WO2009108094A1 - Scie pour travaux de construction - Google Patents

Scie pour travaux de construction Download PDF

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Publication number
WO2009108094A1
WO2009108094A1 PCT/SE2008/050229 SE2008050229W WO2009108094A1 WO 2009108094 A1 WO2009108094 A1 WO 2009108094A1 SE 2008050229 W SE2008050229 W SE 2008050229W WO 2009108094 A1 WO2009108094 A1 WO 2009108094A1
Authority
WO
WIPO (PCT)
Prior art keywords
saw
gear
rpm
motor
saw blade
Prior art date
Application number
PCT/SE2008/050229
Other languages
English (en)
Inventor
Andreas JÖNSSON
Original Assignee
Husqvarna Ab
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Husqvarna Ab filed Critical Husqvarna Ab
Priority to PCT/SE2008/050229 priority Critical patent/WO2009108094A1/fr
Publication of WO2009108094A1 publication Critical patent/WO2009108094A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D47/00—Sawing machines or sawing devices working with circular saw blades, characterised only by constructional features of particular parts
    • B23D47/12—Sawing machines or sawing devices working with circular saw blades, characterised only by constructional features of particular parts of drives for circular saw blades
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28D—WORKING STONE OR STONE-LIKE MATERIALS
    • B28D1/00—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor
    • B28D1/02—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor by sawing
    • B28D1/04—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor by sawing with circular or cylindrical saw-blades or saw-discs
    • B28D1/044—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor by sawing with circular or cylindrical saw-blades or saw-discs the saw blade being movable on slide ways
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B28—WORKING CEMENT, CLAY, OR STONE
    • B28D—WORKING STONE OR STONE-LIKE MATERIALS
    • B28D1/00—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor
    • B28D1/02—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor by sawing
    • B28D1/04—Working stone or stone-like materials, e.g. brick, concrete or glass, not provided for elsewhere; Machines, devices, tools therefor by sawing with circular or cylindrical saw-blades or saw-discs
    • B28D1/045—Sawing grooves in walls; sawing stones from rocks; sawing machines movable on the stones to be cut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • F16D7/024—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces
    • F16D7/025—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs

Definitions

  • the present invention relates to a saw being portable and/or wheeled, such as a wall saw, floor saw or masonry saw comprising a rotatable circular saw blade, a drive motor with an output shaft for rotating the saw blade, and a transmission for interconnecting the output shaft to the rotatable saw blade in order to change an unsuitable high speed and low torque combination of the output shaft into a more useable lower speed and higher torque combination at the rotatable tool.
  • Construction machinery is used in renovating, reconstructing and extending buildings, for example.
  • Wall saws are used for cutting and extending openings for doors, windows and light wells, etc., corrective work on facades, partition walls and garden walls, etc., and controlled demolition of concrete.
  • Floor saws are wheeled and normally used for cutting in concrete floors.
  • Wall saws, floor saws masonry saws and similar construction machinery have a drive motor, usually electric, and a rotary tool driven by the motor.
  • the tool is a circular saw blade equipped with cutting diamond segments.
  • heavy duty wall saws are driven hydraulically, see US 6,955,167 B2, US 2006/0201492 Al, US 2007/0163412 Al, and US 5,887,579, for example.
  • hydraulic wall saws are comparatively heavy and not easy to set up, and comparatively low-weight electric wall saws, such as the one disclosed in US 2006/0189258 Al, for example, have been introduced on the market.
  • Such an electric wall saw is usually driven by an induction motor running at a specifically set rpm for maximum power output.
  • the speed for maximum power output is usually in the order of magnitude between 15000 rpm and 30000 rpm requiring a planetary gear set or the like for reducing the speed to a suitable rpm for the saw blade.
  • Planetary gears are costly and would usually require an oilpump for sufficient supply of lubrication or splash lubrication. Further, it is usually desirable to run the wall saw so that the cutting segments get an optimal peripheral speed.
  • a wall saw usually includes a rack, i.e. a toothed bar or rod, intended to be attached to and equidistantly spaced from the wall or floor, which is to be sawed through.
  • a carriage carries a drive motor for the circular saw blade and is movable along the rack by means of another motor.
  • the wall saw can be remotely controlled for safety and comfort of the operator.
  • the saw blade is mounted at the free end of a pivotal arm attached to the carriage and housing a transmission for transferring the rotation of the drive motor shaft to the saw blade.
  • the pivotal arm, or transmission housing is swung towards or away from the wall by a third motor.
  • the transmission usually includes a first gear mounted on the output shaft of the drive motor, and a second gear having an output shaft, on which the saw blade is intended to be mounted.
  • the second gear may be drivingly connected to the first gear by a chain or, preferably, by one or more interposed gears.
  • the wall saw and especially the teeth of its gears will be exposed to large exterior forces, and the teeth and gears have to be dimensioned to stand such forces.
  • the teeth and gears usually are greatly oversized.
  • An object of the present invention is to provide a saw, in which the forces that may act on the teeth and gears of its transmission are limited and known, so that the latter do not have to be greatly oversized. Thereby also the loads the rotating parts of the motor will be reduced.
  • the transmission of the saw comprises an adjustable friction saw protective clutch.
  • An adjustable friction clutch protects the wall saw or other construction machine against large exterior forces, and by setting the adjustable friction clutch at a desired predetermined value, a possibility to limit the maximum size of the forces that the teeth, gears and bearings are exposed to is provided. Thereby, the transmission may be made more compact and less heavy. The need for over dimensioning is hereby reduced. Advantageously, no over dimensioning is necessary, and the transmission will make out fine in rough environments.
  • the transmission comprises two adjustable friction clutches in parallel.
  • a transmission having two friction clutches will have a larger tooth engagement than a transmission having only a single friction safety clutch, and the transmission assembly can be made more compact.
  • the transmission preferably is mounted in an arm-shaped housing, which can be turned on a pivotal axis that is coaxial with a rotation axis of the output shaft of the motor.
  • the transmission has a first gear arranged on the output shaft, two gear assemblies mounted to be driven in parallel by the first gear, and a common second gear arranged to be driven by the two gear assemblies in parallel.
  • the second gear has an output shaft, on which the saw blade is intended to be mounted, and each gear assembly includes one of said adjustable friction safety clutches.
  • gear transmissions are more reliable than chain transmissions.
  • each gear assembly comprises a fourth gear integral with a coaxial shaft, a fifth gear mounted to be able to rotate on the coaxial shaft, a friction clutch disk clamped axially between the fourth gear and the fifth gear, and a mechanism for pressing the fifth gear with an adjustable pressure against the friction clutch disk to permit transfer of torque from the fifth gear to the fourth gear.
  • a gear assembly with said adjustable friction safety clutch is compact, rugged and can easily be made to stand heavy loads.
  • a clutch transfer plate is fixed on the coaxial shaft between the fourth gear and the friction clutch disk.
  • the friction clutch disk does not have to engage an axial end face of the fourth gear.
  • the coaxial shaft suitably has a free end extending axially from the fifth gear, the free end having a thread, a nut engaging the thread, and a Belleville washer clamped between the nut and the fifth gear, whereby the degree of tightening of the nut determines at what torque the saw blade will stop rotating.
  • the fifth gear meshes with the first gear
  • the fourth gear meshes with the gear driven by the two gear assemblies.
  • the transmission will be compact, rugged and can easily be made to stand heavy loads.
  • the first and fifth gears may be selected to give a speed reduction ration in the order of 3:2, and the fourth gear and the gear driven thereby may be selected to give a speed reduction ratio on the order of 5:1. This results in a preferred over all speed reduction ratio in the order of 7.5: 1 from the drive motor to the rotatable tool.
  • the second and the third gears suitably are of substantially the same size, i.e. a gear ratio in the order of 1:1. Thereby, it will be easy to enclose the transmission in an arm-shaped housing.
  • the drive motor is a permanent magnet motor.
  • a permanent magnet motor has an advantageously high torque performance as compared to an induction motor of the same weight and size.
  • the permanent magnet motor can be arranged to perform a power output close to its maximum power output at substantially all rpm's within an rpm interval of at least 1000 rpm.
  • the permanent magnet motor is arranged to perform a power output close to its maximum power output at substantially all rpm's within an rpm interval of at least 3000 rpm.
  • the motor is arranged to perform a power output close to its maximum power output at substantially all rpm's between 6000 - 9000 rpm.
  • This can be achieved by field weakening by tapping which is a technology known as such for permanent magnet motors and is not described in more detail in this context.
  • the field weakening by tapping results in several advantages.
  • the permanent magnet motor can for example be arranged to provide the functionality of a gear box for obtaining optimal saw blade peripheral speed independently of saw blade diameter. In this way the problem of keeping the peripheral speed of the saw blade constant, independently of saw blade diameter is solved and the need for a separate gear box is removed.
  • Another aspect of the invention is directed to a wall saw having a rotatable circular saw blade, a drive motor with an output shaft for rotating the saw blade, and a transmission for interconnecting the output shaft to the rotatable saw blade in order to transform an unsuitable high speed and low torque of the output shaft to a more useable lower speed with higher torque at the rotatable tool
  • the drive motor is an electric motor having an available power output close to maximum power output at substantially all rpm's within an rpm interval of at least 1000 rpm, and wherein said drive motor at rpm's within said interval thereby also is adjustable to an rpm that via said transmission transfers to an optimal rpm and/or optimal peripheral speed of the saw blade.
  • This aspect of the invention is also directed to a saw as defined in dependent claims 21- 26.
  • the permanent magnet motor for this application might preferebly be a servo motor, e.g. of the type used in industrial robots.
  • a permanent magnet motor for a wall saw typically has a power output of about 11 kW at 6000 rpm increasing only slightly to a power output of about 13 kW at 9000 rpm.
  • the motor also provides the functionality of a gear box in the meaning that in order to adjust saw blade rpm it is possible to adjust the motor rpm, still maintaining a high power output close the the maximum power output. In this way the problem of keeping the peripheral speed of cutting segments of the saw blade constant, independently of saw blade diameter is solved and the need for a separate gear box is removed.
  • field weakening by tapping resolves the problem by limiting output torque at high rpm and limiting average current in motor windings at high rpm, and maintaining a generally constant power output over a wide rpm range (6000- 9000 rpm).
  • This solution also provides a possibility to use a relatively light weight and low cost permanent magnet motor with great flexibility in a wall saw.
  • a typical wall saw as discussed above can therefore have a total weight of only 25 kg, to compare with approximately 40 kg for a corresponding conventional wall saw. This is important as the saw is carried to the work site and mounted there. Further the more compact transmission makes it possible to cut closer to the rack, closer than 190 mm, preferably closer than 170 mm, to compare with 205 mm for a corresponding conventional wall saw. This is a distinct advantage.
  • Fig. 1 is a perspective view of a wall saw movable along a toothed rack and having a circular saw blade driven by a motor via a transmission according to preferred embodiment of the present invention.
  • Fig. 2 is a perspective view of a housing of the transmission shown in Fig. 1.
  • Fig. 3 is a plan view of the gears and the two friction safety clutches of the transmission inside the housing.
  • Fig. 4 is a side view of a friction safety clutch shown in Fig. 3.
  • Fig. 5 is a longitudinal cross sectional view of the friction safety clutch of Fig. 4.
  • the present invention relates to a construction machine having a drive motor, a rotatable tool driven by the prime mover, and a transmission for interconnecting an output shaft of the prime mover to the rotatable tool in order to transform an unsuitable high speed and low torque of the prime mover output shaft to a more useable lower speed with higher torque at the rotatable tool.
  • An exemplary embodiment of such a construction machine is a wall saw having a motor, a circular saw blade driven by the motor, and a transmission for interconnecting an output shaft of the motor to the rotatable saw blade.
  • a wall saw might as well be used for sawing through a floor or a ceiling.
  • Fig. 1 is a perspective view of a wall saw assembly, which is positioned to saw through a floor.
  • the wall saw assembly includes a wall saw 1 that is movable along a toothed rack 2 and has a circular saw blade 3 inside a protective hood 4, and, therefore, shown in a dashed line, and driven by a motor 5 via a transmission 20 according to preferred embodiment of the present invention.
  • the wall saw has two additional motors, not shown, one for moving the wall saw 1 along the toothed rack 2, which is intended to be mounted on the "wall" where an opening is to be sawed, and the other motor for raising and lowering the saw blade 3.
  • a cable 6 is connected to the motor 5 for supplying power to the motors and for transferring control data between a control unit, not shown, and the motors. Cooling water is fed to the motor 5 through a first hose 7, and through a second hose 8 it is passed on to a central area of the saw blade 3 to cool the saw blade and bind dust formed on
  • the transmission 20 includes an arm-shaped housing 21, which is best shown in Fig. 2 and has two ends. The first end is connected to an output shaft 9 of the motor 5, and the other end is connected to a shaft 25, on which the saw blade 3 is to be mounted. On raising and lowering the saw blade 3, the transmission housing 21 will be turned on a pivotal axis that is coaxial with a rotation axis of the output shaft 9 of the motor 5, and said other end of the housing, which carries the saw blade 3, will move in an arc. To permit the arcuate movement of the saw blade 3 inside the protective hood 4, the wall saw is provided with a guide arrangement 10 permitting the hood 4 a limited horizontal movement relative to the motor 5 (as seen in Fig.
  • the hood 4 also has a vertical slot 11 that permits the shaft for the saw blade 3 to move vertically.
  • the permitted movement of the hood 4 relative to the motor 5 is of course vertical instead of horizontal in this embodiment of the invention.
  • the transmission comprises an adjustable friction safety clutch 30-33 (see Fig. 5).
  • an adjustable friction safety clutch protects the wall saw or other construction machine against large exterior forces, and by setting the adjustable friction clutch 30-33 at a desired predetermined value, you will limit the maximum size of the forces that the teeth and gears are exposed to.
  • the transmission 20 may be made more compact and less heavy. No over dimensioning is necessary, and the transmission 20 will make out fine in rough environments.
  • a preferred embodiment of the actual transmission inside the transmission housing 21 is shown in Fig. 3.
  • a first gear 22 is mounted on the motor output shaft 9, which is shown as having a male spline for transferring large forces to the first gear 22 that has a matching female spline.
  • Two gear assemblies 23 are mounted to be driven in parallel by the first gear
  • Each gear assembly 23 includes one of said adjustable friction safety clutches. This design contributes to a compact structure of the transmission 20. Although a drive chain might be used for transferring the rotary force to the second gear 24, it is recommended that a third gear 26 is mounted interposed between the gear assemblies 23 and the second gear 24 to be driven by the gear assemblies 23 and drive the second gear 24. Gear transmissions are more reliable than chain transmissions.
  • each gear assembly 23 comprises a fourth gear 27 integral with a coaxial shaft 28, a fifth gear 29 mounted to be able to rotate on the coaxial shaft 28, a friction clutch disk 30 clamped axially between the fourth gear 27 and the fifth gear 29, and a mechanism 31-33 for pressing the fifth gear 29 with an adjustable pressure against the friction clutch disk 30 to permit transfer of torque from the fifth gear 29 to the fourth gear 27.
  • Such a gear assembly with said adjustable friction safety clutch is compact, rugged and can easily be made to stand heavy loads.
  • the coaxial shaft 28 suitably has a free end extending axially from the fifth gear 29, the free end having a thread 31, a nut 32 engaging the thread 31, and a Belleville washer 33 clamped between the nut 32 and the fifth gear 29, whereby the degree of tightening of the nut 32 determines at what torque the saw blade 3 will stop rotating.
  • a clutch transfer plate 34 is fixed on the coaxial shaft 28 between the fourth gear 27 and the friction clutch disk 30. Thereby the friction clutch disk 30 does not have to engage an axial end face of the fourth gear 27. The clutch transfer plate 34 is locked against rotation on the coaxial shaft 28 in any suitable way.
  • the locking is accomplished by three equiangularly spaced balls 35, one of which is shown.
  • Each ball 35 is located halfway into an individual recess in the coaxial shaft 28 and halfway into a corresponding individual recess in the clutch transfer plate 34.
  • the fifth gear 29 preferably meshes with the first gear 22, and the fourth gear 27 meshes with the gear driven by the two gear assemblies 23, in the shown embodiment the third gear 26 that in its turn meshes with the second gear 24.
  • the gear assemblies 23 might as well be of a design where the first gear 22 meshes with the gear that is rotatable on the coaxial shaft 28, and the gear that is integral with the coaxial shaft 28 meshes with the third gear 26.
  • all rotatable components of the transmission are, of course, mounted in suitable bearings, well known to a person skilled in the art and not shown.
  • the first and fifth gears, 22 and 29, respectively may be selected to give a speed reduction ratio on the order of 3:2, and the fourth gear 27 and the gear driven thereby, in the shown embodiment the third gear 26, may be selected to give a speed reduction ratio on the order of 5:1.
  • the second and the third gears, 24 and 26, respectively suitably are of substantially the same size. Thereby, it will be easy to enclose the transmission in an arm-shaped housing 21.
  • Motor 5 is a permanent magnet motor with a maximum power output of about 13 kW. 13 kW power is obtain at about 9000 rpm. The power output is kept close to maximum all the way down to 6000 rpm where the power output is about 11 kW. This is achieved by means of applying field weakening by tapping at high rpm's and thereby also reducing average current in the motor windings to prevent over heating or burning. While in this embodiment the available power output is maintained close to maximum power output in an rpm interval of 3000 rpm (between 6000-9000 rpm) it might also be suitable to provide a wall saw 1 with a motor 5 performing an available power output close to maximum power output over a wider or a narrower rpm interval, i.e.
  • a permanent magnet motor with the performance described above typically has a weight of just about 8 kg.
  • the permanent magnet motor as described in preceeding paragraph above can be provided in wall saws comprising other kinds of transmissions than those described previously.
  • the parallel friction safety clutch may be omitted or replaced by any other overload protection already known in the art.
  • such a wall saw comprises a rotatable circular saw blade 3, a drive motor 5 with an output shaft 9 for rotating the saw blade 3, and a transmission 20 for interconnecting the output shaft 9 to the rotatable saw blade 3 in order to transform an unsuitable high speed and low torque of the output shaft 9 to a more useable lower speed with higher torque at the rotatable tool 3, wherein the drive motor 5 is an electric motor having an available power output close to its maximum power output at substantially all rpm's within an rpm interval of at least 1000 rpm, and wherein said drive motor 5 at rpm's within said interval thereby also is adjustable to an rpm that via said transmission 20 transfers to an optimal rpm of the saw blade 3.
  • the application of a permanent magnet motor has several further advantages.
  • the rotor temperature reaches very high levels. High temperature and high rpm can cause problems in bearings and shaft seals which can be subject to excessive wear etc.
  • Another important advantage of the permanent magnet motor is that it normally works with a higher torque at a relatively lower rpm than an induction motor. This reduces the speed reduction demands on the transmission.
  • the transmission of the present invention is especially applicable in wall saws and similar construction machines, where a transmission that may be made more compact and less heavy than prior art transmissions is desired.
  • An adjustable friction safety clutch or preferably two adjustable friction safety clutches in parallel, can be set at a desired predetermined value, so as to limit the maximum size of the forces that the teeth and gears of the transmission are exposed to. Thereby, the transmission may be made more compact and less heavy. No over dimensioning is necessary, and the transmission will make out fine in rough environments.
  • Providing a wall saw with a permanent magnet motor according to present invention as the drive motor for driving the saw blade via said transmission is especially applicable for reducing weight of the motor and for gaining a generally constant power output of the motor over a wide rpm-range.
  • the permanent magnet motor can aslo provide the functionality of a gear box.
  • the transmission ratio from the motor output to the saw blade is therefore fixed, i.e. fixed for a certain wall saw, but might of course be different for a different wall saw without departing from the scope of present invention.
  • the adjustment of saw blade rpm depending on saw blade diameter is performed by adjustment of the motor rpm, which can be made continuously if wanted.
  • the overall drive train can be made more compact and less heavy and more cost efficent to manufacture and maintain.
  • a separate gear box with different gears for different saw blade diameters is for example not needed in the solution according to present invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • General Engineering & Computer Science (AREA)
  • Sawing (AREA)

Abstract

L'invention concerne une scie (1) portable et/ou sur roues, telle une scie murale, une scie au sol ou une scie de maçonnerie, comportant une lame de scie circulaire rotative (3), un moteur d'entraînement (5) équipé d'un arbre de sortie (9) à des fins de rotation de la lame de scie (3), et une transmission (20) destinée à raccorder l'arbre de sortie (9) à la lame de scie rotative (3) afin de changer une combinaison inadéquate grande vitesse et faible couple de l'arbre de sortie (9) en une combinaison plus utile vitesse plus faible et couple plus élevé au niveau de l'outil rotatif (3), la transmission (20) comportant au moins un embrayage de protection ajustable de scie à friction (30-33), ou de préférence deux embrayages de sécurité ajustables à friction (30-33) en parallèle, qui peuvent être réglés selon une valeur prédéterminée souhaitée, de manière à limiter la valeur maximale des forces auxquelles les dents et les engrenages de la transmission (20) sont exposés. Aucun surdimensionnement n'est nécessaire, et la transmission (20) fonctionnera bien dans des environnements rudes.
PCT/SE2008/050229 2008-02-29 2008-02-29 Scie pour travaux de construction WO2009108094A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/SE2008/050229 WO2009108094A1 (fr) 2008-02-29 2008-02-29 Scie pour travaux de construction

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Application Number Priority Date Filing Date Title
PCT/SE2008/050229 WO2009108094A1 (fr) 2008-02-29 2008-02-29 Scie pour travaux de construction

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WO2009108094A1 true WO2009108094A1 (fr) 2009-09-03

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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011028154A1 (fr) * 2009-09-02 2011-03-10 Husqvarna Ab Scie pour le travail de découpage dans le bâtiment
WO2011067262A1 (fr) * 2009-12-03 2011-06-09 Cembre S.P.A. Appareil pour le travail d'une pièce
WO2012030290A1 (fr) * 2010-09-01 2012-03-08 Husqvarna Ab Protège-lame pour une scie
WO2012105904A1 (fr) * 2011-02-03 2012-08-09 Husqvarna Ab Scie à chaîne murale ou à sol
CN102744788A (zh) * 2012-06-21 2012-10-24 逄书博 一种墙板拉毛找平机
EP2716927A1 (fr) * 2012-10-02 2014-04-09 Fico Mirrors, S.A. Embrayage approprié pour rétroviseurs électriques de véhicule
EP2983877A4 (fr) * 2013-04-12 2016-04-13 Anders Johnsen Scie murale pourvue d'un embrayage de sécurité
CN108436178A (zh) * 2018-06-01 2018-08-24 新沂市阿湖硅产业科技工业园建设发展有限公司 一种安全机器人
CN108436169A (zh) * 2018-06-01 2018-08-24 新沂市阿湖硅产业科技工业园建设发展有限公司 一种智能机器人
CN108480746A (zh) * 2018-06-01 2018-09-04 新沂市阿湖硅产业科技工业园建设发展有限公司 一种高效的机器人
CN108544546A (zh) * 2018-06-01 2018-09-18 泉州市易快充智能设备有限公司 一种安全的板材加工装置
CN112404579A (zh) * 2020-10-26 2021-02-26 湖南省鼎兴建筑建材有限公司 一种门窗制作用切割设备
WO2023188153A1 (fr) * 2022-03-30 2023-10-05 本田技研工業株式会社 Machine de coupe

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JPS5828045A (ja) * 1981-08-10 1983-02-18 Kohan Kogyo Kk トルクリミツタ付遊星歯車減速装置
JPS6235119A (ja) * 1985-08-07 1987-02-16 Nippon Denso Co Ltd トルク調整方法
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US5653218A (en) * 1993-10-29 1997-08-05 Hitachi Koki Co., Ltd. Electric-powered stone cutter
DE19714253A1 (de) * 1997-04-07 1998-10-08 Hensel Eisenwerk Sägegatter zum Zersägen eines Gesteinsblocks zu Platten
US6318353B1 (en) * 2000-02-21 2001-11-20 Diamond Products, Limited Concrete saw with multispeed drive
US20030172917A1 (en) * 2002-03-18 2003-09-18 Anthony Baratta Pavement working apparatus and methods of making
EP1579939A1 (fr) * 2004-03-25 2005-09-28 HILTI Aktiengesellschaft Outil
US20070180709A1 (en) * 2005-06-29 2007-08-09 Gianni Borinato Circular saw with rotatable handle
DE102006018262A1 (de) * 2006-04-20 2007-10-25 Wemhöner Anlagen GmbH & Co. KG Bearbeitungsmotor für Bearbeitungsmaschinen von plattenförmigen Körpern in der Holz- und Baustoffindustrie

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB704748A (en) * 1950-02-06 1954-03-03 Bath & Portland Stone Firms Lt A rotary cutting machine for stone
JPS5828045A (ja) * 1981-08-10 1983-02-18 Kohan Kogyo Kk トルクリミツタ付遊星歯車減速装置
JPS6235119A (ja) * 1985-08-07 1987-02-16 Nippon Denso Co Ltd トルク調整方法
US5653218A (en) * 1993-10-29 1997-08-05 Hitachi Koki Co., Ltd. Electric-powered stone cutter
EP0785054A1 (fr) * 1996-01-17 1997-07-23 HILTI Aktiengesellschaft Machine à scier des parois et lame de scie
DE19714253A1 (de) * 1997-04-07 1998-10-08 Hensel Eisenwerk Sägegatter zum Zersägen eines Gesteinsblocks zu Platten
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US8998684B2 (en) 2009-12-03 2015-04-07 Cembre S.P.A. Apparatus for the tooling of a workpiece
WO2011067262A1 (fr) * 2009-12-03 2011-06-09 Cembre S.P.A. Appareil pour le travail d'une pièce
US9168596B2 (en) 2010-09-01 2015-10-27 Husqvarna Ab Blade guard for a saw
EP2611584A4 (fr) * 2010-09-01 2017-10-04 Husqvarna AB Protège-lame pour une scie
CN103097093A (zh) * 2010-09-01 2013-05-08 胡斯华纳有限公司 用于锯的锯片防护装置
WO2012030290A1 (fr) * 2010-09-01 2012-03-08 Husqvarna Ab Protège-lame pour une scie
CN103338907A (zh) * 2011-02-03 2013-10-02 胡斯华纳有限公司 墙或地板链锯
AU2012212689B2 (en) * 2011-02-03 2014-11-06 Husqvarna Ab Wall or floor chainsaw
US8955505B2 (en) 2011-02-03 2015-02-17 Husqvarna Ab Wall or floor chainsaw
WO2012105904A1 (fr) * 2011-02-03 2012-08-09 Husqvarna Ab Scie à chaîne murale ou à sol
WO2012105876A1 (fr) * 2011-02-03 2012-08-09 Husqvarna Ab Scie à murs ou planchers
US9539740B2 (en) 2011-02-03 2017-01-10 Husqvarna Ab Wall or floor chainsaw
CN102744788A (zh) * 2012-06-21 2012-10-24 逄书博 一种墙板拉毛找平机
EP2716927A1 (fr) * 2012-10-02 2014-04-09 Fico Mirrors, S.A. Embrayage approprié pour rétroviseurs électriques de véhicule
US9200680B2 (en) 2012-10-02 2015-12-01 Fico Mirrors, S.A. Clutch suitable for vehicles' powered mirrors
EP2983877A4 (fr) * 2013-04-12 2016-04-13 Anders Johnsen Scie murale pourvue d'un embrayage de sécurité
US9623587B2 (en) 2013-04-12 2017-04-18 Tractive Ab Wall saw with safety clutch
CN108436178A (zh) * 2018-06-01 2018-08-24 新沂市阿湖硅产业科技工业园建设发展有限公司 一种安全机器人
CN108436169A (zh) * 2018-06-01 2018-08-24 新沂市阿湖硅产业科技工业园建设发展有限公司 一种智能机器人
CN108480746A (zh) * 2018-06-01 2018-09-04 新沂市阿湖硅产业科技工业园建设发展有限公司 一种高效的机器人
CN108544546A (zh) * 2018-06-01 2018-09-18 泉州市易快充智能设备有限公司 一种安全的板材加工装置
CN112404579A (zh) * 2020-10-26 2021-02-26 湖南省鼎兴建筑建材有限公司 一种门窗制作用切割设备
WO2023188153A1 (fr) * 2022-03-30 2023-10-05 本田技研工業株式会社 Machine de coupe

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