• 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:
    Eccentric shaft (1) for compaction machine, comprising at least a pair of straight circular cylindrical bearing seats (2,3) arranged on each side about the center of gravity (TP) of the center of gravity (1). The bearing seats (2, 3) are arranged in such a way that their cylinder axes (4, 5) approximately intersect or intersect at a concave angle (V), less than 179.8 degrees, towards the center of gravity (TP) when the eccentric axis (1) is located The invention relates to the design of eccentric shafts for compaction machines such as e.g. rollers and vibrator plates. The eccentric shafts are rotatably connected via bearings to the rollers / bottom plates of the rollers / vibration plates and in the intended manner cause them to vibrate when the shafts are actuated to rotate at an appropriate operating speed. The eccentric shafts assume a slightly curved shape during the rotating operation due to the action of the centrifugal force on the eccentrically offset center of gravity of the shaft. The curved shape causes unwanted misalignments of the eccentric shaft bearing seats. The present invention provides exemplary embodiments where the skew in the bearings is virtually eliminated. The invention is particularly suitable for slender eccentric shafts which are designed with a low moment of inertia to be easy to start. In the U.S. patent, US 8206061, an eccentric axis is shown which is optimized with respect to (low) moment of inertia. The shaft has an I-shaped section to counteract the tendency of the shaft to bend out during operation rotation. In the Swedish patent specification, SE53704, the tendency of the easy-to-start eccentric shaft to deflection is limited by a calculated consideration of the bending stress in the most loaded section of the shaft. The skew in the eccentric shaft bearings is thus manageable, but it would be advantageous if the skew could be minimized or eliminated completely. The deflection of the known eccentric shaft and the inclination of its bearing seats are illustrated in Figures 1-2 of the present application. The object of the present invention is to obtain an eccentric shaft whose inclination in the bearings is virtually eliminated when the shaft is rotated in operation. The present invention fulfills the object in that the eccentric shaft is made with a calculated shape change which results in the bearing seats of the shaft being straightened when the shaft is rotated in operation. The invention will be described in more detail with the aid of the attached figures 1-4. Figure 1 shows a previously known eccentric shaft, when it is at rest. Figure 2 shows the known eccentric axis from figure 1 during operation rotation. Figure 3 shows an eccentric shaft made according to the present invention, in a view across its longitudinal extension direction and when the shaft is at rest. Figure 4 shows the eccentric shaft of figure 3 during operation rotation, shows a previously known eccentric shaft 1, comprising a pair of circular cylindrical bearing seats 2, 3, arranged on each side of the center of gravity TP of the center of gravity 1. The position description "on each side" in this context refers to positions in the 1st longitudinal extension direction of the eccentric axis. The bearing seats 2, 3 are arranged along their cylinder axes 4 and 5, respectively, which approximately coincide according to theoretical intentions. In series production of eccentric shafts 1, however, the cylinder shafts 4, 5 will randomly coincide, intersect and intersect due to normal deviations. The center of gravity TP is in the intended manner slightly radially displaced from the coinciding cylinder axes 4, 5 in order to give the eccentric shaft 1 an eccentric action when it is rotated in operation. Shows how the known eccentric shaft 1 from Figure 1 bends out when the shaft 1 is rotated in operation. The eccentric shaft 1 is connected via a shaft coupling to a drive motor (not shown) which rotationally rotates the eccentric shaft 1. The deflection is extremely excessive in the figure to illustrate the phenomenon. The bearings 6, 7 are arranged so as to allow the axial displacement which occurs when the eccentric shaft 1 bends out. The curved shape also causes an undesired skew in the bearings 6, 7 of the eccentric shaft 1. It is entirely possible to arrange the bearings 6, 7 so that they can withstand the skews, but often the skews lead to increased heat generation and shortened life of the bearings 6, 7. on an eccentric shaft 1 according to the present invention. The eccentric shaft 1 has the same performance and is driven and stored in the same way as the eccentric shaft 1 in Figure 1-2. The eccentric shaft 1 comprises a pair of circular cylindrical bearing seats 2, 3, arranged on each side of the center of gravity TP of the center of gravity 1. The bearing seats 2, 3 are arranged along the cylindrical axes 4 and 5 of the circular cylindrical shapes. The bearing seats 2, 3 are arranged in such a way that the cylinder axes 4, 5 approximately intersect each other and in such a way that the center of gravity TP is approximately in a plane determined by 4, 5. The bearing seats 2, 3 are also arranged in such a way that the cylinder shafts 4, 5 intersect at a slightly concave angle V towards the center of gravity TP. The concavity is greatly exaggerated in the figure. As previously mentioned in connection with Figure 1, normal deviations in series production and chance can result in a concave angle V being obtained. However, such eccentric shafts do not provide any appreciable or significant technical effect with respect to the effect sought in the present application. It is unlikely that the most conceivable wide manufacturing tolerance could lead to concave angles V that are less than 179.8 degrees. Claim 1 of the present application therefore excludes eccentric shafts having concave angles of 179.8 degrees or greater. The angle V is 179.4 degrees and is determined by a theoretical calculation of the angular change of the bearing seats 2, 3 when the eccentric shaft 1 is rotated in operation. The bearing seats 2, 3 are calculated in this case to be inclined 0.3 degrees during operation rotation and the angle V is therefore determined to be 180-0.3-0.3 = 179.4 degrees. The start-up of the eccentric shaft 1 will consequently take place during an inclination of the bearing seats 2, 3 of 0.3 degrees each. The previously mentioned shaft coupling will therefore be forced a small wobbling movement during the start-up of the eccentric shaft 1. However, it is quite possible to arrange shaft couplings which can withstand starts at angles V down to 179 degrees or to arrange other types of coupling arrangements which can withstand start-ups degrees. The term "approximately" used above refers in this context to the deviations that normally occur as a result of more or less extensive manufacturing tolerances. In the first exemplary embodiment described above, it is assumed that the eccentric shaft 1 is manufactured according to the narrowest possible tolerances. This provides the best conditions for achieving the advantages of the invention. With wider manufacturing tolerances, or for other reasons, it may be more convenient to describe the cylinder shafts 4, 5 as crossing each other. Such a second embodiment of the invention also provides good conditions for achieving the advantages of the invention. The angle V and the above-mentioned plane are determined in this case by the angle between one of the cylinder shafts 4, 5 and one with this cutting line, parallel to the other of the cylinder shafts 4, 5. The eccentric shaft 1 is most suitably made of ductile iron or cast steel and its bearing seats 2 , 3 and arrangements for connection connections, machined forward by means of a multi-operation machine or equivalent. It is also possible, but not recommended, to bend the eccentric shaft 1 to the angle V. It is also possible to design the middle part of the eccentric shaft slightly bent (in st.f. straight) in order to thus indicate and ensure the desired shape change during operating rotation. shows how the calculated shape change during operating rotation of the eccentric shaft 1 resulted in a deflection of the shaft 1 and an expected straightening of its bearing seats 2, 3. The operating rotation has consequently resulted in an addition of 0.3 + 0.3 degrees to those mentioned in Figure 3. 179.4 degrees. The straightening of the bearing seats 2, 3 and the corresponding cylinder shafts 4, 5 causes the shafts 4, 5 to approximately coincide in a rotation center axis around which the operating rotation takes place. The bearings 6, 7 will thus be loaded under ideal conditions since the inclination of the bearing positions 2, 3 is virtually eliminated when the eccentric shaft 1 is rotated in operation. In interpreting the present application claims, known eccentric shafts having concave angles described above due to unintentional deformations after transport damage, breakdowns or similar events.
    公开号:SE1600149A1
    申请号:SE1600149
    申请日:2016-04-29
    公开日:2017-10-30
    发明作者:Persson Andreas；Christensen Hans
    申请人:Dynapac Compaction Equipment Ab；
    IPC主号:
    专利说明:

    Eccentric shaft for compaction machine The invention relates to the design of eccentric shafts for pre-compaction machines such as roller rollers and vibrator plates. The eccentric shafts are rotatably connected via bearings / roller plates of the rollers / vibration plates and actuate these to vibrate when the shafts are actuated to rotate at an appropriate operating speed. The eccentric shafts assume a slightly curved shape during rotating operation due to the effect of the central force on the axis eccentrically offset center of gravity. The bent shape causes undesired adjustments of the bearing seats of the eccentric shaft. The present invention provides exemplary embodiments where the skew in the bearings is virtually eliminated. The design is especially suitable for slim eccentric shafts which are designed with a low moment of inertia to make it easier to start.
    U.S. Pat. No. 8,206,061 discloses an eccentric shaft which is optimized for (low) moment of inertia. The shaft has an I-shaped section to counteract the shaft's tendency to bend outward rotation. In the Swedish patent specification, SE53704, the tendency of the easy-to-start eccentric shaft to deflection is limited by a calculated consideration of the bending stress in the most stressed section of the shaft. and the skew of its bearing seats is illustrated in Figures 1-2 of the present application. The object of the present invention is to obtain an eccentric shaft warning reduction in the bearings is virtually eliminated when the shaft drive is rotated. The present invention fulfills the purpose in that the attex center axis is made with a calculated shape change which results in the bearing seats of the shaft being straightened when the shaft is rotated in operation.
    The invention will be described in more detail with the aid of the accompanying Figures 1-4. Figure 1 shows a previously known eccentric axis, when it is at rest. Figure 2 shows the known eccentric axis from fi gur l underrun rotation. Figure 3 shows an eccentric shaft made according to the present invention, in a view across its longitudinal extension direction and when the shaft is at rest. Figure 4 shows the eccentric axis from fi gur 3 underrun rotation.
    Figure 1 shows a previously known eccentric shaft 1, comprising a parcircular cylindrical bearing seats 2,3, arranged on each side of the center of gravity TP of the center of gravity 1. The position description "on each side" in this context refers to positions in the longitudinal extension direction of the eccentric axis. The bearing seats 2,3 are arranged along the cylindrical axes 4 and 5 of the circular cylinder shapes, respectively, which approximately coincide according to theoretical intentions. In series production of axis center shafts 1, however, the cylinder shafts 4,5 will randomly coincide, intersect and intersect due to normal deviations. The center of gravity TP is intended to be slightly radially offset from the coincident cylinder shafts 4,5 to give the eccentric shaft 1 eccentric effect when rotated.
    Figure 2 shows how the known eccentric shaft 1 from Figure 1 bends out when the shaft n1 is rotated in operation. The eccentric shaft 1 is connected via a shaft coupling to a single-drive motor (not shown) which rotates the eccentric shaft 1. The deflection is extremely exaggerated in the uren clock to illustrate the phenomenon. The bearings 6,7 are arranged so as to allow the axial displacement which occurs when the eccentric shaft 1 bends out. The curved shape also causes an undesired reduction in the bearings 6,7 of the eccentric shaft 1. It is quite possible to arrange the bearings 6,7 so that they can withstand the skew, but often the pre-cuts increase heat generation and shorten the service life of the bearings 6,7.
    Figure 3 shows a first embodiment of an eccentric shaft 1 according to the present invention. The eccentric shaft 1 has the same performance and is drive driven in the same way as the eccentric shaft 1 in Figure 1-2. The eccentric shaft 1 comprises a pair of circular cylindrical bearing seats 2,3, arranged on each side of the center of gravity TP of the center of gravity 1. The bearing seats 2,3 are arranged along the cylindrical axes 4 and 5 of the circular cylindrical shapes. The bearing seats 2,3 are arranged in such a way that the cylinder shafts 4,5 approximatively intersect each other and in such a way that the center of gravity TPapproximatively lies in a plane determined by the cutting cylinder shafts 4,5. The bearing seats 2,3 are also arranged in such a way that the cylinder shafts 4,5 cut each other at a slightly concave angle V towards the center of gravity TP. The concavity is greatly exaggerated in the fi shape.
    As previously mentioned in connection with Figure 1, normal deviations in series production and chance can result in a concave angle V being obtained. However, such eccentric shafts do not produce any appreciable or significant technical effect with respect to the effect sought in the present application. It is probable that the most conceivable wide manufacturing tolerance could lead to concave angles V that are less than 179.8 degrees. The present application claim 1 therefore excludes eccentric axes exhibiting concave angles of 179.8 degrees or greater.
    The angle V is 179.4 degrees and is determined by a theoretical calculation of the 2.3 change in the angle of the bearing seats when the eccentric shaft 1 is rotated in operation. The bearing seats2,3 are calculated in this case to be inclined 0.3 degrees during operation rotation and the angle V is therefore determined to 180-0.3-0.3 = l79.4 degrees. The start-up of the avex center axis 1 will consequently take place during an inclination of the bearing seats 2,3 of 0.3 degrees each. The previously mentioned shaft coupling will therefore be forced a small wobbling movement during the start-up of the avex center axis 1. However, it is quite possible to arrange shaft couplings which handle start-ups with angles V down to 179 degrees or to arrange other types of coupling arrangements which can handle start-ups with angles down to 178 degrees. The term "approximately" used above refers in this context to the deviations that normally occur as a result of more or less extensive manufacturing tolerances. In the first embodiment described above, it is assumed that the eccentric shaft 1 is manufactured according to the narrowest possible tolerances. This provides the best conditions for achieving the benefits of the invention. For wider manufacturing tolerances, or for other reasons, it may be more convenient to describe the cylinder shafts 4,5 as intersecting. Such a second exemplary embodiment of the coil also provides good conditions for achieving the advantages of the coil. The angle V and the above-mentioned plane are determined in this case by the angle between one of the cylinder shafts 4,5 and one with this cutting line, parallel to the other of the cylinder shafts 4, 5. The eccentric shaft 1 is most suitable in ductile iron or cast steel and its bearing seats 2,3, as well as arrangements for coupling connections, are machined forward with the aid of an operating machine or equivalent. It is also possible, but not recommended, to bend the eccentric axis 1 to the angle V.
    It is also possible to design the central portion of the eccentric shaft slightly bent (instead of straight) in order to indicate and ensure the desired shape change during operating rotation.
    Figure 4 shows how the calculated shape change during operating rotation of the center axis 1 resulted in a deflection of the axis 1 and an expected straightening of its bearing seats 2,3. The drive rotation has consequently resulted in an addition of 0.3 + 0.3 degrees to the 179.4 degrees mentioned in Figure 3. The alignment of the bearing seats 2,3 and the corresponding cylinder shafts 4,5 causes the shafts 4,5 to approximately coincide in a rotation center axis around which the operation rotation takes place. The bearings 6,7 will thus be loaded under ideal conditions since the inclination in the bearing positions 2,3 is virtually eliminated when the eccentric shaft 1 is rotated in operation.
    In interpreting the present application of claims, eccentric shafts which exhibit concave angles described above due to unintentional deformations following transport damage, breakdowns or similar events shall be disregarded.
    权利要求:
    Claims (1)
    [1]
    Eccentric shaft (1) for compacting machine, comprising at least one pair of straight circular cylindrical bearing seats (2, 3) arranged on each side of the center of gravity (TP) of the eccentric shaft (1), characterized in that the bearing seats (2, 3) are arranged on their cylindrical axes (4, 5) approximately intersects or intersects at a concave angle (V), less than 179.8 degrees, the counter-center of gravity (TP) when the eccentric axis (1) is at rest. . Eccentric shaft (1) according to claim 1, characterized in that the cylinder shafts (4, 5) approximately intersect each other and in that the center of gravity (TP) lies approximately in a plane determined by the cutting shaft shafts (4, 5). . Eccentric shaft (1) according to claim 1, characterized in that the cylinder shafts (4, 5) cross each other and in that the center of gravity (TP) lies approximately in a plane determined by one of the cylinder shafts (4, 5) and a line parallel thereto, with the other of the cylinder shafts (4, 5). Eccentric shaft (1) according to one of Claims 1 to 3, characterized in that the angle (V) is greater than 178 degrees. . Eccentric shaft (1) according to one of Claims 1 to 4, characterized in that the angle (V) is greater than 179 degrees.
    类似技术:
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    同族专利:
    公开号 | 公开日
    US10577756B2|2020-03-03|
    SE539929C2|2018-01-16|
    CN109154149B|2021-05-11|
    DE112017002243T5|2019-02-28|
    US20190145060A1|2019-05-16|
    CN109154149A|2019-01-04|
    WO2017188884A1|2017-11-02|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    US5857388A|1996-07-09|1999-01-12|Simpson Industries, Inc.|Balance shafts having minimal mass|
    JP3608502B2|2000-11-07|2005-01-12|株式会社デンソー|Rotating device|
    US6516679B2|2001-01-29|2003-02-11|Ingersoll-Rand Company|Eccentric assembly with eccentric weights that have a speed dependent phased relationship|
    DE202007013473U1|2007-09-25|2007-12-13|Acument Gmbh & Co. Ohg|Eccentric adjustment|
    DE102008026204A1|2008-05-30|2009-12-03|Schaeffler Kg|Bearing arrangement of a shaft|
    DE102009009127A1|2009-02-17|2010-09-16|Schaeffler Technologies Gmbh & Co. Kg|Coil for a superconducting magnetic bearing|
    BRPI0902973B1|2009-08-27|2020-03-10|Embraco Indústria De Compressores E Soluções E Refrigeração Ltda.|ALTERNATIVE REFRIGERATION COMPRESSOR BLOCK|
    US8206061B1|2011-05-26|2012-06-26|Caterpillar Inc.|Eccentric vibratory weight shaft for utility compactor|
    SE537044C2|2013-04-29|2014-12-16|Dynapac Compaction Equip Ab|Eccentric shaft for compacting machine|
    CN103591121B|2013-11-19|2016-01-20|无锡市铁民印刷机械有限公司|Eccentric drive shaft|
    US8967910B2|2014-01-22|2015-03-03|Caterpillar Paving Products Inc.|Eccentric weight shaft for vibratory compactor|
    US9394939B2|2014-01-31|2016-07-19|CEROBEAR GmbH|Bearing system and methods of use thereof|CN111868329A|2018-03-15|2020-10-30|沃尔沃建筑设备公司|Fan for lubrication and cooling of eccentric bearings in surface compactors|
    CN110439915B|2019-08-15|2020-05-08|杭州萧山建一五金有限公司|Transmission shaft|
    DE102019134453A1|2019-12-16|2021-06-17|Hamm Ag|Unbalance arrangement|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1600149A|SE539929C2|2016-04-29|2016-04-29|Eccentric shaft for compacting machine|SE1600149A| SE539929C2|2016-04-29|2016-04-29|Eccentric shaft for compacting machine|
    DE112017002243.6T| DE112017002243T5|2016-04-29|2017-04-26|Eccentric shaft for a compaction machine|
    US16/097,064| US10577756B2|2016-04-29|2017-04-26|Eccentric shaft for a compaction machine|
    PCT/SE2017/050408| WO2017188884A1|2016-04-29|2017-04-26|Eccentric shaft for a compaction machine|
    CN201780026535.8A| CN109154149B|2016-04-29|2017-04-26|Eccentric shaft for compacting machine|
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