• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    l2 ABSTRACTHigh power flat saw (10) having a large diameter saw blade (12), said flat saw (10) comprising a motor (1 1) and a blade shaft drive (1), wherein said blade shaft drive (1)comprises a first pulley (2) and a second pulley (3) and a belt (6), said second pulley (3)being directly connected to a blade shaft (9), said first pulley (2) having a smallerdiameter than the diameter of said second pulley (3), and wherein said blade shaft drive (1) further comprises a dynamic belt tensioner (4) arranged to apply a dynamic force tothe belt (6). To be published with Fig. 1
    公开号:SE1551579A1
    申请号:SE1551579
    申请日:2015-12-02
    公开日:2017-06-03
    发明作者:Sandwall Johan
    申请人:Husqvarna Ab；
    IPC主号:
    专利说明:

    BLADE SHAFT DRIVE by Johan Sandwall TECHNICAL FIELDThe teachings herein relates to flat saws, and more specifically to a blade shaft drive for a high powered flat saw for large diameter saw blades.
    BACKGROUNDFlat saws are commonly used for cutting concrete and asphalt. Flat saws often use intemal combustion engines or electric motors for supply of power to both the sawblade and for propulsion of the entire flat saw. To transfer the power from the motor tothe blade, belt drive is an often used technique. The blade is a rotating circular blade,and a commonly used rule of thumb for achieving efficient saw performance is that thesaw blade should rotate such that the outer periphery of the blade travels at optimaldesigned speed or not more than approximately 65 m/s. This is a design criteria formany saw blades. As flat saws are designed to operate with a certain saw bladediameter, or at least with a defined range of saw blade diameters, the gear ratio of thebelt drive from the motor to the saw blade is adapted to fulfill the above criteria.However, especially in the field of high powered flat saws with large diameter sawblades, this often means that substantial reduction gearing such as gearboxes orjackshafts is necessary between the output from the motor and the saw blade shaft. Thiscauses unwanted power losses and is further complicated. The cutting depth is limitedby blade shaft pulley size and the pulley size will also be a restriction to get correctblade speed. Another problem which is frequent with the blade drive is belt slippageand/or excessive wear. This is even more common when the belt ages, stretches and/or wear for instance when an internal combustion engine having only one or two cylinders is used as this causes noticeable power pulses from pistons due to engine behavior. Theload which is exerted on the saw blade as it cuts through material also varies, whichfurther contributes to the above mentioned problems. It has thus been a long standingneed for a blade shaft drive for a high powered flat saw which alleviates some or all ofthe above mentioned problems. Related art can be found in for instanceUS20l502l7472Al, US8998684B2, US20l20l80773Al, CN20303l689U,GB2436604A, US9l5l366B2, KR675664Bl, US90973l3B2, KR200803525lA,US20020l l7 l 6lAl, US20l20068525Al, US72226l 8B2, US4664645A, US5429420A.
    SUMMARY It is an object of the teachings herein to provide a high powered flat saw havinga large diameter saw blade comprising a blade shaft drive which is improved over priorart. This object is achieved by a concept having the features set forth in the appendedindependent claims; preferred embodiments thereof being defined in the relateddependent claims.
    According to a first aspect of the teachings herein, a high power flat saw isprovided, having a large diameter saw blade. Said flat saw comprises a motor and ablade shaft drive. The blade shaft drive comprises a first pulley and a second pulley anda belt, the second pulley being directly connected to a blade shaft. The first pulley has asmaller diameter than the diameter of the second pulley, and the blade shaft drivefurther comprises a dynamic belt tensioner arranged to apply a dynamic force on the flatside or on the ribbed side of said belt. The first pulley is directly connected to a powertake out shaft being an extension of the crankshaft/rotor of said motor and said first andsaid second pulleys are directly rotationally connected by the belt, wherein said belt is alow profile belt such as poly V belt, thus providing suitable peripheral speed for saidsaw blade. By providing a blade shaft drive for a flat saw for large diameter saw bladeswhich is able to reach sufficient reduction ratios for reaching desired peripheral sawblade speeds and thus desired performance, it is possible to remove any jack shafts orother additional transmissions from the drive. Thereby can a more efficient flat saw be provided with reduced complexity.
    In one embodiment, the dynamic belt tensioner of the blade shaft drivecomprises a resilient member, said belt tensioner further comprises a rotatable idlerpulley for contact with the belt and a pivot arm connecting the idler pulley to theresilient member. The belt tensioner is beneficial for enabling use of a low profile polyV belt, since it stabilizes the resting tension in the belt and will take up slack in the beltdue to load fluctuations and power pulses from the motor.
    In one embodiment of the teachings herein, the resilient member of the belttensioner is a rubber torsion bar. The rubber tension bar requires little or no lubricationand is subj ected to only small amounts of wear since metal to metal friction is reduced.
    In a further embodiment, the blade is attached to the blade shaft via a flange,wherein the ratio between the diameter of said flange and the diameter of said blade isapproximately at least 1 to 6. The ratio between the diameters of the flange and the sawblade is important for safety reasons, if the flange is made smaller in relation to the sawblade the risk of wobbling and uneven cuts increases. The flange will also be arestriction in cutting depth for any given saw blade diameter.
    In one embodiment, the reduction ratio of the blade shaft drive from the powertake out shaft to the blade shaft is in the range of approximately 1:3.6 to approximately1:1.5, preferably approximately 1:2 for a blade diameter of approximately 30” (760mm). The above reduction ratios are beneficial in that they enable the blade shaft driveto reduce the rotational speed from the power take out shaft of the motor to the bladeshaft sufficiently to reach the preferred peripheral speeds of the saw blade for saw bladediameters above 25”.
    In one embodiment of the teachings herein, the outer diameter of said secondpulley is smaller than 1/ 6 of the diameter of the saw blade. Thus, the diameter of thesecond pulley and the surrounding belt will not be a limiting factor for the saw depth,since it will have a smaller diameter than the flange.
    In one embodiment, the saw blade diameter is approximately 25” (635 mm) orlarger.
    In a further embodiment, the low profile belt, such as a poly V belt, has an ISO9982 standardized belt profile selected from the group consisting of PH, PJ, PK, PL andPM, a preferred belt profile being PK. The above belt is a low profile belt, with ribs that does not protrude extensively. As these types of belts allow smaller pulley diametersand bending radius compared to regular V-belts used on flat saws, the ratio can beincreased.
    In one embodiment, the motor is an internal combustion engine with a ratedpower output larger than 25 hp (about 18.6 kW).
    In one further embodiment, the internal combustion engine comprises betweenone and four cylinders, preferably two cylinders.
    In one embodiment, the motor is an electric motor with a rated power outputlarger than 25 hp (about 18.6 kW).
    In yet one further embodiment, the low profile belt comprises between 17 and30 longitudinal ribs, preferably approximately 25 longitudinal ribs for a blade diameterof approximately 30” (760 mm). The number of ribs on the low profile belt is closelylinked to the friction between the pulleys and the belt, and thereby also to the power thatthe belt is able to transfer. The above ranges have proven beneficial in that the belt is able transfer sufficient amounts of power without risking any significant belt slippage.
    BRIEF DESCRIPTION OF THE DRAWINGS Embodiments of the teachings herein will be described in further detail in thefollowing with reference to the accompanying drawings which illustrate non-limitingexamples on how the embodiments can be reduced into practice and in which: Fig. 1 shows a perspective view of a flat saw according to one embodiment, Fig. 2 shows a side view of a schematic outline of the blade shaft driveaccording to one embodiment, Fig. 3 shows a cross sectioned top view of a schematic outline of the bladeshaft drive according to one embodiment, and Fig. 4 shows a cross sectioned view of a low profile belt such as a poly V belt according to one embodiment.
    DETAILED DESCRIPTION OF EMBODIMENTS The disclosed embodiments will now be described more fully hereinafter withreference to the accompanying drawings, in which certain embodiments of the inventionare shown. Like numbers refer to like elements throughout.
    In Fig. 1, a perspective view of a high power flat saw 10 according to oneembodiment is shown. The flat saw 10 comprises a motor 11, preferably an internalcombustion engine 11 with a rated power output larger than 25 hp (l8.6 kW) andcomprising between one and four cylinders. The combustion engine ll is configured tooperate at between approximately 1000 RPM to 4000 RPM, preferably at its top peak oftorque and power at approximately 3000 RPM to 3600 RPM. The industry standardRPM for combustion engines must be taken into consideration. The motor ll may alsobe an electrical motor 11, configured to achieve a power output of at least 25 hp (l8.6kW). The electrical motor may be for instance a brushless DC motor, a switchedreluctance motor, a universal motor, or an AC motor. These examples should not beseen as limiting, any electrical motor which can deliver the specified power output maybe used. The saw blade 12 is a large diameter saw blade 12, having a diameter ofapproximately 25” (about 635 mm) or larger. The motor ll is connected via a bladeshaft drive 1 to the blade shaft 9 and the saw blade 12. The blade shaft drive 1comprises a low profile belt 6 such as a poly V belt for powering the blade shaft 9 andthus the saw blade 12.
    The blade shaft drive 1 further comprises a first pulley 2 and a second pulley 3,the first pulley 2 having a smaller diameter than the second pulley 3 to achieve areduction ratio between the motor ll and the saw blade shaft 9. This is necessary sincemost saw blades 12 are designed to function optimally when the peripheral speed of theblade is around or below 65 m/s while performing cuts. Thus, the blade shaft drive 1must reduce the rotational speed from the motor 11 power take out shaft 8 to the bladeshaft 9. The power take out shaft 8, or output shaft, is the shaft through which power isdelivered by the motor ll and is preferably an extension of the crankshaft or rotor ofsaid motor ll. A reduction ratio of between 113.6 and 1:1.5 is desired depending on theactual diameter of the saw blade. A preferred reduction ratio is approximately 1:2 for a blade diameter of approximately 30” (760 mm). The above reduction ratios are required for large diameter saw blades 12, i.e. blades With a diameter in excess of 25”. The first 2and second 3 pulleys are directly rotationally connected by the low profile belt 6, thusrotation of one pulley will cause rotation of the other and no intermediate shaft ortransmission is needed for achieving above mentioned reduction ratios.
    With reference to Figs 1, 2 and 3 simultaneously, the first pulley 2 is connectedto the power take out shaft 8, which preferably is an extension of the crankshaft/rotor ofsaid motor 11, thus avoiding any gearing between the power take out shaft 8 and thecrankshaft/rotor of the motor 11. Such an extension may in one embodiment be aseparate shaft such as a stub shaft connected to the crank shaft/rotor for instance bymeans of a spline connection or clutch. The opening in the motor housing throughwhich the extension of crank shaft extends may further comprise a bushing and/or abearing to support the shaft 8 and to ensure that for instance lubricant will not leak outfrom the motor 11.
    The second pulley 3 is connected to the blade shaft 9 which in tum isconnected to the saw blade via a flange 7. The first 2 and second 3 pulleys may beconnected to their respective shafts 8, 9 by means of spline connections, fasteners or anyother commonly known means for fixing a pulley to a shaft.
    The blade shaft 9 may, which is shown in Fig. 1, extend to the opposite side ofthe flat saw 10 in relation to the blade shaft drive 1 and connect via the flange 7 to thesaw blade 12 on that side of the saw 10. Another alternative is shown in Fig. 3, wherethe flange 7 and the blade shaft drive 1 are located on the same side of the flat saw 10.The blade shaft 9 is rotatably attached to the flat saw 10. The saw blade 12 is fitted tothe blade shaft flange 7 by means of fasteners, such as one or several nuts, screws orbolts. The diameter of the flange 7 is at least one sixth of the diameter of the saw blade,which is required to avoid wobbling and uneven cuts. As it is desired to achieveincreased saw depths for any given saw blade diameter, the above relationship betweenthe blade and the flange is a restriction as safety can by no means be compromised forachieving larger saw depths.
    The saw depth also comes in conflict with the desire to achieve a highreduction ratio for the blade shaft drive 1, since it is in this regard desired to increase the size of the second pulley 3 and to decrease the size of the first pulley 2. The second pulley 3 should not be larger than the flange 7 since this Will limit saw depth. Flat sawsare often configured such that the saw depth can be varied. This can be achieved in anumber of ways, one of which may be to fit a wheel on a frame which can be loweredand raised by the operator of the saw 10. By lowering and raising the Wheel, the sawpivots around the two rear wheels (in the case where the saw blade 12 is mounted to thefront of the saw 10 as is shown in Fig. 1) which allows the saw depth to be varied.When the saw depth is increased, the limiting component for the saw depth of the saw10 should preferably be the flange 7 and not the second pulley 3 and/or belt. Preferably,the flange 7 is prevented from coming into contact with the surface to be cut byproviding a predefined mechanical stop for the frame and wheel defining a maximumsaw depth, wherein said maximum saw depth is preferably less than the maximumradius of the saw blade minus the maximum radius of the flange. Furthermore, adecrease in the size of the first pulley 2 is also limited by for instance the size of thepower take out shaft 8 and belt properties.
    In prior art, to achieve a suitable reduction ratio in view of the above,gearboxes or jackshafts are commonly used. This however causes the overall efficiencyof the flat saw to decrease and adds unnecessary complexity to the blade shaft drive. Itis especially problematic to achieve the correct reduction ratio for high power flat sawswith large saw blade diameters since a larger blade requires a higher reduction ratio.The applicant has trough insightful and inventive reasoning realized that by providing apoly V belt 6 as specified in this disclosure having a low belt profile in combinationwith a belt tensioner 4, it is possible to achieve sufficient reduction ratio while removingthe need for a gearbox or a jackshaft. The functionality of such a blade shaft drive 1 isimproved by the dynamic belt tensioner 4, by significantly reducing the risk of beltslippage and the tensioner 4 will take up slack in the belt 6 due to fluctuations andpower pulses from the combustion engine 11.
    As can be seen in Fig. 2, the belt tensioner 4 applies a force to the side of thelow profile belt 6 which does not comprise ribs 61, i.e. the flat side. It is however alsopossible that the belt tensioner 4 applies a force to the ribbed side of the belt 6. The belttensioner 4 comprises a pivot arm 41 and an idler pulley 42. The idler pulley 42 is rotatably connected to the pivot arm 41 and is airanged such that it comes into contact With the belt 6. The pivot ann 41 is, at the end opposite the idler pulley 42, connected toa resilient member 43 such as a torsion bar or a torsion spring which allows the pivotarm 41 to pivot in a resilient manner and apply a dynamic force to the belt 6. Theresilient member 43 may in one embodiment be a rubber torsion bar. In Fig. 3, the bladeshaft drive 1 can be seen from a top view also showing the blade shaft 9 and the powertake out shaft 8. The power take out shaft 8, as mentioned above, is preferably anextension of the crank shaft/rotor of the motor 11.
    As large amounts of torque and power is transferred through the power take outshaft 8 to the first pulley 2, it is beneficial to keep the diameter of the power take outshaft 8 as large as possible to enable it to withstand high loads. This however comes inconflict With the desire to reduce the diameter of the first pulley 2 to increase thereduction ratio, which emphasizes the need to keep the protrusion of the ribs of the belt6, i.e. the belt profile, as low as possible. Since reducing the protrusion of the ribs 61 ofa belt 6 reduces its ability to transfer torque and increases for instance the risk of beltslippage, this is not an obvious solution to reduce the diameter of the first pulley 2.However, as mentioned above, the addition of the belt tensioner 4 which harmonizes thetension in the belt 6 during different load conditions and the selection of the number ofribs of the be1t6 as specified below will make it possible to provide a blade shaft drive1 with a low profile belt 6. This has been achieved through extensive testing, in whichthe applicant discovered that it is possible to achieve the desired reduction ratio, thusreaching a maximum velocity of 65 m/s of the peripheral edge of the saw blade whileavoiding any further transmission means for high powered flat saws with large diametersaw blades. With reference to Fig. 4, a cross sectioned view of an exemplary low profilebe1t6 such as a poly V belt can be seen. The belt 6 preferably comprises 25 longitudinalribs 61, however the number of ribs 61 may be in the range of 17 to 30. The first 2 andsecond 3 pulleys naturally comprises corresponding numbers of grooves for interactionwith the ribs 61 of the belt 6. The belt 6 profile may be any one of the ISO 9982standardized profiles PH, PJ, PK, PL and PM. As these profiles are described in ISO9982, they will not be described in further detail in this disclosure. A preferred beltprofile is PK. However, other low profile poly-V belt profiles defined or not defined inISO 9982 may also be used.
    It should be mentioned that the inventive concept is by no means limited to theembodiments described herein, and several modifications are feasible Without departingfrom the scope of the invention as defined in the appended claims. For instance, two or more separate poly V belts could be used.
    权利要求:
    Claims (12)
    [1] 1. High power flat saw (10) having a large diameter saw blade (12), said flatsaw (10) comprising a motor (11) and a blade shaft drive (1), wherein said blade shaftdrive (1) comprises a first pulley (2) and a second pulley (3) and a belt (6), said secondpulley (3) being directly connected to a blade shaft (9), said first pulley (2) having asmaller diameter than the diameter of said second pulley (3), and wherein said drive (1)further comprises a dynamic belt tensioner (4) arranged to apply a dynamic force to saidbelt (6), characterized in that the first pulley (2) is directly connected to a power takeout shaft (8) being an extension of a crankshaft/rotor of said motor (11), wherein saidfirst (2) and said second (3) pulleys are directly rotationally connected by the belt (6)and wherein the belt (6) is a low profile belt (6) such as a poly V belt.
    [2] 2. A high power flat saw according to claim 1, wherein the dynamic belttensioner (4) of the blade shaft drive (1) comprises a resilient member (43), said belttensioner (4) further comprises a rotatable idler pulley (42) for contact with the belt (6) and a pivot arm (41) connecting the idler pulley (42) to the resilient member (43).
    [3] 3. A high power flat saw according to claim 2, wherein the resilient member (43) is a rubber torsion bar.
    [4] 4. A high power flat saw according to any one of the preceding claims, whereinthe blade (12) is releasably connected to the blade shaft (9) via a flange (7), and whereinthe ratio between the diameter of said flange (7) and the diameter of said blade (12) is at least 1 to 6.
    [5] 5. A high power flat saw according to any one of the preceding claims, whereinthe reduction ratio of the blade shaft drive (1) from the power take out shaft (8) to theblade shaft (9) is in the range of between 133.6 and 131.5, preferably approximately 1:2 for a blade diameter of approximately 30” (about 760 mm). ll
    [6] 6. A high power flat saw according to any one of the preceding claims, whereinthe outer diameter of said second pulley (3) is smaller than 1/6 of the diameter of the saw blade.
    [7] 7. A high power flat saw according to any one of the preceding claims, wherein the saw blade (12) diameter is approximately 25” (about 635 mm) or larger.
    [8] 8. A high power flat saw according to any one of the preceding claims, whereinthe low profile belt (6) has an ISO 9982 standardized belt profile selected from thegroup consisting of PH, PJ , PK, PL and PM, a preferred belt profile being PK.
    [9] 9. A high power flat saw according to any one of the preceding claims, whereinthe motor (1 1) is an intemal combustion engine (1 1) with a rated power output larger than 25 hp (18.6 kW).
    [10] 10. A high power flat saw according to any one of claims 1 to 8, wherein the motor (1 1) is an electrical motor with a rated power output larger than 25 hp (l8.6 kW).
    [11] 11. A high power flat saw according to claim 9, wherein the intemalcombustion engine (11) comprises between one and four cylinders, preferably 2 cylinders.
    [12] 12. A high power flat saw according to any one of the preceding claims,wherein the low profile belt (6) comprises between 17 and 30 longitudinal ribs (61), preferably approximately 25 longitudinal ribs (61).
    类似技术:
    公开号 | 公开日 | 专利标题
    US4664645A|1987-05-12|Blade shaft drive assembly
    CA2521132A1|2004-10-21|Helically-toothed-belt transmission device
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    US9592725B2|2017-03-14|Remote located clutch
    SE1551579A1|2017-06-03|Blade shaft drive
    BRPI0908526A2|2019-02-26|vehicle power unit
    EP1582768A3|2006-08-16|Belt type continuously variable transmission
    KR101339190B1|2013-12-10|Power Transmission Apparatus for Electric Vehicle with Continuousle Variable Transmission
    JP2007146801A5|2008-11-27|
    FR2918319B1|2019-05-10|TRANSMISSION LINE FOR A MOTOR VEHICLE
    CN201422266Y|2010-03-17|Self-propelled power transmission system of mowing vehicle
    GB2511315A|2014-09-03|Oil pump drive
    JP2844978B2|1999-01-13|Variable speed accessory drive
    KR200417585Y1|2006-05-30|The power transmit device for slice-mixer
    CN209170911U|2019-07-30|Double end grass trimmer and its transmission device, grass-mowing
    RU43198U1|2005-01-10|SCREW CENTRIFUGE DRIVE
    WO2009102263A1|2009-08-20|Apparatus for driving a cooling fan
    KR20010000357A|2001-01-05|A automatic transmission without location of automobile
    JPH0719305A|1995-01-20|Conical friction wheel type gear ratio continuously variable transmission
    EP3853501A1|2021-07-28|Powertrain with a continuously variable transmission for an electric vehicle and method for operating such powertrain
    EP2690317A2|2014-01-29|Driven-side pulley
    KR960029662A|1996-08-17|Composite for continuously variable transmission
    同族专利:
    公开号 | 公开日
    AU2016364683A1|2018-06-21|
    US20170304914A1|2017-10-26|
    SE539452C2|2017-09-26|
    CN108602142A|2018-09-28|
    EP3383571A4|2019-08-07|
    WO2017095291A1|2017-06-08|
    EP3383571A1|2018-10-10|
    AU2016364683B2|2021-09-09|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1551579A|SE539452C2|2015-12-02|2015-12-02|Blade shaft drive|SE1551579A| SE539452C2|2015-12-02|2015-12-02|Blade shaft drive|
    AU2016364683A| AU2016364683B2|2015-12-02|2016-09-20|High power flat saw with blade shaft drive|
    US15/513,382| US20170304914A1|2015-12-02|2016-09-20|High power flat saw with blade shaft drive|
    EP16871142.2A| EP3383571A4|2015-12-02|2016-09-20|High power flat saw with blade shaft drive|
    PCT/SE2016/050876| WO2017095291A1|2015-12-02|2016-09-20|High power flat saw with blade shaft drive|
    CN201680080789.3A| CN108602142A|2015-12-02|2016-09-20|The high power flat sawing of band saw blade axis driver|
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