EP2523780B1 - Marteau perforateur et/ou percuteur avec refroidissement des composants de l'appareil - Google Patents

Marteau perforateur et/ou percuteur avec refroidissement des composants de l'appareil Download PDF

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Publication number
EP2523780B1
EP2523780B1 EP11700320.2A EP11700320A EP2523780B1 EP 2523780 B1 EP2523780 B1 EP 2523780B1 EP 11700320 A EP11700320 A EP 11700320A EP 2523780 B1 EP2523780 B1 EP 2523780B1
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EP
European Patent Office
Prior art keywords
cooling air
air flow
duct
hammer
cooling
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
Application number
EP11700320.2A
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German (de)
English (en)
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EP2523780A1 (fr
Inventor
Michael Fischer
Otto W. Stenzel
Wolfgang Hausler
Rudolf Berger
Christian Littek
Helmut Braun
Manfred Zinsmeister
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wacker Neuson Produktion GmbH and Co KG
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Wacker Neuson Produktion GmbH and Co KG
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Publication of EP2523780A1 publication Critical patent/EP2523780A1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/20—Devices for cleaning or cooling tool or work
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/06—Means for driving the impulse member
    • B25D9/10—Means for driving the impulse member comprising a built-in internal-combustion engine
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0057—Details related to cleaning or cooling the tool or workpiece
    • B25D2217/0061—Details related to cleaning or cooling the tool or workpiece related to cooling

Definitions

  • the invention relates to a hammer drill and / or impact hammer with an internal combustion engine.
  • hammers - Hammer drills and / or percussion hammers with internal combustion engines - hereinafter also referred to briefly as hammers - are known in particular as relatively heavy breakers with which work is carried out essentially vertically downwards.
  • a cooling air blower driven via the crankshaft of the internal combustion engine is provided for cooling the engine.
  • the cooling air fan generates a cooling air flow which is guided along the outside of the cylinder of the internal combustion engine, in particular along the cooling fins provided on the outside of the cylinder.
  • the engine cooling exhaust air discharged from the engine is usually very hot and must therefore be led away from the hammer in the shortest possible way.
  • the striking mechanism which is provided for generating the working movement of the hammer and is driven by the internal combustion engine, can also heat up considerably, in particular if it is an air spring hammer mechanism, due to the air compression. To cool the striking mechanism, it is therefore known to provide an additional fan wheel, which generates a separate cooling air flow for the striking mechanism. Corresponding installation space must be provided for this additional fan wheel and design effort must be carried out.
  • a rock drilling machine in which a cooling air flow is generated by a cooling air blower.
  • the cooling air flow is guided over ribs on the outer wall of an engine cylinder and subsequently emerges on the underside of the hood forming the cooling air channel.
  • a hammer with a cooling air blower which generates a cooling air flow.
  • the cooling air flow is led through a cladding to the outer wall of the cylinder of an internal combustion engine, the cross section of the cooling air channel tapering in the direction of flow.
  • the invention has for its object to provide a hammer drill and / or percussion hammer, in which an improved cooling of the components is possible.
  • the object is achieved by a hammer drill and / or percussion hammer according to claim 1.
  • a hammer drill and / or percussion hammer has an internal combustion engine with a cylinder and a piston movable in the cylinder, a cooling air blower for generating a cooling air flow and a cooling air duct for guiding the cooling air flow from the cooling air blower to an outer wall of the cylinder.
  • the cooling air duct Downstream from the outer wall of the cylinder, the cooling air duct has a duct region in which a plurality of partial cooling air flows are branched off from the cooling air flow (main cooling air flow).
  • the channel area is designed such that the cross section of the channel area related to a flow direction of the cooling air flow tapers to the extent that partial cooling air flows are branched off from the cooling air flow, so that the flow rate of the cooling air flow in the channel area remains essentially constant.
  • the cooling air duct is to define the entire length of the cooling air flow from the cooling air blower to the outlet from the hammer, the duct region only indicates a partial region of the cooling air duct.
  • the channel area is of particular importance for the following consideration.
  • the cooling air duct in the area in which the cylinder or the outer wall of the cylinder is to be cooled is thus designed in such a way that the flow rate of the cooling air flow (main cooling air flow) remains constant even when partial cooling air flows have already been branched off.
  • the cross section of the duct area is kept essentially constant, so that the flow rate of the cooling air is gradually reduced when partial cooling air flows are branched off.
  • the engine cooling air can be blown through the engine with a comparatively lower flow resistance. This increases the volume flow and thus reduces the temperature of the cooling air.
  • the engine only emits the amount of heat it needs to the cooling air, which also means that the cooling air does not heat up as much.
  • the prior art usually strives for a cooling air distribution in which as much heat as possible is extracted from the engine, but this is often not necessary.
  • a plurality of cooling fins running parallel to one another can be formed on the outer wall of the cylinder, a partial channel being formed in each case between two mutually adjacent cooling fins for guiding a partial cooling air flow, the partial cooling air flow being branched off from the cooling air flow brought up by the cooling air blower.
  • the cooling fins are provided on the outer wall of the cylinder in a known manner and are usually cast in one piece with the cylinder housing or subsequently attached as cooling elements on the outer wall of the cylinder.
  • One of the subchannels into which a respective partial cooling air flow is introduced is formed between the adjacent cooling fins.
  • the respective partial cooling air flows are gradually branched off from the main cooling air flow when the main cooling air flow passes the cooling fins of the cylinder becomes.
  • the channel area can be guided upstream of the cooling fins past the cooling fins and thus past the subchannels or the initial areas of the subchannels.
  • the duct area can be designed in such a way that the cross section of the duct area tapers in its course along the initial areas of the respective subchannels to the extent that partial cooling air flows are branched off from the cooling air flow, so that the above requirement is met that the flow velocity of the cooling air flow in the channel area remains essentially constant.
  • the flow rates of the partial cooling air flows in the sub-channels can be essentially the same. In particular, they can also be the same as the flow rate of the remaining cooling air flow in the duct area. In this way, an equalization and optimization of the cooling air flow is achieved with the lowest possible flow resistance. An indication of an unnecessary flow resistance would be e.g. a strong change in the flow velocity in the cooling air duct.
  • a cooling air duct for guiding the cooling air flow from the cooling air blower along an outer wall of the cylinder, the cooling air duct having a duct section downstream of the outer wall of the cylinder for guiding the cooling air flow to an exhaust system of the internal combustion engine and / or to the striking mechanism.
  • cooling air which has already warmed up as it flows past the cylinder, can continue to be used to cool other hot components whose temperature during operation is above the temperature that the Has cooling air flow downstream of the cylinder.
  • These components include in particular the exhaust system of the internal combustion engine or the striking mechanism.
  • the engine cooling exhaust air is thus used to further components of the hammer, namely in particular the exhaust system, for. B. the silencer, and to cool the hammer mechanism.
  • the exhaust system and the striking mechanism in particular are subject to high thermal loads during operation of the hammer.
  • their waste heat can be problematic for the components themselves.
  • the waste heat can also lead to excessive heating of other components of the hammer, e.g. B. lead the carburetor or the tank system, which can impair reliable operation.
  • cooling air engine cooling exhaust air coming from the engine, that is to say from the outer wall of the cylinder, is still relatively cool and can therefore be used to cool the other components.
  • this engine cooling exhaust air flow divided downstream of the outer wall of the cylinder and supplied in the form of two separate cooling air flows to the exhaust system and the hammer mechanism.
  • the cooling air duct By cleverly designing the cooling air duct, it is thus possible to conduct a cooling air flow suitable for the respective device.
  • the cooling air flow either only to the exhaust system or only to the striking mechanism or to both assemblies.
  • the cooling air flow can also be directed first to the exhaust system and then to the striking mechanism.
  • the cooling air flow can also be divided into two parallel cooling air flows, which flow parallel to the exhaust system and the striking mechanism.
  • cooling air flow downstream of the outer wall of the cylinder is divided into two cooling air flows, one cooling air flow being led directly to the exhaust system and a second cooling air flow first to the striking mechanism and only then to the exhaust system.
  • the exact design of the cooling air duct and thus the routing of the cooling air flow depends on the temperature distributions in the hammer and on the desired cooling effect.
  • the cooling air duct has a first duct section downstream of the outer wall of the cylinder, for guiding the cooling air flow to the striking mechanism. Downstream of the striking mechanism, the cooling air duct has a second duct section for guiding the cooling air flow to the exhaust system. In this way, the cooling air flow is first routed to the striking mechanism and then to the exhaust system.
  • the cooling air duct is divided downstream from the outer wall of the cylinder into a first cooling air duct for a first cooling air flow and into a second cooling air duct for a second cooling air flow.
  • the first cooling air duct serves to guide the first cooling air flow to an exhaust system of the internal combustion engine, while the second cooling air duct serves to guide the second cooling air flow to the striking mechanism.
  • the hammer mechanism can be an air spring hammer mechanism and a guide housing and one of the internal combustion engine in the guide housing z.
  • the first duct section can also be designed accordingly in order to guide the cooling air flow to the outside of the guide housing.
  • the heat in the striking mechanism arises especially in the vicinity of the air compression area inside the striking mechanism if the striking mechanism is an air spring hammer mechanism known per se. This heat is emitted to the outside via the guide housing and can be dissipated by the cooling air flow. Since the temperature generated in the hammer mechanism is higher than the temperature of the engine cooling exhaust air, the engine cooling exhaust air can still be used effectively to cool the hammer mechanism.
  • the second cooling air duct can be designed such that the second cooling air flow can also be conducted downstream of the impact mechanism to the exhaust system of the internal combustion engine. It has been found that the cooling air, even if it has already cooled the engine (cylinder) and the hammer mechanism, is still at a temperature which is lower than the exhaust system of the internal combustion engine, in particular lower than the temperature of the muffler belonging to the exhaust system . For this reason, it may be advantageous to use the cooling air after cooling the striking mechanism to support the cooling of the muffler in order to improve the cooling effect.
  • the variants described above can be combined with one another as desired. It is thus possible to independently implement the division of the cooling air flow into a first cooling air flow and a second cooling air flow downstream from the outer wall of the cylinder. It is also possible to design the cooling air duct in the duct region located upstream from the outer wall of the cylinder in the manner described, so that the flow rate of the cooling air flow in this duct region remains essentially constant. However, the two variants can also be combined with one another in order to achieve particularly effective cooling.
  • FIGS. 1 to 4 show in different representations a schematic example of a hammer drill and / or percussion hammer according to the invention.
  • the hammer has an internal combustion engine 1 which drives a striking mechanism 5 via a first crank mechanism 2, a transmission 3 and a second crank mechanism 4.
  • the striking mechanism 5 in turn acts on a tool 6, in the present example a chisel.
  • the construction of such a hammer is widely known and therefore does not need to be explained in detail.
  • the internal combustion engine 1 has a cylinder 7, inside which a piston 8 is movably guided.
  • the piston 8 drives the first crank mechanism 2 via a connecting rod 9.
  • the transmission 3 and thus the second crank mechanism 4 are moved via a crankshaft 10 of the crank mechanism 2.
  • the striking mechanism 5 is designed as an air spring hammer mechanism and has a connecting rod 11 moved by the second crank mechanism 4, which moves a drive piston 12 back and forth in a guide housing 13 belonging to the striking mechanism.
  • a percussion piston 14 In the interior of the drive piston 12, a percussion piston 14 is guided, which is moved towards the end of the tool 6 and is returned via an air spring 15 formed between the drive piston 12 and the percussion piston 14.
  • the function of such a striking mechanism 5 is also known and does not need to be discussed in greater detail at this point.
  • a cooling air blower 16 with a fan wheel 17, a blower housing 18 and a cooling air inlet 19 is arranged.
  • the fan wheel 17 is driven in rotation by the crankshaft 10 and thereby sucks ambient air via the cooling air inlet 19.
  • the cooling air is then led via a cooling air duct 20 to the components of the hammer to be cooled.
  • the cooling air duct 20 leads the cooling air to an outer wall of the cylinder 7, on which numerous cooling fins 21 are arranged in a known manner.
  • the cooling air duct 20 leads the cooling air to an outer wall of the cylinder 7, on which numerous cooling fins 21 are arranged in a known manner.
  • FIG 3 For reasons of clarity, only two of the cooling fins 21 are identified by the reference number 21.
  • the outer wall of the cylinder 7 has a plurality of cooling fins 21, as well as directly Figure 3 seen.
  • respective sub-channels 22 are formed, in which the air flow from the cooling air channel 20 can be guided past the outer wall of the cylinder 7.
  • Each of these sub-channels 22 thus branches off a partial cooling air flow from the main cooling air flow in the channel region of the cooling air channel 20 located upstream from the cylinder 7.
  • the cooling air flow in the cooling air duct 20 flows from above, ie coming from the cooling air blower 16 in the downward direction, partial cooling air flows being branched off gradually via respective sub-ducts 22 in the duct region mentioned and being guided past the outer wall of the cylinder 7.
  • the cooling air duct 20 tapers to the extent that cooling air is branched off from it into the respective sub-duct 22.
  • the cross section of the cooling air duct 20 is to be reduced in such a way that the flow rate of the cooling air flow in the cooling air duct 20 provided upstream from the cylinder 7 remains constant. In Figure 3 this taper is recognizable by an obliquely extending channel cover 23.
  • the cross-sectional tapering of the cooling air duct in Figure 4 can be seen where the channel cover 23 begins at a channel inlet 24 - based on an operating position of the hammer with the working direction directed vertically downward - both in the vertical direction downward and in the horizontal direction, away from the channel inlet 24 and thus runs obliquely Cooling air duct 20 tapers.
  • the channel inlet 24 is in Figure 4 only shown in broken lines, since it is of course not visible from the outside under the channel cover 23.
  • the cooling air flow thus effected in the cooling air duct 20 and in the various sub-ducts 22 largely has a constant, identical speed, which is positive for an optimized engine cooling.
  • the cooling air can be released to the environment downstream of the internal combustion engine 1, that is to say downstream of the outer wall of the cylinder 7.
  • the cooling air coming from the engine is still used to cool components which are heated during operation of the hammer.
  • the cooling air duct 20 is divided into a first cooling air duct 26 and a second cooling air duct 27 at an outlet 25, at which the cooling air is guided away from the cooling fins 21 and the outer wall of the cylinder 7.
  • the division takes place with the aid of baffles 28 and 29.
  • the baffles 28, 29 can be suitably shaped in space in order to guide the respective cooling air flows to the areas to be cooled.
  • a first cooling air flow is led into the first cooling air duct 26 and is led to an exhaust system 30 of the internal combustion engine 1, in particular to a silencer.
  • the exhaust system 30 with the muffler becomes particularly hot when the hammer is in operation, so that the cooling air coming from the engine, although already heated, can still contribute to cooling the exhaust system 30. This also ensures in particular that the exhaust system 30 does not in turn other components of the hammer, such as. B. the fuel supply, the tank or the carburetor can heat up in an impermissible manner when the hammer is used for a long time.
  • the second cooling air duct 27 leads the second cooling air flow as cooling air to the striking mechanism 5, in particular to the outer wall of the guide housing 13 of the striking mechanism 5 and there to an area of the striking mechanism 5 in which the air spring 15 is compressed.
  • the compression of the air spring 15 causes a strong heating in the striking mechanism 5. This heat can be dissipated by the second cooling air flow introduced in the second cooling air duct 27.
  • an 80 ° C engine cooling exhaust air can still cool down the 300 ° C hot silencer without any problems.
  • cooling air duct in such a way that the cooling air, after flowing past the cylinder 7, is first led to the outer wall of the guide housing 13 and subsequently along the exhaust system 30.
  • the cooling air can also be directed exclusively to the exhaust system 30.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Exhaust Silencers (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (10)

  1. Marteau perforateur et/ou percuteur, avec
    - un moteur à combustion interne (1), avec un cylindre (7) et avec un piston (8) mobile dans le cylindre (7) ;
    - un mécanisme de percussion (5) entraîné par le moteur à combustion interne (3) ;
    - un ventilateur d'air de refroidissement (16) destiné à la production d'un flux d'air de refroidissement ; et avec
    - un canal d'air de refroidissement (20) destiné à l'acheminement du flux d'air de refroidissement à partir du ventilateur d'air de refroidissement (16) le long d'une paroi extérieure du cylindre (7) ;
    caractérisé en ce que
    - le mécanisme de percussion (5) est entraîné par le moteur à combustion interne par le biais d'une transmission (3) ;
    - le canal d'air de refroidissement (20) comporte en aval de la paroi extérieure du cylindre (7) un premier tronçon de canal pour l'acheminement du flux d'air de refroidissement vers le mécanisme de percussion (5).
  2. Marteau perforateur et/ou percuteur selon la revendication 1, caractérisé en ce que
    - le canal d'air de refroidissement (20) comporte en aval du mécanisme de percussion (5) un deuxième tronçon de canal pour l'acheminement du flux d'air de refroidissement vers un système de gaz d'échappement (30) du moteur à combustion interne (1).
  3. Marteau perforateur et/ou percuteur selon la revendication 1 ou 2, caractérisé en ce que
    - le canal d'air de refroidissement (20) est, en aval de la paroi extérieure du cylindre (7), divisé en un premier canal d'air de refroidissement (26) pour un premier flux d'air de refroidissement et en un deuxième canal d'air de refroidissement (27) pour un deuxième flux d'air de refroidissement ;
    - le premier canal d'air de refroidissement (26) sert à l'acheminement du premier flux d'air de refroidissement vers le système de gaz d'échappement (30) du moteur à combustion interne (1), et en ce que
    - le deuxième canal d'air de refroidissement (27) sert à l'acheminement du deuxième flux d'air de refroidissement vers le mécanisme de percussion (5).
  4. Marteau perforateur et/ou percuteur selon la revendication 3, caractérisé en ce que
    - le mécanisme de percussion (5) comporte un boîtier de guidage (13) et un piston d'entraînement (12) pouvant être déplacé par le moteur à combustion interne (1) dans le boîtier de guidage (13) ; et en ce que
    - le deuxième canal d'air de refroidissement (27) sert à l'acheminement du deuxième flux d'air de refroidissement vers un côté extérieur du boîtier de guidage (13).
  5. Marteau perforateur et/ou percuteur selon la revendication 3 ou 4, caractérisé en ce que le deuxième canal d'air de refroidissement (27) est constitué de telle sorte que le deuxième flux d'air de refroidissement en aval du mécanisme de percussion (5) peut être conduit vers le système de gaz d'échappement (30) du moteur à combustion interne (1).
  6. Marteau perforateur et/ou percuteur selon l'une des revendications 1 à 5, dans lequel
    - en amont de la paroi extérieure du cylindre (7), le canal d'air de refroidissement (20) comporte une zone de canal dans laquelle plusieurs flux d'air de refroidissement partiels peuvent être ramifiés à partir du flux d'air de refroidissement ; et
    - la zone de canal est constituée de telle sorte que la section transversale de la zone de canal, rapportée à une direction d'écoulement du flux d'air de refroidissement, se rétrécit à mesure que les flux d'air de refroidissement partiels sont ramifiés à partir du flux d'air de refroidissement de telle sorte que la vitesse d'écoulement du flux d'air de refroidissement demeure essentiellement constante dans la zone de canal.
  7. Marteau perforateur et/ou percuteur selon la revendication 6, caractérisé en ce que
    - sur la paroi extérieure du cylindre (7), plusieurs ailettes de refroidissement (21) sont constituées parallèlement entre elles ; et en ce que
    - entre deux ailettes de refroidissement (21) respectivement voisines l'une de l'autre, il est constitué respectivement un canal partiel (22) pour l'acheminement d'un flux d'air de refroidissement partiel, le flux d'air de refroidissement partiel étant ramifié à partir du flux d'air de refroidissement apporté par le ventilateur d'air de refroidissement (16).
  8. Marteau perforateur et/ou percuteur selon la revendication 6 ou 7, caractérisé en ce que, en amont des ailettes de refroidissement (21), la zone de canal est guidée devant les ailettes de refroidissement (21) et donc devant les canaux partiels (22) et est constituée de telle sorte que la section transversale de la zone de canal, dans son tracé le long des zones initiales des canaux partiels respectifs, se rétrécit à mesure que des flux d'air de refroidissement partiels sont ramifiés à partir du flux d'air de refroidissement de telle sorte que la vitesse d'écoulement du flux d'air de refroidissement dans la zone de canal demeure essentiellement constante.
  9. Marteau perforateur et/ou percuteur selon l'une des revendications 6 à 8, caractérisé en ce que les vitesses d'écoulement des flux d'air de refroidissement partiels dans les canaux partiels (22) sont essentiellement égales.
  10. Marteau perforateur et/ou percuteur selon l'une des revendications 6 à 9, caractérisé en ce que le ventilateur d'air de refroidissement (16) est entraîné par un vilebrequin (10) du moteur à combustion interne (1).
EP11700320.2A 2010-01-15 2011-01-13 Marteau perforateur et/ou percuteur avec refroidissement des composants de l'appareil Active EP2523780B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010004724A DE102010004724A1 (de) 2010-01-15 2010-01-15 Bohr- und/oder Schlaghammer mit Kühlung von Gerätekomponenten
PCT/EP2011/000134 WO2011085989A1 (fr) 2010-01-15 2011-01-13 Marteau perforateur et/ou percuteur avec refroidissement des composants de l'appareil

Publications (2)

Publication Number Publication Date
EP2523780A1 EP2523780A1 (fr) 2012-11-21
EP2523780B1 true EP2523780B1 (fr) 2020-03-04

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US (1) US9272407B2 (fr)
EP (1) EP2523780B1 (fr)
CN (1) CN102770245B (fr)
DE (1) DE102010004724A1 (fr)
WO (1) WO2011085989A1 (fr)

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GB201413008D0 (en) 2014-07-23 2014-09-03 Black & Decker Inc A range of power tools
CN108166367B (zh) * 2016-05-31 2021-07-09 泉州泉港灿鹏机械设备有限公司 一种破碎锤
US10710923B2 (en) * 2017-10-26 2020-07-14 Wuhan China Star Optoelectronics Semiconductor Display Technology Co., Ltd. Wheel cutter for cutting a flexible glass substrate and cutting method thereof
CN108890374A (zh) * 2018-07-22 2018-11-27 苏州优康通信设备有限公司 一种通信器材的钻孔设备

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WO2011085989A1 (fr) 2011-07-21
EP2523780A1 (fr) 2012-11-21
US9272407B2 (en) 2016-03-01
DE102010004724A1 (de) 2011-07-21
CN102770245A (zh) 2012-11-07
US20130098650A1 (en) 2013-04-25
CN102770245B (zh) 2016-01-20

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