time, which may for example correspond to the time for one or more Anwerfhübe. This flushes the fuel system during the startup process. The different parameters for actuating the first valve can be suitably combined.
Ein einfacher Aufbau ergibt sich, wenn das Ventil ein in Entlastungsrichtung öffnendes Druckhalteventil ist. Das Druckhalteventil arbeitet mechanisch, so dass zur Ansteuerung des Druckhalteventils keine weiteren Einrichtungen notwendig sind. Dadurch, dass das erste Ventil nur in Entlastungsrichtung öffnet und in Gegenrichtung zur Entlastungsrichtung, also in Strömungsrichtung vom Kraftstofftank zum Kraftstoffraum, ist ein Öffnen in Gegenrichtung verhindert, beispielsweise, wenn im Kraftstofftank ein höherer Druck herrscht als im Kraftstoffraum. Dies ist insbesondere bei Kraftstoffsystemen der Fall, bei denen der Kraftstofftank mit Druck beaufschlagt ist. Vorteilhaft ist das erste Ventil ein elektrisch betätigtes Ventil. Der Verbrennungsmotor besitzt dabei insbesondere eine Steuereinrichtung, die das erste Ventil betätigt. Dadurch kann eine vorteilhafte Ansteuerung des ersten Ventils, die insbesondere mehrere Einflussfaktoren berücksichtigt, erreicht werden.A simple construction results when the valve is a pressure relief valve opening in the relief direction. The pressure-holding valve operates mechanically, so that no further devices are necessary for controlling the pressure-holding valve. Characterized in that the first valve opens only in the discharge direction and in the opposite direction to the discharge direction, ie in the flow direction from the fuel tank to the fuel chamber, opening in the opposite direction is prevented, for example, when in the fuel tank, a higher pressure than in the fuel chamber. This is particularly the case with fuel systems in which the fuel tank is pressurized. Advantageously, the first valve is an electrically operated valve. The internal combustion engine has in particular a control device which actuates the first valve. As a result, an advantageous control of the first valve, which takes into account in particular a plurality of influencing factors, can be achieved.
Es kann vorgesehen sein, dass ein zweites Ventil in einer Bypassleitung zum ersten Ventil angeordnet ist. Vorteilhaft ist das zweite Ventil ein Druckhalteventil, während das erste Ventil ein elektrisch betätigtes Ventil ist. Über das in der Bypassleitung angeordnete Druckhalteventil kann unabhängig von den zur Betätigung des ersten Ventils genutzten Parametern sichergestellt werden, dass der Druck im Kraftstoffsystem nicht unzulässig steigt.It can be provided that a second valve is arranged in a bypass line to the first valve. Advantageously, the second valve is a pressure-holding valve, while the first valve is an electrically operated valve. Via the pressure-maintaining valve arranged in the bypass line, it is possible to ensure that the pressure in the fuel system does not increase inadmissibly, independently of the parameters used to actuate the first valve.
Die Förderpumpe kann manuell antreibbar, mechanisch angetrieben, elektrisch angetrieben oder pneumatisch angetrieben sein. Der mechanische Antrieb erfolgt vorteilhaft über den Verbrennungsmotor. Der pneumatische Antrieb erfolgt vorteilhaft über den schwankenden Druck im Verbrennungsmotor, insbesondere in einem Kurbelgehäuse des Verbrennungsmotors.The feed pump can be manually driven, mechanically driven, electrically driven or pneumatically driven. The mechanical drive is advantageously via the internal combustion engine. The pneumatic drive is advantageously carried out via the fluctuating pressure in the internal combustion engine, in particular in a crankcase of the internal combustion engine.
Ausführungsbeispiele der Erfindung werden im Folgenden anhand der Zeichnung erläutert. Es zeigen:
- Fig. 1
- eine schematische Seitenansicht eines Trennschleifers mit einem Verbrennungsmotor,
- Fig. 2
- eine teilweise schematische Schnittdarstellung des Verbrennungsmotors aus
Fig. 1 , - Fig. 3
- eine teilgeschnittene Seitenansicht eines Teils des Trennschleifers aus
Fig. 1 , - Fig. 4
- eine schematische Darstellung des Kraftstoffsystems des Verbrennungsmotors,
- Fig. 5
- einen Schnitt durch einen Halter des Kraftstoffsystems,
- Fig. 6 bis Fig. 10
- schematische Darstellungen von Ausführungsbeispielen des Kraftstoffsystems des Verbrennungsmotors.
- Fig. 1
- a schematic side view of a cutting machine with an internal combustion engine,
- Fig. 2
- a partial schematic sectional view of the internal combustion engine
Fig. 1 . - Fig. 3
- a partially sectioned side view of a portion of the cutting off
Fig. 1 . - Fig. 4
- a schematic representation of the fuel system of the internal combustion engine,
- Fig. 5
- a section through a holder of the fuel system,
- FIG. 6 to FIG. 10
- schematic representations of embodiments of the fuel system of the internal combustion engine.
Am Kurbelgehäuse 14 ist ein Halter 24 befestigt, der eine Aufnahme 25 für das in
Der Kurbelgehäuseinnenraum 31 ist im Bereich des unteren Totpunkts des Kolbens 21 über mindestens einen Überströmkanal 19 mit dem Brennraum 22 verbunden. Im Ausführungsbeispiel ist ein einziger Überströmkanal 19 vorgesehen, der sich in mehrere Äste aufteilt und mit mehreren Überströmfenstern 20 in den Brennraum 22 mündet. Die Überströmfenster 20 sind vom Kolben 21 schlitzgesteuert und im Bereich des unteren Totpunkts des Kolbens 21 geöffnet. Aus dem Brennraum 22 führt ein ebenfalls vom Kolben 21 schlitzgesteuerter Auslass 18.The
Im Betrieb wird über den Ansaugkanal 30 Verbrennungsluft in den Kurbelgehäuseinnenraum 31 zugeführt. In den Kurbelgehäuseinnenraum 31 wird auch Kraftstoff über das Kraftstoffventil 26 (
Wie
Wie
Der Verbrennungsmotor 12 besitzt eine Steuereinrichtung 78, die das Kraftstoffventil 26, nämlich die zuzuführende Kraftstoffmenge und den Zeitpunkt, wann die Kraftstoffmenge zuzuführen ist, steuert. Die Steuereinrichtung 78 steuert außerdem den Zündzeitpunkt. Auch weitere elektrische Komponenten des Trennschleifers 1 können von der Steuereinrichtung 78 gesteuert werden.The
Sowohl der Druckdämpfer 36 als auch das Kraftstoffventil 26 sind im Halter 24 angeordnet. Der Druckdämpfer 36 besitzt eine Dämpfungsmembran 54, die den Dämpfungsraum 53 begrenzt. An der dem Dämpfungsraum 53 abgewandten Seite der Dämpfungsmembran 54 ist ein Rückraum 56 ausgebildet, in dem eine Feder 55 angeordnet ist. Die Feder 55 spannt die Dämpfungsmembran 54 in die gewünschte Lage vor. Anstatt der Feder 55 kann die Dämpfungsmembran 54 auch aufgrund ihrer Eigenelastizität in der gewünschten Stellung gehalten werden. Der Rückraum 56 ist über eine Öffnung 57 mit einem Referenzdruck beaufschlagt. Der Referenzdruck ist vorteilhaft der Umgebungsdruck. Die Zuleitung 50 führt durch den Druckdämpfer 36 bis zum Kraftstoffventil 26.Both the
Das Kraftstoffventil 26 ist über eine Entlastungsleitung 58 mit dem Kraftstofftank 32 verbunden. In der Entlastungsleitung 58 ist ein erstes Ventil 73 angeordnet, das im Ausführungsbeispiel als mechanisch wirkendes Druckbegrenzungsventil ausgebildet ist. Das erste Ventil 73 besitzt ein Ventilglied, das von einer Feder beaufschlagt ist. Steigt der Druck stromauf des ersten Ventils 73 über einen vorgegebenen Druck an, so öffnet das erste Ventil 73. Das erste Ventil 73 öffnet dabei, wenn die Druckdifferenz zwischen Kraftstoffventil 26 und Kraftstofftank 32 einen konstruktiv vorgegebenen Wert, der über die Feder des ersten Ventils 73 definiert wird, übersteigt. Ist der Druck im Kraftstofftank 32 größer als der Druck im Kraftstoffventil 26, so bleibt das erste Ventil 73 geschlossen. Dies kann dann der Fall sein, wenn der Kraftstofftank 32 mit Druck beaufschlagt ist. Das erste Ventil 73 sperrt demnach in Strömungsrichtung vom Kraftstofftank 32 zum Kraftstoffventil 26. Ein Strömen von Kraftstoff vom Kraftstofftank 32 zum Kraftstoffventil 26 ist dadurch verhindert.The
Das Kraftstoffsystem besitzt die Förderpumpe 69, die in der Zuleitung 50 stromab der Regelkammer 43 und stromauf des Druckdämpfers 36 angeordnet ist. Die Begriffe "stromab" und "stromauf" beziehen sich dabei auf die Strömungsrichtung des Kraftstoffs im Kraftstoffsystem. Die Förderpumpe 69 ist manuell vom Bediener zu betätigen. Hierzu besitzt die Förderpumpe 69 den auch in
Das Kraftstoffventil 26 besitzt ein Gehäuse 67, in dem ein Kraftstoffraum 62 ausgebildet ist. Der Kraftstoffraum 62 besitzt eine Dosieröffnung 87, die von dem Kraftstoffventil 26, das als elektromagnetisches Ventil ausgebildet ist, geöffnet und verschlossen wird und die den Kraftstoffraum 62 mit dem Kraftstoffkanal 61 im Halter 24, der in den Kurbelgehäuseinnenraum 31 mündet, verbindet. Wie
Vor dem Starten des Verbrennungsmotors 12 wird vorteilhaft die Förderpumpe 69 vom Bediener durch mehrmaliges Zusammendrücken des Pumpenbalgs 77 betätigt. Dadurch drückt die Förderpumpe 69 Kraftstoff über die Zuleitung 50 in den Kraftstoffraum 62 des Kraftstoffventils 26. Sobald die vom ersten Ventil 73 konstruktiv vorgegebene Druckdifferenz stromauf und stromab des Ventils 73, also zwischen Kraftstoffraum 62 und Kraftstofftank 32, erreicht ist, öffnet das Ventil 73 und der Kraftstoff strömt über die Entlastungsleitung 58 zurück in den Kraftstofftank 32. Die Förderpumpe 69 saugt Kraftstoff über die Regelkammer 43 des Druckreglers 35 und über die Kraftstoffpumpe 34 aus dem Kraftstofftank 32 an. Der über die Förderpumpe 69 geförderte Kraftstoff spült das Kraftstoffsystem. Dadurch, dass der Kraftstoff unter Druck zum Kraftstoffventil 26 gefördert wird, wird die Funktion der Förderpumpe 69 durch eventuell im Kraftstoffraum 62 vorhandene Gasblasen nicht behindert. Die Kraftstoffpumpe 34 und der Druckregler 35 sind, wie die
In der Entlastungsleitung 58 ist im Ausführungsbeispiel nach
Beim Ausführungsbeispiel nach
Beim Ausführungsbeispiel nach
Beim Ausführungsbeispiel nach
Beim Ausführungsbeispiel nach
Beim Ausführungsbeispiel nach
In den Ausführungsbeispielen sind unterschiedliche Kombinationen von Förderpumpen und Ventilen in der Entlastungsleitung gezeigt. Die gezeigten Kombinationen sind nur beispielhaft. Alle gezeigten Förderpumpen können mit allen gezeigten Anordnungen der Förderpumpe und mit allen gezeigten Ventilanordnungen beliebig kombiniert werden.In the embodiments, different combinations of feed pumps and valves in the discharge line are shown. The combinations shown are only examples. All shown delivery pumps can be combined as desired with all shown arrangements of the delivery pump and with all shown valve arrangements.
Der Druck im Kraftstoffsystem stromab der Kraftstoffpumpe ist vorteilhaft bei allen Ausführungsbeispielen gering und beträgt nur wenige Bar oder ein oder mehrere Zehntel Bar oberhalb Umgebungsdruck. Vorteilhaft beträgt der Druck in der Größenordnung von etwa 100 mbar oberhalb Umgebungsdruck.The pressure in the fuel system downstream of the fuel pump is advantageous in all embodiments low and is only a few bar or one or more tenths bar above ambient pressure. Advantageously, the pressure is in the order of about 100 mbar above ambient pressure.
Claims (15)
dadurch gekennzeichnet, dass die Förderpumpe (59, 69, 79, 89) in einer Zuleitung (50, 72) zum Kraftstoffraum (62) des Kraftstoffventils (26) angeordnet ist und Kraftstoff in den Kraftstoffraum (62) fördert, und dass der Kraftstoffraum (62) mit einer Entlastungsleitung (58) verbunden ist, in der ein erstes Ventil (60, 73) angeordnet ist.An internal combustion engine with a fuel system, the fuel system comprising a fuel valve (26), the fuel valve (26) having a housing (67) in which a fuel chamber (62) is formed, the fuel system having a fuel pump (34) containing the fuel from a fuel tank (32) into the fuel chamber (62), and wherein the fuel system has a feed pump (59, 69, 79, 89) for forcibly feeding fuel into the fuel system,
characterized in that the feed pump (59, 69, 79, 89) in a feed line (50, 72) to the fuel chamber (62) of the fuel valve (26) is arranged and fuel in the fuel chamber (62) promotes, and that the fuel chamber ( 62) is connected to a relief line (58) in which a first valve (60, 73) is arranged.
dadurch gekennzeichnet, dass die Zuleitung (50), in der die Förderpumpe (59, 69, 79, 89) angeordnet ist, im Strömungsweg von einem Pumpenraum (38) der Kraftstoffpumpe (34) zu dem Kraftstoffraum (62) liegt.Internal combustion engine according to claim 1,
characterized in that the supply line (50), in which the feed pump (59, 69, 79, 89) is arranged in the flow path of a pump chamber (38) of the fuel pump (34) to the fuel chamber (62).
dadurch gekennzeichnet, dass stromab der Kraftstoffpumpe (34) ein Druckregler (35) angeordnet ist, und dass die Zuleitung (50) eine Regelkammer (43) des Druckreglers (35) mit dem Kraftstoffraum (62) verbindet.Internal combustion engine according to claim 2,
characterized in that downstream of the fuel pump (34), a pressure regulator (35) is arranged, and that the supply line (50) connects a control chamber (43) of the pressure regulator (35) with the fuel chamber (62).
dadurch gekennzeichnet, dass die Zuleitung (72) eine Bypassleitung zur Kraftstoffpumpe (34) ist und den Kraftstofftank (32) mit dem Kraftstoffraum (62) verbindet.Internal combustion engine according to claim 1,
characterized in that the supply line (72) is a bypass line to the fuel pump (34) and connects the fuel tank (32) with the fuel chamber (62).
dadurch gekennzeichnet, dass das erste Ventil (60, 73) in Abhängigkeit eines Drucks betätigt ist.Internal combustion engine according to one of claims 1 to 4,
characterized in that the first valve (60, 73) is actuated in response to a pressure.
dadurch gekennzeichnet, dass das erste Ventil (60, 73) in Abhängigkeit des Drucks im Kraftstoffraum (62) betätigt ist.Internal combustion engine according to claim 5,
characterized in that the first valve (60, 73) is actuated in dependence on the pressure in the fuel chamber (62).
dadurch gekennzeichnet, dass das erste Ventil (60, 73) in Abhängigkeit der Druckdifferenz zwischen Kraftstoffraum (62) und Kraftstofftank (32) betätigt ist.Internal combustion engine according to claim 5,
characterized in that the first valve (60, 73) is actuated as a function of the pressure difference between the fuel chamber (62) and the fuel tank (32).
dadurch gekennzeichnet, dass das erste Ventil (60) in Abhängigkeit einer Temperatur betätigt ist.Internal combustion engine according to one of claims 1 to 7,
characterized in that the first valve (60) is actuated in response to a temperature.
dadurch gekennzeichnet, dass das erste Ventil (60) in Abhängigkeit der Drehzahl des Verbrennungsmotors (12) betätigt ist.Internal combustion engine according to one of claims 1 to 8,
characterized in that the first valve (60) is actuated in dependence on the rotational speed of the internal combustion engine (12).
dadurch gekennzeichnet, dass das erste Ventil (60) zeitgesteuert betätigt ist.Internal combustion engine according to one of claims 1 to 9,
characterized in that the first valve (60) is operated timed.
dadurch gekennzeichnet, dass das erste Ventil (73) insbesondere ein in Entlastungsrichtung öffnendes Druckhalteventil ist, wobei das erste Ventil (73) insbesondere in Gegenrichtung zur Entlastungsrichtung sperrt.Internal combustion engine according to one of claims 5 to 7,
characterized in that the first valve (73) is in particular a pressure-maintaining valve which opens in the relief direction, wherein the first valve (73) blocks in particular in the opposite direction to the unloading direction.
dadurch gekennzeichnet, dass das erste Ventil ein elektrisch betätigtes Ventil ist.Internal combustion engine according to one of claims 5 to 10,
characterized in that the first valve is an electrically operated valve.
dadurch gekennzeichnet, dass der Verbrennungsmotor eine Steuereinrichtung (78) besitzt, die das erste Ventil (60) betätigt.Internal combustion engine according to claim 12,
characterized in that the internal combustion engine has a control device (78) which actuates the first valve (60).
dadurch gekennzeichnet, dass ein zweites Ventil (71) in einer Bypassleitung (70) zum ersten Ventil (60) angeordnet ist, wobei das zweite Ventil (71) vorteilhaft ein Druckhalteventil ist.Internal combustion engine according to claim 12 or 13,
characterized in that a second valve (71) in a bypass line (70) to the first valve (60) is arranged, wherein the second valve (71) is advantageously a pressure holding valve.
dadurch gekennzeichnet, dass die Förderpumpe (59, 69, 79, 89) manuell antreibbar ist oder mechanisch über den Verbrennungsmotor (12), elektrisch oder pneumatisch angetrieben ist.Internal combustion engine according to one of claims 1 to 14,
characterized in that the feed pump (59, 69, 79, 89) is manually driven or mechanically via the internal combustion engine (12), driven electrically or pneumatically.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011120465A DE102011120465A1 (en) | 2011-12-07 | 2011-12-07 | Internal combustion engine with a fuel system |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2602470A2 true EP2602470A2 (en) | 2013-06-12 |
EP2602470A3 EP2602470A3 (en) | 2014-12-10 |
EP2602470B1 EP2602470B1 (en) | 2016-06-29 |
Family
ID=47520657
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12008126.0A Active EP2602470B1 (en) | 2011-12-07 | 2012-12-05 | Internal combustion engine with a fuel system |
Country Status (4)
Country | Link |
---|---|
US (1) | US9534528B2 (en) |
EP (1) | EP2602470B1 (en) |
CN (1) | CN103174566B (en) |
DE (1) | DE102011120465A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2022093099A1 (en) * | 2020-10-26 | 2022-05-05 | Husqvarna Ab | Fuel supply arrangement, two stroke engine, and power tool |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015208934A1 (en) | 2014-05-13 | 2015-11-19 | Robert Bosch Gmbh | SPRING-LOADED COMPONENT MOUNTING WITHIN FUEL TANK |
DE102015006303A1 (en) * | 2015-05-16 | 2016-11-17 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Cooling system with a coolant pump for an internal combustion engine |
DE102015016484A1 (en) * | 2015-12-15 | 2017-06-22 | Andreas Stihl Ag & Co. Kg | Manually operated feed pump and fuel system with a feed pump |
US10800065B2 (en) * | 2015-12-15 | 2020-10-13 | Andreas Stihl Ag & Co. Kg | Hand-guided power tool with a control device |
DE102015016485A1 (en) * | 2015-12-15 | 2017-06-22 | Andreas Stihl Ag & Co. Kg | Hand-held implement with a control device |
DE102018004881A1 (en) * | 2018-06-19 | 2019-12-19 | Andreas Stihl Ag & Co. Kg | Carburetor and hand-held implement with an internal combustion engine with a carburetor |
DE102020000989A1 (en) | 2020-02-15 | 2021-08-19 | Andreas Stihl Ag & Co. Kg | Two-stroke engine and method of operating a two-stroke engine |
CN113565659A (en) * | 2021-07-20 | 2021-10-29 | 河北华北柴油机有限责任公司 | Reliability assessment method for manual fuel pump |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10341600A1 (en) | 2003-09-10 | 2005-04-14 | Andreas Stihl Ag & Co. Kg | Carburetor arrangement of a hand-held implement |
EP2075453A2 (en) | 2007-12-27 | 2009-07-01 | Denso Corporation | Fuel feed apparatus |
Family Cites Families (50)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB885152A (en) | 1958-10-02 | 1961-12-20 | Linde Eismasch Ag | Improvements in or relating to internal combustion engines |
JPS5037806B1 (en) | 1971-03-10 | 1975-12-05 | ||
US4205637A (en) | 1976-12-13 | 1980-06-03 | Toyota Jidosha Kogyo Kabushiki Kaisha | Electronic fuel injection system for an internal combustion engine having electromagnetic valves and a fuel damper upstream thereof |
IT1115980B (en) | 1978-05-12 | 1986-02-10 | Univ Belfast | IMPROVEMENT IN TWO STROKE INTERNAL COMBUSTION ENGINES |
DE2933052A1 (en) * | 1979-08-16 | 1981-03-26 | Robert Bosch Gmbh, 70469 Stuttgart | FUEL INJECTION SYSTEM |
JPS56110509A (en) | 1980-02-05 | 1981-09-01 | Yanmar Diesel Engine Co Ltd | Air-cooled type internal combustion engine |
DE3307241A1 (en) | 1983-03-02 | 1984-09-06 | Robert Bosch Gmbh, 7000 Stuttgart | AGGREGATE FOR PROCESSING FUEL, ESPECIALLY FROM A STORAGE TANK FOR THE INTERNAL COMBUSTION ENGINE OF A MOTOR VEHICLE |
DE3435248A1 (en) | 1984-09-26 | 1986-04-03 | Audi AG, 8070 Ingolstadt | DAMPING ELEMENT FOR DAMPING PRESSURE VIBRATIONS IN FUEL LINES |
EP0280923A3 (en) | 1987-03-06 | 1989-02-22 | WALBRO CORPORATION (Corporation of Delaware) | Engine manifold pulse dampener |
DE3817404C2 (en) | 1988-05-21 | 1997-08-07 | Stihl Maschf Andreas | Diaphragm fuel pump for an internal combustion engine of a motor chain saw equipped with a diaphragm carburettor |
US5042445A (en) * | 1988-09-23 | 1991-08-27 | Cummins Engine Company, Inc. | Electronic controlled fuel supply system for high pressure injector |
US4971016A (en) * | 1988-09-23 | 1990-11-20 | Cummins Engine Company, Inc. | Electronic controlled fuel supply system for high pressure injector |
JP2733329B2 (en) | 1989-08-31 | 1998-03-30 | キヤノン株式会社 | Toner kit |
SE500639C2 (en) | 1989-09-12 | 1994-08-01 | Electrolux Ab | Controls, for example gas controls for chainsaws |
JP2691461B2 (en) | 1990-01-29 | 1997-12-17 | ヤンマーディーゼル株式会社 | Air-cooled internal combustion engine |
SE468487B (en) | 1991-05-24 | 1993-01-25 | Electrolux Ab | TWO-TAKING ENGINE WITH BRAIN INJECTION |
US5207203A (en) * | 1992-03-23 | 1993-05-04 | General Motors Corporation | Fuel system |
DE4223756C2 (en) | 1992-07-18 | 1997-01-09 | Stihl Maschf Andreas | Fuel pump for a two-stroke engine |
DE4329876B4 (en) | 1993-09-03 | 2004-07-29 | Fa. Andreas Stihl | Breather valve for a fuel tank |
US5488933A (en) | 1994-02-14 | 1996-02-06 | Pham; Roger N. C. | Fuel supply system for miniature engines |
JPH08303330A (en) | 1995-04-28 | 1996-11-19 | Yamaha Motor Co Ltd | Crank chamber compression type 2 cycle diesel engine |
US5673670A (en) | 1995-07-05 | 1997-10-07 | Ford Motor Company | Returnless fuel delivery system |
JPH09151739A (en) | 1995-11-30 | 1997-06-10 | Kioritz Corp | 2-cycle internal combustion engine |
US5967120A (en) | 1996-01-16 | 1999-10-19 | Ford Global Technologies, Inc. | Returnless fuel delivery system |
JPH09242552A (en) | 1996-03-01 | 1997-09-16 | Kioritz Corp | Two-cycle internal combustion engine |
US5664532A (en) * | 1996-03-22 | 1997-09-09 | August; Rex David | Universal fuel priming system |
CA2251764A1 (en) | 1996-04-12 | 1997-10-23 | Andreas Singer | Hand-guided appliance with an internal combustion engine with direct electronic injection |
JPH10131800A (en) | 1996-10-30 | 1998-05-19 | Kioritz Corp | Control device for internal combustion engine |
JP3530694B2 (en) | 1996-12-06 | 2004-05-24 | 株式会社共立 | Two-stroke internal combustion engine |
DE19654290A1 (en) | 1996-12-27 | 1998-07-02 | Dolmar Gmbh | Driving device for a lawn trimmer |
JP3630897B2 (en) | 1997-02-10 | 2005-03-23 | 株式会社共立 | 2-cycle internal combustion engine |
DE19732741A1 (en) * | 1997-07-30 | 1999-02-04 | Bosch Gmbh Robert | Starting procedure for two stroke engine |
CN1288332C (en) | 2001-05-11 | 2006-12-06 | 电气联合股份有限公司 | Crankcase scavenged internal combustion engine |
KR100569164B1 (en) | 2002-09-24 | 2006-04-07 | 혼다 기켄 고교 가부시키가이샤 | Air-cooled internal combustion engine |
US6701900B1 (en) * | 2002-12-31 | 2004-03-09 | Caterpillar Inc. | Quick priming fuel system and common passageway housing for same |
EP1614901B1 (en) | 2003-03-13 | 2018-12-26 | Yanmar Co., Ltd. | Cover structure for engine |
SE0302439D0 (en) | 2003-09-12 | 2003-09-12 | Electrolux Ab | Throttle control device for a hand held tool |
JP4392300B2 (en) | 2004-07-22 | 2009-12-24 | ヤンマー株式会社 | Cylinder head cooling structure |
KR101131883B1 (en) | 2004-07-22 | 2012-04-03 | 얀마 가부시키가이샤 | Engine |
DE102005002273B4 (en) | 2005-01-18 | 2017-08-10 | Andreas Stihl Ag & Co. Kg | Method for operating a single-cylinder two-stroke engine |
ATE420744T1 (en) | 2005-10-07 | 2009-01-15 | Black & Decker | SAW |
JP5250222B2 (en) | 2006-08-16 | 2013-07-31 | アンドレアス シュティール アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト | Ignition device for internal combustion engine and method for operating ignition device |
JP2008045489A (en) | 2006-08-16 | 2008-02-28 | Honda Motor Co Ltd | General purpose internal combustion engine |
US7527043B2 (en) * | 2007-07-05 | 2009-05-05 | Caterpillar Inc. | Liquid fuel system with anti-drainback valve and engine using same |
US8261718B2 (en) | 2007-11-01 | 2012-09-11 | Caterpillar Inc. | High pressure pump and method of reducing fluid mixing within same |
JP5248921B2 (en) | 2008-05-30 | 2013-07-31 | ヤマハ発動機株式会社 | Outboard motor |
US7827971B2 (en) * | 2009-01-26 | 2010-11-09 | Gm Global Technology Operations, Inc. | Engine assembly with fuel filter gas removal apparatus |
JP2010180775A (en) * | 2009-02-05 | 2010-08-19 | Fuji Heavy Ind Ltd | Fuel supply system for engine |
DE102009057731B4 (en) | 2009-12-10 | 2022-02-03 | Andreas Stihl Ag & Co. Kg | Method for operating an implement with a diagnostic device |
EP2531707B1 (en) | 2010-02-05 | 2018-04-11 | Insitu, Inc. | Two-stroke, fuel injected internal combustion engines for unmanned aircraft and associated systems and methods |
-
2011
- 2011-12-07 DE DE102011120465A patent/DE102011120465A1/en not_active Withdrawn
-
2012
- 2012-12-05 EP EP12008126.0A patent/EP2602470B1/en active Active
- 2012-12-07 US US13/707,832 patent/US9534528B2/en active Active
- 2012-12-07 CN CN201210521852.6A patent/CN103174566B/en active Active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10341600A1 (en) | 2003-09-10 | 2005-04-14 | Andreas Stihl Ag & Co. Kg | Carburetor arrangement of a hand-held implement |
EP2075453A2 (en) | 2007-12-27 | 2009-07-01 | Denso Corporation | Fuel feed apparatus |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2022093099A1 (en) * | 2020-10-26 | 2022-05-05 | Husqvarna Ab | Fuel supply arrangement, two stroke engine, and power tool |
Also Published As
Publication number | Publication date |
---|---|
EP2602470B1 (en) | 2016-06-29 |
US20130340722A1 (en) | 2013-12-26 |
CN103174566A (en) | 2013-06-26 |
US9534528B2 (en) | 2017-01-03 |
EP2602470A3 (en) | 2014-12-10 |
CN103174566B (en) | 2017-06-13 |
DE102011120465A1 (en) | 2013-06-13 |
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