EP2610458B1 - Work device - Google Patents
Work device Download PDFInfo
- Publication number
- EP2610458B1 EP2610458B1 EP12008124.5A EP12008124A EP2610458B1 EP 2610458 B1 EP2610458 B1 EP 2610458B1 EP 12008124 A EP12008124 A EP 12008124A EP 2610458 B1 EP2610458 B1 EP 2610458B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cooling
- air
- working implement
- zone
- internal combustion
- 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.)
- Active
Links
- 238000001816 cooling Methods 0.000 claims description 139
- 238000002485 combustion reaction Methods 0.000 claims description 74
- 239000000446 fuel Substances 0.000 claims description 54
- 238000005192 partition Methods 0.000 claims description 37
- 239000002828 fuel tank Substances 0.000 claims description 4
- 239000012530 fluid Substances 0.000 claims 1
- 239000003570 air Substances 0.000 description 121
- 238000002347 injection Methods 0.000 description 25
- 239000007924 injection Substances 0.000 description 25
- 239000007788 liquid Substances 0.000 description 8
- 238000000926 separation method Methods 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 6
- 230000010355 oscillation Effects 0.000 description 5
- 238000003303 reheating Methods 0.000 description 5
- 238000004140 cleaning Methods 0.000 description 4
- 239000007789 gas Substances 0.000 description 3
- 239000002245 particle Substances 0.000 description 3
- JTJMJGYZQZDUJJ-UHFFFAOYSA-N phencyclidine Chemical class C1CCCCN1C1(C=2C=CC=CC=2)CCCCC1 JTJMJGYZQZDUJJ-UHFFFAOYSA-N 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 239000012212 insulator Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 244000025254 Cannabis sativa Species 0.000 description 1
- 238000004887 air purification Methods 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 239000013013 elastic material Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 230000003584 silencer Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000013022 venting Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
- F01P5/04—Pump-driving arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P1/00—Air cooling
- F01P1/06—Arrangements for cooling other engine or machine parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P1/00—Air cooling
- F01P1/02—Arrangements for cooling cylinders or cylinder heads, e.g. ducting cooling-air from its pressure source to cylinders or along cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P1/00—Air cooling
- F01P1/06—Arrangements for cooling other engine or machine parts
- F01P1/10—Arrangements for cooling other engine or machine parts for cooling fuel injectors or sparking-plugs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
- F01P11/12—Filtering, cooling, or silencing cooling-air
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
- F01P5/06—Guiding or ducting air to, or from, ducted fans
-
- 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
- F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
- F02B63/02—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for hand-held tools
Definitions
- the invention relates to a working device of the type specified in the preamble of claim 1.
- a working device namely a grass trimmer known, which has a fuel pump, an injection valve and an internal combustion engine.
- the fuel pump is arranged.
- the injection valve is arranged above a fan and cooled by the cooling air conveyed by the fan.
- a similar work tool is used in the WO 97/39228 shown.
- the invention has for its object to provide a working device of the generic type, in which an improved cooling of the fuel pump is achieved.
- the implement has several cooling zones.
- a first cooling zone the cylinder of the internal combustion engine is arranged, which is the hottest component of the working device during operation.
- the fuel pump is arranged in a second cooling zone.
- a buffer zone is formed, which is separated from both the first cooling zone and the second cooling zone via at least one partition wall.
- the buffer zone causes a good thermal separation of the first and the second cooling zone. This can prevent excessive heating of the fuel pump during operation. Excessive heating of the fuel pump can form gas bubbles in the fuel pump, which prevent further fuel to the engine can be promoted. Excessive heating of the fuel pump must therefore be avoided.
- a buffer zone is arranged between the first and the second cooling zone. This results in a spatial separation of the fuel pump from the cylinder, which also prevents excessive heating of the fuel pump.
- the buffer zone Due to the buffer zone, an excessive heating of the fuel pump is reduced even when the internal combustion engine is switched off during reheating of the internal combustion engine.
- the reheating of the internal combustion engine refers to the period of time after the engine is switched off, during which the heat is distributed in the components. In this case, the cylinder of the internal combustion engine cools down and gives off its heat to other components, in particular to adjacent components such as the crankcase, which heat up as a result. Since cooling air is no longer conveyed during reheating, higher temperatures can occur at individual components during reheating than during operation.
- the buffer zone reduces heat transfer to the fuel pump during reheating.
- the partitions do not necessarily separate the cooling zones from the buffer zone, but at least partially. In particular, the partitions provide a substantial separation which ensures that the air streams in the cooling zones and the buffer zone flow substantially separately from each other. At suitable locations, a substantially dense separation through the at least one partition may be advantageous.
- the second cooling zone lies in the flow path of the combustion air sucked by the internal combustion engine.
- the implement has a fan wheel which serves to convey cooling air.
- the combustion air sucked in by the internal combustion engine was not already compressed, and thus heated, like the air conveyed by the fan wheel.
- the combustion air sucked in by the internal combustion engine is thereby somewhat cooler than the cooling air conveyed by the fan wheel.
- the implement has an intake opening, via which the cooling air is sucked into the second cooling zone.
- the fuel pump is advantageously arranged in the flow path of the cooling air flowing through the intake opening.
- the fuel pump is in particular immediately adjacent to the intake opening in the second cooling zone arranged.
- the cooling of the fuel pump combustion air is thus not yet heated by other components, so that there is a very good cooling of the fuel pump.
- the combustion air is advantageously sucked directly from the environment into the second cooling zone.
- the intake opening is arranged in particular in a region which has the largest possible distance to the outlet of the cooling air flowing through the first cooling zone from the working device, ie to the outlet of the cooling air, which cools the cylinder.
- the buffer zone is arranged.
- the cooling air is conveyed into the buffer zone by the fan.
- the buffer zone can be arranged on the suction side of the fan wheel, ie upstream of the fan wheel, or on the pressure side of the fan wheel, ie downstream of the fan wheel.
- a simple arrangement results in an arrangement of the buffer zone downstream of the fan, so when the fan presses the cooling air in the buffer zone.
- the fan wheel sucks the cooling air through the buffer zone, that is, the buffer zone is upstream of the fan.
- the cooling air is sucked in this case from a lying in the usual parking position of the implement below area and passes through an opening in the fan housing in the fan housing.
- the sucked by the fan cooling air was not yet compressed by the fan and is therefore cooler than the cooling air flowing from the fan, so that the arrangement of the buffer zone in the sucked by the fan cooling air flow effective cooling of the buffer zone results.
- the injection valve is arranged in the buffer zone. Because the injection valve is not arranged in the first cooling zone but in a buffer zone which is at least partially separated from the first cooling zone by a dividing wall, improved cooling of the injection valve can be achieved.
- a pressure damper is arranged in the buffer zone adjacent to the injection valve. The pressure damper must also be cooled as well as possible during operation in order to prevent gas bubble formation in the pressure damper. At the same time it is advantageous, the pressure damper as close as possible to the injection valve to arrange. This can be accomplished by placing the pressure damper adjacent to the injector in the buffer zone.
- the injection valve is arranged in a region which is connected via a connecting channel with the interior of the fan wheel housing.
- the cooling air can be directed to the area in which the injection valve is arranged.
- the channel is designed to be as short as possible in order to keep the flow resistance low and to achieve the most direct possible cooling of the region in which the injection valve is arranged.
- the cooling of the injection valve can be improved if the injection valve is arranged in an antechamber of the buffer zone, from which the cooling air flows into a main chamber of the buffer zone.
- the subdivision of the buffer zone into an antechamber and a main chamber allows for improved, direct cooling of the injection valve and possibly the pressure damper.
- the air entering the buffer zone goes directly to the injector and the pressure damper before being heated by other components.
- the pre-chamber is advantageously made small, so that the cooling air is purposefully guided to the injection valve or a component surrounding the injection valve.
- a simple construction results when the prechamber is separated from an air guiding component by the main chamber.
- the air guide component is advantageously held on a crankcase of the internal combustion engine.
- the cooling air flows advantageous between the air guide member and the crankcase in the main chamber.
- the connection opening between the prechamber and the main chamber of the buffer zone is formed in a simple manner in that the air guiding component is not sealed with respect to the crankcase of the internal combustion engine, but has a small distance to it.
- the air guide component advantageously encloses the components arranged in the pre-chamber as closely as possible, so that it is ensured that the components are flowed around by the cooling air and are well cooled.
- the first partition is at least partially formed by a portion of an engine cover.
- the engine cover is advantageously disposed within the outer housing of the implement and covered by a hood of the implement. This makes it possible to avoid contact between the operator and the engine cover which heats up during operation.
- the engine cover covers the cylinder of the internal combustion engine. Under the engine cover, the fan promotes cooling air. Particularly advantageously, the cooling air is pressed under the engine cover. However, it may also be provided to arrange the fan so that the cooling air is sucked under the engine cover, so the first cooling zone is located on the suction side of the fan. It may be advantageous that the first partition is at least partially bounded by the air guide component.
- At least one partition wall section of the second partition is integrally formed on the tank housing of the implement.
- the buffer zone is advantageously located between an air filter of the working device and the internal combustion engine.
- the internal combustion engine has an intake passage which connects the internal combustion engine with the air filter and which is guided through the buffer zone due to the arrangement of the buffer zone between the air filter and the internal combustion engine. It is envisaged that the intake passage of the internal combustion engine protrudes through the second partition wall.
- a simple construction results if at least one partition wall section of the second partition wall is formed on a separate component fixed to the tank housing.
- the two partition wall sections advantageously limit the passage opening for the intake passage, so that the intake passage can be placed on the tank housing and the separate component can be placed on the tank housing and fixed thereto. As a result, a simple structure and a simple assembly is achieved.
- a discharge channel for liquid removal from the second cooling zone leads into the buffer zone through the second partition wall.
- the discharge channel is advantageous as a depression in a wall bounding the second cooling zone of the tank housing educated. This results in a simple structure. For the discharge channel no additional components are needed.
- the discharge channel falls in the parking position of the working device from the second cooling zone to the buffer zone. This ensures that liquid from the second cooling zone can flow into the buffer zone.
- the liquid flows from the buffer zone into the environment.
- the air pressure in the buffer zone may be higher than the air pressure in the second cooling zone, in particular, when the cooling air is conveyed into the buffer zone by the fan of the implement.
- the discharge channel is connected to the second cooling zone downstream of the fuel pump in relation to the flow direction in the second cooling zone. Air that flows from the buffer zone into the second cooling zone can not thereby flow to the fuel pump, but is sucked to the engine.
- the handles are usually vibration-decoupled from the internal combustion engine via anti-vibration elements.
- a vibrating gap is usually formed between the engine and the handles.
- the oscillation gap extends between the tank housing and the internal combustion engine.
- the oscillation gap advantageously extends through the buffer zone.
- the fuel pump is advantageously fixed to the tank housing and separated by the extending through the buffer zone oscillation gap of the arranged in the first cooling zone cylinder. This results in a large distance between the fuel pump and the cylinder, which ensures that the fuel pump is not heated inadmissible.
- the volume of the buffer zone changes during operation in the case of relative movements of the tank housing and the internal combustion engine.
- the arrangement of a solid insulating body, which fills the buffer zone is not possible because this insulator would hinder the relative movement between the tank housing and the engine.
- Fig. 1 shows as an exemplary embodiment of a working device, in particular a hand-held implement, a power grinder 1.
- the implement is advantageously portable.
- the implement may instead of a cutting machine 1 also another working device such as a brushcutter, a chainsaw, a hedge trimmer or the like. Be.
- the power cutter 1 has a housing 2, the structure of which will be explained in more detail below.
- a boom 3 is fixed, which projects forward and at the free end of a cutting disc 4 is rotatably mounted, which is at least partially covered by a protective cover 5.
- a protective cover 5 For guiding the cutting grinder 1 is an upper handle 6, which is formed on a hood 8 of the housing 2, and a handle tube 7, which engages over the housing 2 on the side facing the blade 4.
- an air filter cover 9 is fixed.
- To stop the cutting grinder 1 serve on the housing 2 and the handle tube 7 fixed feet 13. If the power grinder 1 is placed on a flat surface, it is located in the in Fig. 1 shown parking position 69.
- an internal combustion engine 12 is arranged, which serves for the rotary drive of the cutting disc 4.
- the internal combustion engine 12 is a two-stroke engine in the embodiment. However, the engine 12 may also be a compound lubricated or a separately lubricated four-stroke engine.
- the internal combustion engine 12 is advantageously a single-cylinder engine.
- To operate the internal combustion engine 12 is a pivotally mounted on the upper handle 6 throttle lever 10. The throttle lever 10 can only be pressed when a likewise mounted on the upper handle 6 throttle lever lock 11 is actuated.
- a fuel pump 23 is arranged in the housing 2.
- the fuel pump 23 is adjacent to the air filter cover 9, ie arranged on the blade 4 remote from the rear side of the housing 2.
- the hood 8 has an intake opening 65, which is formed by a plurality of cooling air slots 66.
- the cooling air slots 66 are formed immediately adjacent to the fuel pump 23 in the hood 8 of the housing 2.
- an engine cover 27 is provided which partially covers the engine 12. The engine cover 27 is covered by the hood 8.
- Fig. 2 shows a plan view of the grinder 1, wherein the boom 3 is not shown. In addition, the hood 8 and the air filter cover 9 are removed. Other components are not shown to better illustrate the structural design.
- a first cooling zone A is formed, in which a cylinder 17 of the internal combustion engine 12 is arranged.
- the first cooling zone A promotes a driven by the internal combustion engine 12 fan 28 cooling air.
- the cooling air will flow along in Fig. 2 schematically drawn arrows 61 conveyed over the cylinder 17 and passes forward, ie in the direction of the cutting wheel 4, from the housing 2.
- the fan 28 sucks the cooling air through a in Fig. 2 schematically shown Lüfterraddeckel 70 directly from the environment.
- the fuel pump 23 is arranged in a second cooling zone C, directly adjacent to the suction opening 65 (FIG. Fig. 1 ).
- the ambient air flows from the environment directly through the fuel pump 23.
- the suction port 65 is a separate suction port for cooling air, which is separated from the suction port of the intake air from the fan 28 cooling air.
- the air sucked into the second cooling zone C is combustion air for the internal combustion engine 12, which is in the direction of an arrow 63 in FIG Fig. 2 not shown air inlet openings of an air cleaning unit 71 flows.
- the air purification unit 71 is partially formed on a tank housing 25 of the cutter 1.
- Fig. 2 Also shows, in the tank housing 25, a fuel tank 32 is formed, from which the fuel pump 23 sucks the fuel.
- the fuel pump 23 is for this purpose with the in Fig. 8 shown connecting piece 51, which in the in Fig. 2 shown mounting opening 41 of the tank housing 25 is fixed.
- a buffer zone B is formed between the first cooling zone A and the second cooling zone C.
- the buffer zone B is separated from the first cooling zone A by a partition formed by the engine cover 27.
- the separation between the first cooling zone A and the buffer zone B runs in the in Fig. 2
- the buffer zone B is separated from the second cooling zone C by a partition wall which is partially separated from the one shown in FIG Fig. 2 shown upper partition wall portion 35 is formed.
- the upper partition wall section 35 is formed on an assembly aid 36, which is placed on the tank housing 25.
- the mounting aid 36 has two arms 37 which hold a receptacle 38.
- the receptacle 38 receives the throttle lever 10 facing the end of a Bowden cable.
- the Bowden cable which runs through the Bowden cable sheath, serves to transmit the adjusting movement of the throttle lever 10 to a throttle element, which is still shown below, in an intake passage of the internal combustion engine 12.
- the tank housing 25 is separated from a motor unit 24 of the cutting grinder 1 via a vibration gap 60.
- the vibration gap 60 is bridged by a plurality of anti-vibration elements, of which in Fig. 2 an anti-vibration element 40 is shown.
- the engine unit 24 comprises the internal combustion engine 12, a mounting flange 72 for the boom 3, and a fan wheel housing 44 arranged on the opposite side of the internal combustion engine 12, in which the fan wheel 28 is arranged.
- the tank housing 25 and motor unit 24 move relative to each other. As a result, the volume of the buffer zone B changes permanently during operation.
- the combustion air sucked into the second cooling zone C flows into air inlet openings 73 of the air cleaning unit 71 on the longitudinal side of the cutting grinder 1, which faces away from the mounting flange 72 and on which the fan impeller 28 is arranged.
- the air inlet openings 73 open into cyclones 33, which in Fig. 4 are shown.
- the air inlet openings 73 are arranged adjacent to the outer circumference of the Lüfterradgephinuses 44. From the cyclones 33, the combustion air flows into an air filter, not shown, and from there into an intake passage of the internal combustion engine 12.
- the combustion air is sucked into the second cooling zone C from the environment.
- it could also be provided to convey air from an overpressure region of the fan wheel housing 44 into the second cooling zone C and from there as combustion air to the air inlet openings 73.
- the combustion engine 12 combustion air is supplied, which is under pressure.
- the Lüfterradgephase 44 forms a fan coil and is integrally formed on a crankcase 14 of the engine 12.
- the Lüfterradgephase 44 defines a fan coil 78.
- a connection opening 46 is formed in an overpressure region of the fan coil 78, in which a connection sleeve 75 is arranged.
- the connecting sleeve 75 which may be a rubber grommet, for example, connects the overpressure region of the ventilator wheel housing 44 to a connecting channel 47 which opens into an antechamber 67 formed in the buffer zone B.
- a holder 42 for an injection valve of the internal combustion engine 12 is arranged in the antechamber 67.
- a pressure damper 45 is also integrated for the funded by the fuel pump 23 fuel.
- the pre-chamber 67 and the connecting channel 47 are formed in a hood-shaped air guide member 43.
- the air guide member 43 is held on the crankcase 14.
- the air guide member 43 encloses the holder 42 closely, so that only a narrow flow path for the cooling air is formed between the air guide member 43 and holder 42. This ensures that the holder 42 and arranged in the holder 42 injection valve are well cooled.
- the air guide member 43 does not seal with the crankcase 14 so that the cooling air forced into the air guide member 43 along the arrow 62 can escape into a main chamber 68 of the buffer zone B through gaps formed between the air guide member 43 and the crankcase 14. From the main chamber 68 the cooling air flows out of the housing 2 in the direction of the arrow 49 adjacent to the mounting flange 72.
- FIGS. 3 and 4 show, on the internal combustion engine 12, an exhaust muffler 19 is fixed, which is arranged on the cutting disc 4 facing the front of the housing 2.
- a crankshaft not shown in the figures is rotatably mounted about an axis of rotation 15.
- the axis of rotation 15 of the crankshaft is below the cutting plane and is shown only schematically.
- an overflow channel 18 leads, which opens into a cylinder 17 formed in the combustion chamber.
- the cylinder 17 has a cylinder longitudinal axis 29, which in the in Fig. 1 shown usual parking position 69 against the in Fig. 1 shown vertical 79 is slightly inclined rearwardly toward the upper handle 6.
- a throttle element in the embodiment, a throttle valve 22, is pivotally mounted.
- an intake passage 30 is guided, the combustion air into the crankcase interior 16 supplies.
- the throttle housing 21 is connected via an intake 20 with a fixed to the air filter bottom of the air filter channel section 53.
- the intake manifold 20 is made of an elastic material and is therefore elastic. Due to its elasticity, the intake manifold can compensate for relative movements between the motor unit 24, on which the throttle housing 21 is fixed, and the tank housing 25 with the channel section 53.
- the arranged in the buffer zone B intake 20 bridges the vibration gap 60.
- a further anti-vibration element 64 which bridges the oscillation gap 60, is shown between a web 59 of the tank housing 25 projecting in the direction of the separating disk 4 and the motor unit 24.
- a plurality of anti-vibration elements 64 are arranged between the web 59 and the motor unit 24, which are arranged next to the web 59 and which are not shown in the figures.
- the combustion air is sucked through the second cooling zone C from the environment via the fuel pump 23 into the air inlet openings 73 of the air cleaning unit 71.
- the fan 28 conveys cooling air into the first cooling zone A, which is formed in the space between the engine cover 27 and the cylinder 17, in the direction of the arrow 61 (FIG. Fig. 4 ). Cooling air is forced into the buffer zone from an overpressure region of the fan wheel spiral 78 into the prechamber 67 arranged below the venting guide component 43. The air escapes into the environment via the main chamber 68 of the buffer zone B.
- the combustion air is purified in the air cleaning unit 71 and supplied via the channel section 53, the intake manifold 20 and the throttle body 21 in the crankcase interior 16.
- the fuel / air mixture from the crankcase interior 16 flows via the overflow channel 18, which opens with at least one overflow opening, not shown, into a combustion chamber formed in the cylinder 17, into the combustion chamber.
- the overflow openings are also controlled by the piston. After combustion, the exhaust gases escape from the combustion chamber via a likewise slot-controlled outlet in the exhaust muffler 19th
- a discharge channel 39 is formed.
- the discharge channel 39 is formed as a depression in the wall of the tank housing 25.
- the discharge channel 39 is connected downstream of the fuel pump 23 to the second cooling zone C.
- the discharge channel 39 extends under a lower partition wall section 34 formed on the tank housing 25.
- the lower partition wall section 34 is part of the dividing wall which separates the second cooling zone C from the buffer zone B.
- the discharge channel 39 extends through the dividing wall.
- the discharge channel 39 extends in the usual Abstellposition 69 from the second cooling zone C in the buffer zone B sloping. There are no depressions formed where liquid could accumulate.
- In Abstellposition 69 in the second cooling zone C accumulated liquid via the discharge channel 39 under the partition wall section 34 through into the buffer zone B and from there into the environment. This ensures that, despite the separation of the buffer zone B from the second cooling zone C, no liquid can accumulate in the second cooling zone C.
- the liquid may, for example, be water which is used during operation of the cutting-off grinder 1 for cooling the separating disk 4.
- Fig. 5 shows a view of the cyclone 33 and in the fuel tank 32.
- the tank housing 25 is in the in Fig. 5 formed plane shown divided.
- the cyclones 33 separate coarse dirt particles from the intake combustion air. These dirt particles are fed to a discharge channel 50 formed on the tank housing 25, which open into a negative pressure region in the fan wheel housing 44. As a result, dirt particles are sucked into the Lüfterradgephase 44 and discharged from there.
- the channel portion 53 in which a portion of the suction passage 30 is guided passes through the partition wall formed between the second cooling zone C and the buffer zone B.
- the lower, integrally formed on the tank housing 25 partition wall portion 34 has an approximately semicircular opening for receiving the channel portion 53.
- a corresponding semicircular receptacle for the channel portion 53 also has the upper partition wall portion 35th
- the upper partition wall portion 35 is formed on a separately formed mounting aid 36.
- the two arms 37 of the mounting aid 36 project up to the hood 8 upwards.
- the receptacle 38 is adjacent to the hood 8, in the vicinity of the pivot point of the throttle lever 10 is arranged.
- a control unit 80 is arranged, which serves to control the internal combustion engine 12 and possibly other electrical components of the cutting grinder 1.
- the control unit 80 delimits the cooling zone C and the buffer zone B.
- the control unit 80 has a housing 81, on which a rib 82 projecting downwards in the parking position 69 is formed, which forms a partition wall section of the dividing wall between the second cooling zone C and the buffer zone B. forms.
- the rib 82 is located on a wall 83 of the mounting aid 36 (see also Fig. 6 ) and extends to a bottom 84 of the mounting aid 36.
- the bottom 84 extends transversely to the wall 83 and the rib 82 and extends in the parking position 69 is approximately horizontal.
- the rib 82 which rests against the wall 83 and the bottom 84, there is a substantial dense separation of buffer zone B and second cooling zone C in this area.
- the rib 82, the wall 83 and the bottom 84 act in the manner of a labyrinth seal.
- Fig. 8 shows the design of the tank housing 25 with the web 59, the integrally formed discharge channel 39 and the integrally formed on the tank housing 25 lower partition wall portion 34th Fig. 8 also shows the tank opening 52, in which a closure for the tank lid is fixed.
- the port 51 has two ports 54, wherein one of the terminals 54 for connection to the fuel pump 23 and the other of the terminals 54 is used for connection to a coming from the injection valve return line for fuel.
- Fig. 9 shows a perspective view of the engine unit 24, wherein the arranged under the engine cover 27 cylinder 17 is not shown, so that a Zylinderan gleichflansch 55 of the crankcase 14 is visible.
- a mounting opening 48 is arranged, which opens into the crankcase interior 16 and in which one or more sensors, such as a combined pressure-temperature sensor, can be arranged.
- Fig. 9 also schematically shows the holder 42 arranged in the injection valve 26, which supplies the fuel directly into the crankcase interior 16. As Fig.
- a partition wall portion 85 is formed on the air guide member 43, which abuts against the engine cover 27 and forms with this the partition wall between the first cooling zone A and buffer zone B. Adjacent to the Lüfterradgekoruse 44, a guide portion 86 is arranged. The guide portion 86 is also formed on the air guide member 43 and serves to guide in Fig. 9 not shown electrical cables. In addition, two ribs 87 are integrally formed on the air guide component 43, between which a cable, not shown, is guided and clamped.
- Fig. 10 schematically shows the course of the cooling air flow in the buffer zone B.
- the cooling air flows from the overpressure zone in the fan housing 44 along the arrow 62 through the connecting channel 47 in the formed under the cover antechamber 67.
- the cooling air flows around the holder 42 and thus cools both the injection valve 26 and the pressure damper 45.
- the holder 42 is advantageously made of plastic, so that it acts as an insulator and little heat is transferred from the crankcase 14 to the injection valve 26.
- the cooling air flows through the in Fig. 11 shown gap 77, which extends advantageously over the entire edge of the air guide member 43, in the main chamber 68. In the main chamber 68, the cooling air flows along the in Fig.
- a clutch which is advantageously designed as a centrifugal clutch, and a drive wheel for a V-belt for driving the cutting disc 4.
- a starting device for the internal combustion engine 12 may be arranged on the mounting flange 72.
- a flow guide rib 76 is formed on the air guide component 43, which divides the inflowing cooling air, as shown by the arrows 62. A portion of the cooling air flows to the pressure damper 45 and another part of the cooling air flows around the holder 42 in the region of the injection valve 26. As a result, the pressure damper 45 and the injection valve 26 are well cooled.
- Fig. 12 shows a view under the engine cover 27, wherein the cylinder 17 is not shown. As a result, the throttle valve 22 in the intake passage 30 and the Zylinderan gleichflansch 55 are visible.
- the Lüfterradgepuruse 44 has an opening 31 in the upper, the cylinder 17 adjacent region of the Lüfterradgephaseuses 44 through which the cooling air is conveyed along the arrow 61 from a pressure range of the Lüfterradgephinuses 44 under the engine cover 27 and the cylinder 17 is cooled.
- the motor unit 24 engages over the web 59 of the tank housing 25th
- Fig. 12 also shows the parting plane 56 of the crankcase 14. The parting plane 56 is parallel to the in Fig. 12 schematically drawn cylinder longitudinal axis 29 and towards the in Fig. 12 also schematically drawn axis of rotation 15 of the crankshaft laterally offset to the cylinder longitudinal axis 29th
- the cooling air is conveyed into the first cooling zone A and into the buffer zone B by the fan wheel 28.
- the buffer zone B is flowed through by the air sucked by the fan 28 cooling air.
- the air sucked in by the fan is cooler than the air delivered by the fan 28, since the air heats up due to the compression work of the fan 28.
- the cooling air is advantageously transported from a lower, in the parking position 69 (FIG. Fig. 1 ) is sucked to the floor facing the area of the cutting grinder 1 and passes through an opening, in particular the connecting opening 46, in the fan housing 44th
Description
Die Erfindung betrifft ein Arbeitsgerät der im Oberbegriff des Anspruchs 1 angegebenen Gattung.The invention relates to a working device of the type specified in the preamble of
Aus der
Der Erfindung liegt die Aufgabe zugrunde, ein Arbeitsgerät der gattungsgemäßen Art zu schaffen, bei dem eine verbesserte Kühlung der Kraftstoffpumpe erreicht wird.The invention has for its object to provide a working device of the generic type, in which an improved cooling of the fuel pump is achieved.
Diese Aufgabe wird durch ein Arbeitsgerät mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by a working device with the features of
Das Arbeitsgerät besitzt mehrere Kühlzonen. In einer ersten Kühlzone ist der Zylinder des Verbrennungsmotors angeordnet, der im Betrieb das heißeste Bauteil des Arbeitsgeräts ist. In einer zweiten Kühlzone ist die Kraftstoffpumpe angeordnet. Zwischen der ersten und der zweiten Kühlzone ist eine Pufferzone ausgebildet, die sowohl von der ersten Kühlzone als auch von der zweiten Kühlzone über jeweils mindestens eine Trennwand getrennt ist. Die Pufferzone bewirkt eine gute thermische Trennung der ersten und der zweiten Kühlzone. Dadurch kann eine übermäßige Erwärmung der Kraftstoffpumpe im Betrieb vermieden werden. Bei übermäßiger Erwärmung der Kraftstoffpumpe können sich in der Kraftstoffpumpe Gasblasen bilden, die verhindern, dass weiter Kraftstoff zum Verbrennungsmotor gefördert werden kann. Eine übermäßige Erwärmung der Kraftstoffpumpe muss deshalb vermieden werden. Zwischen der ersten und der zweiten Kühlzone ist eine Pufferzone angeordnet. Dadurch ergibt sich eine räumliche Trennung der Kraftstoffpumpe vom Zylinder, die ebenfalls eine übermäßige Erwärmung der Kraftstoffpumpe verhindert.The implement has several cooling zones. In a first cooling zone, the cylinder of the internal combustion engine is arranged, which is the hottest component of the working device during operation. In a second cooling zone, the fuel pump is arranged. Between the first and the second cooling zone, a buffer zone is formed, which is separated from both the first cooling zone and the second cooling zone via at least one partition wall. The buffer zone causes a good thermal separation of the first and the second cooling zone. This can prevent excessive heating of the fuel pump during operation. Excessive heating of the fuel pump can form gas bubbles in the fuel pump, which prevent further fuel to the engine can be promoted. Excessive heating of the fuel pump must therefore be avoided. Between the first and the second cooling zone, a buffer zone is arranged. This results in a spatial separation of the fuel pump from the cylinder, which also prevents excessive heating of the fuel pump.
Durch die Pufferzone wird auch bei abgestelltem Verbrennungsmotor während des Nachheizens des Verbrennungsmotors ein übermäßiges Aufheizen der Kraftstoffpumpe verringert. Das Nachheizen des Verbrennungsmotors bezeichnet die Zeitspanne nach dem Abstellen des Verbrennungsmotors, während der sich die Wärme in den Bauteilen verteilt. Dabei kühlt der Zylinder des Verbrennungsmotors ab und gibt seine Wärme an andere Bauteile, insbesondere an benachbarte Bauteile wie das Kurbelgehäuse, ab, die sich dadurch erwärmen. Da während des Nachheizens keine Kühlluft mehr gefördert wird, können an einzelnen Bauteilen während des Nachheizens höhere Temperaturen entstehen als im Betrieb. Durch die Pufferzone wird die Wärmeübertragung auf die Kraftstoffpumpe während des Nachheizens verringert. Die Trennwände trennen die Kühlzonen von der Pufferzone dabei nicht zwingend dichtend, sondern mindestens teilweise. Die Trennwände stellen insbesondere eine weitgehende Trennung her, die sicherstellt, dass die Luftströme in den Kühlzonen und der Pufferzone im Wesentlichen getrennt voneinander strömen. An geeigneten Stellen kann eine im Wesentlichen dichte Trennung durch die mindestens eine Trennwand vorteilhaft sein.Due to the buffer zone, an excessive heating of the fuel pump is reduced even when the internal combustion engine is switched off during reheating of the internal combustion engine. The reheating of the internal combustion engine refers to the period of time after the engine is switched off, during which the heat is distributed in the components. In this case, the cylinder of the internal combustion engine cools down and gives off its heat to other components, in particular to adjacent components such as the crankcase, which heat up as a result. Since cooling air is no longer conveyed during reheating, higher temperatures can occur at individual components during reheating than during operation. The buffer zone reduces heat transfer to the fuel pump during reheating. The partitions do not necessarily separate the cooling zones from the buffer zone, but at least partially. In particular, the partitions provide a substantial separation which ensures that the air streams in the cooling zones and the buffer zone flow substantially separately from each other. At suitable locations, a substantially dense separation through the at least one partition may be advantageous.
Um eine gute Kühlung der Kraftstoffpumpe im Betrieb zu erreichen, ist vorgesehen, dass die zweite Kühlzone im Strömungsweg der vom Verbrennungsmotor angesaugten Verbrennungsluft liegt. Das Arbeitsgerät besitzt ein Lüfterrad, das zur Förderung von Kühlluft dient. Die vom Verbrennungsmotor angesaugte Verbrennungsluft wurde nicht wie die vom Lüfterrad geförderte Luft bereits verdichtet und dadurch erwärmt. Die vom Verbrennungsmotor angesaugte Verbrennungsluft ist dadurch etwas kühler als die vom Lüfterrad geförderte Kühlluft. Vorteilhaft besitzt das Arbeitsgerät eine Ansaugöffnung, über die die Kühlluft in die zweite Kühlzone angesaugt wird. Vorteilhaft ist die Kraftstoffpumpe im Strömungsweg der durch die Ansaugöffnung einströmenden Kühlluft angeordnet. Die Kraftstoffpumpe ist insbesondere unmittelbar benachbart zu der Ansaugöffnung in die zweite Kühlzone angeordnet. Die die Kraftstoffpumpe kühlende Verbrennungsluft ist dadurch noch nicht durch andere Bauteile erwärmt, so dass sich eine sehr gute Kühlung der Kraftstoffpumpe ergibt. Die Verbrennungsluft wird vorteilhaft direkt aus der Umgebung in die zweite Kühlzone angesaugt. Die Ansaugöffnung ist dabei insbesondere in einem Bereich angeordnet, der einen möglichst großen Abstand zum Austritt der durch die erste Kühlzone strömenden Kühlluft aus dem Arbeitsgerät, also zum Austritt der Kühlluft, die den Zylinder kühlt, besitzt.In order to achieve a good cooling of the fuel pump during operation, it is provided that the second cooling zone lies in the flow path of the combustion air sucked by the internal combustion engine. The implement has a fan wheel which serves to convey cooling air. The combustion air sucked in by the internal combustion engine was not already compressed, and thus heated, like the air conveyed by the fan wheel. The combustion air sucked in by the internal combustion engine is thereby somewhat cooler than the cooling air conveyed by the fan wheel. Advantageously, the implement has an intake opening, via which the cooling air is sucked into the second cooling zone. The fuel pump is advantageously arranged in the flow path of the cooling air flowing through the intake opening. The fuel pump is in particular immediately adjacent to the intake opening in the second cooling zone arranged. The cooling of the fuel pump combustion air is thus not yet heated by other components, so that there is a very good cooling of the fuel pump. The combustion air is advantageously sucked directly from the environment into the second cooling zone. The intake opening is arranged in particular in a region which has the largest possible distance to the outlet of the cooling air flowing through the first cooling zone from the working device, ie to the outlet of the cooling air, which cools the cylinder.
Zwischen der ersten und der zweiten Kühlzone ist die Pufferzone angeordnet. Vorteilhaft wird die Kühlluft in die Pufferzone vom Lüfterrad gefördert. Dadurch ergibt sich eine gute Kühlung der Pufferzone, und die Wärmeübertragung von der ersten Kühlzone auf die zweite Kühlzone wird minimiert. Die Pufferzone kann dabei auf der Saugseite des Lüfterrads, also stromauf des Lüfterrads, oder auf der Druckseite des Lüfterrads, also stromab des Lüfterrads, angeordnet sein. Eine einfache Anordnung ergibt sich bei einer Anordnung der Pufferzone stromab des Lüfterrads, also wenn das Lüfterrad die Kühlluft in die Pufferzone drückt. Es kann jedoch auch vorteilhaft sein, dass das Lüfterrad die Kühlluft durch die Pufferzone saugt, die Pufferzone also stromauf des Lüfterrads liegt. Insbesondere wird die Kühlluft in diesem Fall von einem in üblicher Abstellposition des Arbeitsgeräts unten liegenden Bereich angesaugt und gelangt über eine Öffnung im Lüfterradgehäuse in das Lüfterradgehäuse. Die vom Lüfterrad angesaugte Kühlluft wurde vom Lüfterrad noch nicht verdichtet und ist deshalb kühler als die vom Lüfterrad abströmende Kühlluft, so dass sich durch die Anordnung der Pufferzone in dem vom Lüfterrad angesaugten Kühlluftstrom eine effektive Kühlung der Pufferzone ergibt.Between the first and the second cooling zone, the buffer zone is arranged. Advantageously, the cooling air is conveyed into the buffer zone by the fan. This results in a good cooling of the buffer zone, and the heat transfer from the first cooling zone to the second cooling zone is minimized. The buffer zone can be arranged on the suction side of the fan wheel, ie upstream of the fan wheel, or on the pressure side of the fan wheel, ie downstream of the fan wheel. A simple arrangement results in an arrangement of the buffer zone downstream of the fan, so when the fan presses the cooling air in the buffer zone. However, it may also be advantageous that the fan wheel sucks the cooling air through the buffer zone, that is, the buffer zone is upstream of the fan. In particular, the cooling air is sucked in this case from a lying in the usual parking position of the implement below area and passes through an opening in the fan housing in the fan housing. The sucked by the fan cooling air was not yet compressed by the fan and is therefore cooler than the cooling air flowing from the fan, so that the arrangement of the buffer zone in the sucked by the fan cooling air flow effective cooling of the buffer zone results.
Vorteilhaft ist das Einspritzventil in der Pufferzone angeordnet. Dadurch, dass das Einspritzventil nicht in der ersten Kühlzone, sondern in einer von der ersten Kühlzone durch eine Trennwand mindestens teilweise getrennten Pufferzone angeordnet ist, kann eine verbesserte Kühlung des Einspritzventils erreicht werden. Vorteilhaft ist benachbart zum Einspritzventil ein Druckdämpfer in der Pufferzone angeordnet. Auch der Druckdämpfer muss im Betrieb möglichst gut gekühlt werden, um eine Gasblasenbildung im Druckdämpfer zu verhindern. Gleichzeitig ist es vorteilhaft, den Druckdämpfer so nah wie möglich am Einspritzventil anzuordnen. Dies kann dadurch erreicht werden, dass der Druckdämpfer benachbart zum Einspritzventil in der Pufferzone angeordnet wird.Advantageously, the injection valve is arranged in the buffer zone. Because the injection valve is not arranged in the first cooling zone but in a buffer zone which is at least partially separated from the first cooling zone by a dividing wall, improved cooling of the injection valve can be achieved. Advantageously, a pressure damper is arranged in the buffer zone adjacent to the injection valve. The pressure damper must also be cooled as well as possible during operation in order to prevent gas bubble formation in the pressure damper. At the same time it is advantageous, the pressure damper as close as possible to the injection valve to arrange. This can be accomplished by placing the pressure damper adjacent to the injector in the buffer zone.
Um eine möglichst gute Kühlung von Einspritzventil und Druckdämpfer zu erreichen, ist vorgesehen, dass das Einspritzventil in einem Bereich angeordnet ist, der über einen Verbindungskanal mit dem Innenraum des Lüfterradgehäuses verbunden ist. Dadurch kann die Kühlluft zielgerichtet in den Bereich geleitet werden, in dem das Einspritzventil angeordnet ist. Der Kanal ist dabei möglichst kurz ausgebildet, um den Strömungswiderstand gering zu halten und eine möglichst unmittelbare Kühlung des Bereichs, in dem das Einspritzventil angeordnet ist, zu erreichen. Die Kühlung des Einspritzventils kann verbessert werden, wenn das Einspritzventil in einer Vorkammer der Pufferzone angeordnet wird, aus der die Kühlluft in eine Hauptkammer der Pufferzone strömt. Die Unterteilung der Pufferzone in eine Vorkammer und eine Hauptkammer ermöglicht eine verbesserte, unmittelbare Kühlung des Einspritzventils und ggf. des Druckdämpfers. Die in die Pufferzone einströmende Luft gelangt direkt zum Einspritzventil und zum Druckdämpfer, bevor sie durch andere Bauteile erwärmt wurde. Die Vorkammer ist dabei vorteilhaft klein ausgebildet, so dass die Kühlluft zielgerichtet zum Einspritzventil bzw. einem das Einspritzventil umgebenden Bauteil geführt wird.In order to achieve the best possible cooling of injection valve and pressure damper, it is provided that the injection valve is arranged in a region which is connected via a connecting channel with the interior of the fan wheel housing. As a result, the cooling air can be directed to the area in which the injection valve is arranged. The channel is designed to be as short as possible in order to keep the flow resistance low and to achieve the most direct possible cooling of the region in which the injection valve is arranged. The cooling of the injection valve can be improved if the injection valve is arranged in an antechamber of the buffer zone, from which the cooling air flows into a main chamber of the buffer zone. The subdivision of the buffer zone into an antechamber and a main chamber allows for improved, direct cooling of the injection valve and possibly the pressure damper. The air entering the buffer zone goes directly to the injector and the pressure damper before being heated by other components. The pre-chamber is advantageously made small, so that the cooling air is purposefully guided to the injection valve or a component surrounding the injection valve.
Ein einfacher Aufbau ergibt sich, wenn die Vorkammer von einem Luftführungsbauteil von der Hauptkammer getrennt ist. Das Luftführungsbauteil ist vorteilhaft an einem Kurbelgehäuse des Verbrennungsmotors gehalten. Die Kühlluft strömt dabei vorteilhaft zwischen dem Luftführungsbauteil und dem Kurbelgehäuse in die Hauptkammer. Die Verbindungsöffnung zwischen Vorkammer und Hauptkammer der Pufferzone wird auf einfache Weise dadurch gebildet, dass das Luftführungsbauteil gegenüber dem Kurbelgehäuse des Verbrennungsmotors nicht abgedichtet ist, sondern zu diesem einen geringen Abstand besitzt. Dadurch wird auch die direkte Aufheizung des Luftführungsbauteils, die durch den Kontakt mit dem Kurbelgehäuse hervorgerufen wird, verringert. Das Luftführungsbauteil umschließt die in der Vorkammer angeordneten Komponenten vorteilhaft möglichst eng, so dass sichergestellt ist, dass die Komponenten von der Kühlluft umströmt und gut gekühlt werden.A simple construction results when the prechamber is separated from an air guiding component by the main chamber. The air guide component is advantageously held on a crankcase of the internal combustion engine. The cooling air flows advantageous between the air guide member and the crankcase in the main chamber. The connection opening between the prechamber and the main chamber of the buffer zone is formed in a simple manner in that the air guiding component is not sealed with respect to the crankcase of the internal combustion engine, but has a small distance to it. As a result, the direct heating of the air guide component, which is caused by the contact with the crankcase, is reduced. The air guide component advantageously encloses the components arranged in the pre-chamber as closely as possible, so that it is ensured that the components are flowed around by the cooling air and are well cooled.
Vorteilhaft ist die erste Trennwand mindestens teilweise von einem Abschnitt einer Motorabdeckung gebildet. Die Motorabdeckung ist vorteilhaft innerhalb des Außengehäuses des Arbeitsgeräts angeordnet und von einer Haube des Arbeitsgeräts abgedeckt. Dadurch kann ein Kontakt des Bedieners mit der sich im Betrieb erwärmenden Motorabdeckung vermieden werden. Die Motorabdeckung deckt den Zylinder des Verbrennungsmotors ab. Unter die Motorabdeckung fördert das Lüfterrad Kühlluft. Besonders vorteilhaft wird die Kühlluft unter die Motorabdeckung gedrückt. Es kann jedoch auch vorgesehen sein, das Lüfterrad so anzuordnen, dass die Kühlluft unter die Motorabdeckung angesaugt wird, die erste Kühlzone also auf der Saugseite des Lüfterrads liegt. Es kann vorteilhaft sein, dass die erste Trennwand mindestens teilweise von dem Luftführungsbauteil begrenzt ist.Advantageously, the first partition is at least partially formed by a portion of an engine cover. The engine cover is advantageously disposed within the outer housing of the implement and covered by a hood of the implement. This makes it possible to avoid contact between the operator and the engine cover which heats up during operation. The engine cover covers the cylinder of the internal combustion engine. Under the engine cover, the fan promotes cooling air. Particularly advantageously, the cooling air is pressed under the engine cover. However, it may also be provided to arrange the fan so that the cooling air is sucked under the engine cover, so the first cooling zone is located on the suction side of the fan. It may be advantageous that the first partition is at least partially bounded by the air guide component.
Vorteilhaft ist mindestens ein Trennwandabschnitt der zweiten Trennwand an dem Tankgehäuse des Arbeitsgeräts angeformt. Die Pufferzone liegt vorteilhaft zwischen einem Luftfilter des Arbeitsgeräts und dem Verbrennungsmotor. Der Verbrennungsmotor besitzt einen Ansaugkanal, der den Verbrennungsmotor mit dem Luftfilter verbindet und der aufgrund der Anordnung der Pufferzone zwischen Luftfilter und Verbrennungsmotor durch die Pufferzone geführt ist. Es ist vorgesehen, dass der Ansaugkanal des Verbrennungsmotors durch die zweite Trennwand ragt. Ein einfacher Aufbau ergibt sich, wenn mindestens ein Trennwandabschnitt der zweiten Trennwand an einem separaten, an dem Tankgehäuse fixierten Bauteil ausgebildet ist. Die beiden Trennwandabschnitte begrenzen vorteilhaft die Durchtrittsöffnung für den Ansaugkanal, so dass der Ansaugkanal auf das Tankgehäuse aufgelegt und das separate Bauteil auf dem Tankgehäuse aufgesetzt und an diesem fixiert werden kann. Dadurch wird ein einfacher Aufbau und eine einfache Montage erreicht.Advantageously, at least one partition wall section of the second partition is integrally formed on the tank housing of the implement. The buffer zone is advantageously located between an air filter of the working device and the internal combustion engine. The internal combustion engine has an intake passage which connects the internal combustion engine with the air filter and which is guided through the buffer zone due to the arrangement of the buffer zone between the air filter and the internal combustion engine. It is envisaged that the intake passage of the internal combustion engine protrudes through the second partition wall. A simple construction results if at least one partition wall section of the second partition wall is formed on a separate component fixed to the tank housing. The two partition wall sections advantageously limit the passage opening for the intake passage, so that the intake passage can be placed on the tank housing and the separate component can be placed on the tank housing and fixed thereto. As a result, a simple structure and a simple assembly is achieved.
Arbeitsgeräte wie beispielsweise Trennschleifer oder dgl. arbeiten im Betrieb mit Wasser. Um eine Abfuhr von im Betrieb angesammelter Flüssigkeit im Gehäuse des Arbeitsgeräts zu ermöglichen, ist vorgesehen, dass durch die zweite Trennwand ein Ableitkanal zur Flüssigkeitsabfuhr aus der zweiten Kühlzone in die Pufferzone führt. Der Ableitkanal ist vorteilhaft als Vertiefung in einer die zweite Kühlzone begrenzenden Wand des Tankgehäuses ausgebildet. Dadurch ergibt sich ein einfacher Aufbau. Für den Ableitkanal werden keine zusätzlichen Bauteile benötigt. Vorteilhaft fällt der Ableitkanal in Abstellposition des Arbeitsgeräts von der zweiten Kühlzone zur Pufferzone ab. Dadurch wird gewährleistet, dass Flüssigkeit aus der zweiten Kühlzone in die Pufferzone strömen kann. Vorteilhaft fließt die Flüssigkeit aus der Pufferzone in die Umgebung ab. Im Betrieb kann der Luftdruck in der Pufferzone höher sein als der Luftdruck in der zweiten Kühlzone, insbesondere, wenn die Kühlluft in die Pufferzone vom Lüfterrad des Arbeitsgeräts gefördert wird. Um zu verhindern, dass aus der Pufferzone warme Luft auf die in der zweiten Kühlzone angeordnete Kraftstoffpumpe strömt, ist vorgesehen, dass der Ableitkanal bezogen auf die Strömungsrichtung in der zweiten Kühlzone stromab der Kraftstoffpumpe mit der zweiten Kühlzone verbunden ist. Luft, die aus der Pufferzone in die zweite Kühlzone strömt, kann dadurch nicht zur Kraftstoffpumpe strömen, sondern wird zum Verbrennungsmotor angesaugt.Work tools such as cutters or the like. Work in operation with water. In order to enable a removal of liquid accumulated during operation in the housing of the working device, it is provided that a discharge channel for liquid removal from the second cooling zone leads into the buffer zone through the second partition wall. The discharge channel is advantageous as a depression in a wall bounding the second cooling zone of the tank housing educated. This results in a simple structure. For the discharge channel no additional components are needed. Advantageously, the discharge channel falls in the parking position of the working device from the second cooling zone to the buffer zone. This ensures that liquid from the second cooling zone can flow into the buffer zone. Advantageously, the liquid flows from the buffer zone into the environment. In operation, the air pressure in the buffer zone may be higher than the air pressure in the second cooling zone, in particular, when the cooling air is conveyed into the buffer zone by the fan of the implement. In order to prevent warm air from flowing out of the buffer zone onto the fuel pump arranged in the second cooling zone, it is provided that the discharge channel is connected to the second cooling zone downstream of the fuel pump in relation to the flow direction in the second cooling zone. Air that flows from the buffer zone into the second cooling zone can not thereby flow to the fuel pump, but is sucked to the engine.
Im Betrieb des Verbrennungsmotors entstehen starke Vibrationen. Damit der Bediener das Arbeitsgerät an Handgriffen des Arbeitsgeräts gut führen kann, sind die Handgriffe üblicherweise vom Verbrennungsmotor über Antivibrationselemente schwingungsentkoppelt. Um eine Relativbewegung der Griffe zum Verbrennungsmotor zu erlauben, ist zwischen dem Verbrennungsmotor und den Handgriffen üblicherweise ein Schwingspalt ausgebildet. Vorteilhaft verläuft der Schwingspalt zwischen dem Tankgehäuse und dem Verbrennungsmotor. Der Schwingspalt verläuft dabei vorteilhaft durch die Pufferzone. Die Kraftstoffpumpe ist vorteilhaft am Tankgehäuse festgelegt und über den durch die Pufferzone verlaufenden Schwingspalt von dem in der ersten Kühlzone angeordneten Zylinder getrennt. Dadurch ergibt sich ein großer Abstand zwischen Kraftstoffpumpe und Zylinder, der sicherstellt, dass die Kraftstoffpumpe nicht unzulässig erwärmt wird. Aufgrund des durch die Pufferzone verlaufenden Schwingspalts ändert sich im Betrieb bei Relativbewegungen von Tankgehäuse und Verbrennungsmotor das Volumen der Pufferzone. Die Anordnung eines festen Isolierkörpers, der die Pufferzone ausfüllt, ist nicht möglich, da dieser Isolierkörper die Relativbewegung zwischen Tankgehäuse und Verbrennungsmotor behindern würde. Durch die Anordnung der Pufferzone zwischen den beiden Kühlzonen kann dennoch eine gute thermische Trennung der Kraftstoffpumpe vom Verbrennungsmotor erreicht werden.During operation of the internal combustion engine, strong vibrations occur. In order for the operator to be able to easily guide the implement by means of handles of the implement, the handles are usually vibration-decoupled from the internal combustion engine via anti-vibration elements. In order to allow a relative movement of the handles to the engine, a vibrating gap is usually formed between the engine and the handles. Advantageously, the oscillation gap extends between the tank housing and the internal combustion engine. The oscillation gap advantageously extends through the buffer zone. The fuel pump is advantageously fixed to the tank housing and separated by the extending through the buffer zone oscillation gap of the arranged in the first cooling zone cylinder. This results in a large distance between the fuel pump and the cylinder, which ensures that the fuel pump is not heated inadmissible. Due to the oscillation gap running through the buffer zone, the volume of the buffer zone changes during operation in the case of relative movements of the tank housing and the internal combustion engine. The arrangement of a solid insulating body, which fills the buffer zone is not possible because this insulator would hinder the relative movement between the tank housing and the engine. By arranging the buffer zone between the two cooling zones Nevertheless, a good thermal separation of the fuel pump can be achieved by the internal combustion engine.
Ein Ausführungsbeispiel der Erfindung wird im Folgenden anhand der Zeichnung erläutert. Es zeigen:
- Fig. 1
- eine schematische Seitenansicht eines Trennschleifers,
- Fig. 2
- eine Ansicht auf Motoreinheit und Tankgehäuse des Trennschleifers aus
Fig. 1 in Richtung des Pfeils II inFig. 1 , - Fig. 3
- einen Schnitt durch Motoreinheit und Tankgehäuse oberhalb der Drehachse der Kurbelwelle,
- Fig. 4
- eine teilgeschnittene Seitenansicht von Tankgehäuse und Motoreinheit in Richtung des Pfeils IV in
Fig. 2 , - Fig. 5
- eine Seitenansicht in Richtung des Pfeils V in
Fig. 4 , - Fig. 6
- eine perspektivische Darstellung der Montagehilfe,
- Fig. 7
- eine ausschnittsweise teilgeschnittene Seitenansicht von Tankgehäuse und Motoreinheit in Richtung des Pfeils IV in
Fig. 2 , - Fig. 8
- eine perspektivische Darstellung des Tankgehäuses,
- Fig. 9
- eine perspektivische Ansicht der Motoreinheit,
- Fig. 10
- eine Seitenansicht auf die Motoreinheit in Richtung des Pfeils X in
Fig. 4 , - Fig. 11
- eine perspektivische Schnittdarstellung der Motoreinheit auf der Höhe des Kraftstoffventils,
- Fig. 12
- eine Seitenansicht der Motoreinheit in Richtung des Pfeils XII in
Fig. 4 ohne Zylinder und Abgasschalldämpfer.
- Fig. 1
- a schematic side view of a cutting grinder,
- Fig. 2
- a view of the motor unit and tank housing of the cutting off
Fig. 1 in the direction of arrow II inFig. 1 . - Fig. 3
- a section through the engine unit and tank housing above the axis of rotation of the crankshaft,
- Fig. 4
- a partially sectioned side view of the tank housing and motor unit in the direction of arrow IV in
Fig. 2 . - Fig. 5
- a side view in the direction of arrow V in
Fig. 4 . - Fig. 6
- a perspective view of the mounting aid,
- Fig. 7
- a partially sectioned side view of tank housing and motor unit in the direction of arrow IV in
Fig. 2 . - Fig. 8
- a perspective view of the tank housing,
- Fig. 9
- a perspective view of the motor unit,
- Fig. 10
- a side view of the motor unit in the direction of arrow X in
Fig. 4 . - Fig. 11
- a perspective sectional view of the engine unit at the height of the fuel valve,
- Fig. 12
- a side view of the motor unit in the direction of arrow XII in
Fig. 4 without cylinder and exhaust silencer.
Der Trennschleifer 1 besitzt ein Gehäuse 2, dessen Aufbau im Folgenden noch näher erläutert wird. An dem Gehäuse 2 ist ein Ausleger 3 festgelegt, der nach vorne ragt und an dessen freiem Ende eine Trennscheibe 4 drehbar gelagert ist, die mindestens teilweise von einer Schutzhaube 5 abgedeckt ist. Zum Führen des Trennschleifers 1 dient ein oberer Handgriff 6, der an einer Haube 8 des Gehäuses 2 ausgebildet ist, sowie ein Griffrohr 7, das das Gehäuse 2 an der der Trennscheibe 4 zugewandten Seite übergreift. An der der Trennscheibe 4 abgewandten Seite des Gehäuses 2 ist ein Luftfilterdeckel 9 festgelegt. Zum Abstellen des Trennschleifers 1 dienen am Gehäuse 2 und am Griffrohr 7 festgelegte Standfüße 13. Wird der Trennschleifer 1 auf einer ebenen Unterlage abgestellt, so befindet er sich in der in
Im Gehäuse 2 ist ein Verbrennungsmotor 12 angeordnet, der zum rotierenden Antrieb der Trennscheibe 4 dient. Der Verbrennungsmotor 12 ist im Ausführungsbeispiel ein Zweitaktmotor. Der Verbrennungsmotor 12 kann jedoch auch ein gemischgeschmierter oder ein getrenntgeschmierter Viertaktmotor sein. Der Verbrennungsmotor 12 ist vorteilhaft ein Einzylindermotor. Zur Bedienung des Verbrennungsmotors 12 dient ein am oberen Handgriff 6 schwenkbar gelagerter Gashebel 10. Der Gashebel 10 kann nur gedrückt werden, wenn eine ebenfalls am oberen Handgriff 6 gelagerte Gashebelsperre 11 betätigt ist. Um den Verbrennungsmotor 12 mit Kraftstoff zu versorgen, ist eine Kraftstoffpumpe 23 im Gehäuse 2 angeordnet. Die Kraftstoffpumpe 23 ist benachbart zum Luftfilterdeckel 9, also an der der Trennscheibe 4 abgewandten Rückseite des Gehäuses 2 angeordnet. Dadurch lässt sich ein vergleichsweise großer Abstand zwischen dem Verbrennungsmotor 12 und der Kraftstoffpumpe 23 erreichen, wodurch die Wärmeübertragung vom Verbrennungsmotor 12 auf die Kraftstoffpumpe 23 verringert wird. Die Kraftstoffpumpe 23 ist so angeordnet, dass sich ein möglichst großer Abstand zu einem Zylinder 17 (
Unter der Motorabdeckung 27 ist eine erste Kühlzone A ausgebildet, in der ein Zylinder 17 des Verbrennungsmotors 12 angeordnet ist. In die erste Kühlzone A fördert ein vom Verbrennungsmotor 12 angetriebenes Lüfterrad 28 Kühlluft. Die Kühlluft wird entlang der in
Die Kraftstoffpumpe 23 ist in einer zweiten Kühlzone C angeordnet, und zwar unmittelbar benachbart zur Ansaugöffnung 65 (
Zwischen der ersten Kühlzone A und der zweiten Kühlzone C ist eine Pufferzone B ausgebildet. Die Pufferzone B ist von der ersten Kühlzone A durch eine Trennwand getrennt, die von der Motorabdeckung 27 gebildet ist. Die Trennung zwischen der ersten Kühlzone A und der Pufferzone B verläuft in der in
Das Tankgehäuse 25 ist von einer Motoreinheit 24 des Trennschleifers 1 über einen Schwingspalt 60 getrennt. Der Schwingspalt 60 ist von mehreren Antivibrationselementen überbrückt, von denen in
Wie
Die Lufteintrittsöffnungen 73 münden in Zyklone 33, die in
Im Ausführungsbeispiel wird die Verbrennungsluft in die zweite Kühlzone C aus der Umgebung angesaugt. Alternativ könnte jedoch auch vorgesehen sein, Luft aus einem Überdruckbereich des Lüfterradgehäuses 44 in die zweite Kühlzone C und von dort als Verbrennungsluft zu den Lufteintrittsöffnungen 73 zu fördern. Dadurch wird dem Verbrennungsmotor 12 Verbrennungsluft zugeführt, die unter Überdruck steht.In the exemplary embodiment, the combustion air is sucked into the second cooling zone C from the environment. Alternatively, however, it could also be provided to convey air from an overpressure region of the
Das Lüfterradgehäuse 44 bildet eine Lüfterspirale und ist an einem Kurbelgehäuse 14 des Verbrennungsmotors 12 angeformt. Das Lüfterradgehäuse 44 begrenzt eine Lüfterspirale 78. An der dem Kurbelgehäuse 14 zugewandten Rückwand 74 des Lüfterradgehäuses 44 ist in einem Überdruckbereich der Lüfterspirale 78 eine Verbindungsöffnung 46 ausgebildet, in der eine Anschlusstülle 75 angeordnet ist. Die Anschlusstülle 75, die beispielsweise eine Gummitülle sein kann, verbindet den Überdruckbereich des Lüfterradgehäuses 44 mit einem Verbindungskanal 47, der in eine in der Pufferzone B ausgebildete Vorkammer 67 mündet. In der Vorkammer 67 ist ein Halter 42 für ein Einspritzventil des Verbrennungsmotors 12 angeordnet. In den Halter 42 ist außerdem ein Druckdämpfer 45 für den von der Kraftstoffpumpe 23 geförderten Kraftstoff integriert. Die Vorkammer 67 und der Verbindungskanal 47 sind in einem haubenförmigen Luftführungsbauteil 43 ausgebildet. Das Luftführungsbauteil 43 ist am Kurbelgehäuse 14 gehalten. Das Luftführungsbauteil 43 umschließt den Halter 42 eng, so dass zwischen Luftführungsbauteil 43 und Halter 42 nur ein schmaler Strömungspfad für die Kühlluft gebildet ist. Dadurch wird sichergestellt, dass der Halter 42 und das im Halter 42 angeordnete Einspritzventil gut gekühlt werden. Das Luftführungsbauteil 43 schließt nicht dichtend mit dem Kurbelgehäuse 14 ab, so dass die in das Luftführungsbauteil 43 entlang des Pfeils 62 gedrückte Kühlluft durch zwischen dem Luftführungsbauteil 43 und dem Kurbelgehäuse 14 gebildete Spalte in eine Hauptkammer 68 der Pufferzone B entweichen kann. Aus der Hauptkammer 68 strömt die Kühlluft in Richtung des Pfeils 49 benachbart zum Montageflansch 72 aus dem Gehäuse 2 aus.The
Wie die
Am Zylinder 17 ist ein in
Im Betrieb wird die Verbrennungsluft durch die zweite Kühlzone C aus der Umgebung über die Kraftstoffpumpe 23 in die Lufteintrittsöffnungen 73 der Luftreinigungseinheit 71 angesaugt. Das Lüfterrad 28 fördert Kühlluft in die erste Kühlzone A, die im Zwischenraum zwischen der Motorabdeckung 27 und dem Zylinder 17 gebildet ist, in Richtung des Pfeils 61 (
An der die zweite Kühlzone C und die Pufferzone B begrenzenden, in Abstellposition 69 oben liegenden Wand des Tankgehäuses 25 ist ein Ableitkanal 39 ausgebildet. Der Ableitkanal 39 ist als Vertiefung in der Wand des Tankgehäuses 25 ausgebildet. Wie
Wie
Wie auch
Wie
Wie
Im gezeigten Ausführungsbeispiel wird die Kühlluft in die erste Kühlzone A und in die Pufferzone B vom Lüfterrad 28 gefördert. Alternativ kann vorgesehen sein, dass die Pufferzone B von der vom Lüfterrad 28 angesaugten Kühlluft durchströmt ist. Die vom Lüfterrad angesaugte Luft ist kühler als die vom Lüfterrad 28 geförderte Luft, da sich die Luft aufgrund der Verdichtungsarbeit des Lüfterrads 28 erwärmt. Wird die Pufferzone B von der vom Lüfterrad 28 angesaugten Luft durchströmt, so wird die Kühlluft vorteilhaft von einem unteren, in Abstellposition 69 (
Claims (15)
- Working implement with an internal combustion engine (12) which is supplied with fuel via an injector (26), wherein the fuel is delivered by a fuel pump (23) from a fuel tank (32) to the injector (26), wherein the working implement comprises a fan impeller (28) driven by the internal combustion engine (12), wherein the internal combustion engine (12) has a cylinder (17) located in a first cooling zone (A) of the working implement, wherein the fan impeller (28) conveys cooling air through the first cooling zone (A), and wherein the fuel pump (23) is located in a second cooling zone (C) of the working implement,
characterised in that a buffer zone (B) separated from the first cooling zone (A) by at least one first partition and from the second cooling zone (C) by at least one second partition is formed between the first cooling zone (A) and the second cooling zone (C). - Working implement according to claim 1,
characterised in that the second cooling zone (C) lies in the flow path of the combustion air drawn in by the internal combustion engine (12). - Working implement according to claim 2,
characterised in that the cooling air flows into the second cooling zone (C) through an intake opening (65), and in that the fuel pump (23) lies in the flow path of the cooling air flowing through the intake opening (65). - Working implement according to claim 3,
characterised in that the fuel pump (23) is located immediately adjacent to the intake opening (65). - Working implement according to any of claims 2 to 4,
characterised in that the combustion air is drawn into the second cooling zone (C) directly from the environment. - Working implement according to any of claims 1 to 5,
characterised in that cooling air is delivered into the buffer zone (B) by the fan impeller (28). - Working implement according to any of claims 1 to 6,
characterised in that the injector (26) is located in the buffer zone (B). - Working implement according to claim 7,
characterised in that a pressure damper (45) is located adjacent to the injector (26) in the buffer zone (B). - Working implement according to claim 7 or 8,
characterised in that the fan impeller (28) is located in an impeller housing (44), and in that the injector (26) is located in a region which is connected to the interior of the impeller housing (44) via a connecting passage (47). - Working implement according to any of claims 7 to 9,
characterised in that the injector (26) is located in a prechamber (67) of the buffer zone (B), from which cooling air flows into a main chamber (68) of the buffer zone (B), wherein the prechamber (67) is in particular separated from the main chamber (68) by an air ducting component (43), wherein the air ducting component (43) is advantageously held on a crankcase (14) of the internal combustion engine (12), and wherein the cooling air advantageously flows into the main chamber (68) between the air ducting component (43) and the crankcase (14). - Working implement according to any of claims 1 to 10,
characterised in that the first partition is at least partially represented by a section of an engine cover (27), wherein the engine cover (27) covers the cylinder (17) of the internal combustion engine (12), and wherein cooling air is delivered by the fan impeller (28) under the engine cover (27). - Working implement according to any of claims 1 to 11,
characterised in that the fuel tank (32) is formed in a tank housing (25), wherein in particular at least one partition section (34) of the second partition is formed integral with the tank housing (25) of the working implement. - Working implement according to claim 12,
characterised in that a component bounding the intake port (30) of the internal combustion engine (12) projects through the second partition, and in that at least one partition section (35) of the second partition is formed on a separate component secured to the tank housing (25). - Working implement according to claim 12 or 13,
characterised in that a discharge passage (39) for the discharge of fluid from the second cooling zone (C) leads into the buffer zone (B) through the second partition, wherein the discharge passage (39) is advantageously connected to the second cooling zone (C) downstream of the fuel pump (23) in respect to the direction of flow of the air flowing through the second cooling zone (C). - Working implement according to any of claims 12 to 14,
characterised in that the tank housing (25) is separated from the internal combustion engine (12) by swinging gap (60) extending through the buffer zone (B).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011120471A DE102011120471A1 (en) | 2011-12-07 | 2011-12-07 | implement |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2610458A1 EP2610458A1 (en) | 2013-07-03 |
EP2610458B1 true EP2610458B1 (en) | 2014-09-17 |
Family
ID=47602704
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12008124.5A Active EP2610458B1 (en) | 2011-12-07 | 2012-12-05 | Work device |
Country Status (4)
Country | Link |
---|---|
US (1) | US9175594B2 (en) |
EP (1) | EP2610458B1 (en) |
CN (1) | CN103174501B (en) |
DE (1) | DE102011120471A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013012746A1 (en) * | 2013-07-31 | 2015-02-05 | Andreas Stihl Ag & Co. Kg | Hand-held implement |
DE102015013784A1 (en) * | 2015-10-20 | 2017-04-20 | Andreas Stihl Ag & Co. Kg | Hand-held implement |
SE1850338A1 (en) * | 2018-03-27 | 2019-09-28 | Husqvarna Ab | A cooling and air intake arrangement for a combustion engine |
Family Cites Families (33)
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 |
JPS56110509A (en) | 1980-02-05 | 1981-09-01 | Yanmar Diesel Engine Co Ltd | Air-cooled type internal combustion engine |
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 |
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 |
DE4223756C2 (en) | 1992-07-18 | 1997-01-09 | Stihl Maschf Andreas | Fuel pump for a two-stroke engine |
US5488933A (en) | 1994-02-14 | 1996-02-06 | Pham; Roger N. C. | Fuel supply system for miniature engines |
JPH09151739A (en) | 1995-11-30 | 1997-06-10 | Kioritz Corp | 2-cycle internal combustion engine |
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 |
JP2001507632A (en) | 1996-04-12 | 2001-06-12 | ドルマール・ゲゼルシャフト・ミット・ベシュレンクテル・ハフツング | Hand tool with internal combustion engine with electronic direct injection |
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 |
BR0117017A (en) | 2001-05-11 | 2004-04-20 | Electrolux Ab | Clean sump internal combustion engine |
US6701900B1 (en) | 2002-12-31 | 2004-03-09 | Caterpillar Inc. | Quick priming fuel system and common passageway housing for same |
WO2004081386A1 (en) | 2003-03-13 | 2004-09-23 | Yanmar Co., Ltd. | Cover structure for engine |
DE10341600A1 (en) | 2003-09-10 | 2005-04-14 | Andreas Stihl Ag & Co. Kg | Carburetor arrangement of a hand-held implement |
SE0302439D0 (en) | 2003-09-12 | 2003-09-12 | Electrolux Ab | Throttle control device for a hand held tool |
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 |
DE602006004810D1 (en) | 2005-10-07 | 2009-03-05 | Black & Decker | saw |
TWI341773B (en) * | 2005-11-16 | 2011-05-11 | Illinois Tool Works | Fuel supply and combustion chamber systems for fastener-driving tools |
US7552714B2 (en) | 2006-08-16 | 2009-06-30 | Andreas Stihl Ag & Co. Kg | Ignition device for an internal combustion engine and method for its operation |
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 |
JP4488069B2 (en) | 2007-12-27 | 2010-06-23 | 株式会社デンソー | Fuel supply device |
DE102009057731B4 (en) | 2009-12-10 | 2022-02-03 | Andreas Stihl Ag & Co. Kg | Method for operating an implement with a diagnostic device |
-
2011
- 2011-12-07 DE DE102011120471A patent/DE102011120471A1/en not_active Withdrawn
-
2012
- 2012-12-05 EP EP12008124.5A patent/EP2610458B1/en active Active
- 2012-12-07 US US13/707,771 patent/US9175594B2/en active Active
- 2012-12-07 CN CN201210522011.7A patent/CN103174501B/en active Active
Also Published As
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DE102011120471A1 (en) | 2013-06-13 |
US9175594B2 (en) | 2015-11-03 |
EP2610458A1 (en) | 2013-07-03 |
CN103174501B (en) | 2017-03-01 |
CN103174501A (en) | 2013-06-26 |
US20130340693A1 (en) | 2013-12-26 |
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