• 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:
    The present invention relates to a shaft joint comprising a first shaft (1) supported by a bearing at one end (1-1) and a second shaft (2) supported by a bearing at a second end (2-2). Said first shaft (1) and second shaft (2) are coaxially arranged such that one end (1-2) of the first shaft (1) is opposite to the first end (2-1) of the second shaft (2). The end surface of the second end (1-2) of the first shaft (1) has a recess (6) and a projection (7) protruding from the end surface of the first end (2-1) of the second shaft (2) and receiving said protrusion (7). The shaft coupling further comprises only one third bearing (8) and a coupling (9) receiving the second end (1-2) of the first shaft (1) and the first end (2-1) of the second shaft (2). Such a solution can allow for greater radial error between the shafts without overloading the joints structures.
    公开号:FI20185062A1
    申请号:FI20185062
    申请日:2018-01-23
    公开日:2019-07-24
    发明作者:Teppo Lindberg；Jussi Puhakka；Pekka Laakkonen
    申请人:Konecranes Global Oy；
    IPC主号:
    专利说明:

    FIELD OF THE INVENTION The present invention relates to transmission in shaft couplings.
    Description of the Related Art It is known in the art to connect the shafts coaxially to each other for transmission such that a single bearing is provided at the first and second ends of the first and second shafts, i.e. a joint comprising four bearings.
    The problem with the above solution is that the radial error between the shafts due to the installation of the shafts can result in a significant load on the structures of the shafts.
    SUMMARY OF THE INVENTION An object of the invention is thus to provide a device for solving the above problem. The object of the invention is achieved by a device characterized by what is stated in the independent claim. Preferred embodiments of the invention are claimed in the dependent claims.
    The above object is achieved by an axle joint comprising a first shaft having a first end and a second end, a first bearing arranged in the vicinity of the first end, and that the invention further comprises a second shaft having a first end and a second end, and with a second bearing disposed adjacent one end, and said first axis and the second axis being coaxially arranged such that one end of the first axis is opposite the first end of the second axis.
    The end surface of the second end of said first shaft has a recess and a projection protruding from the end surface of the first end of the second shaft, and said recess receives said projection so that the side surface of the projection and the side surface of the recess are facing each other. The side surface of the projection or the side surface of the recess, or both of said opposed surfaces, is curved in the axial direction of the first axis and the second axis.
    In order to support the first and second axles, the shaft joint comprises, in addition to the first and second bearings mentioned, only one third bearing arranged near the junction of the first and second axles.
    The shaft coupling further comprises a switch receiving the second end of the first shaft and the first end of the second shaft and engaging these non-
    20185062 prh 23 -01-2018 rotatably to each other to transmit force between said first and second axles.
    Such a shaft connection permits a greater radial error between the shafts, i.e., the shafts need not be as precisely parallel as in the known solutions without significant additional load on the structures of the shaft connection.
    BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be further described in connection with preferred embodiments, with reference to the accompanying drawings, in which:
    Figure 1 shows a cross-sectional view of a first embodiment of the invention; and Fig. 2 is an enlarged cross-sectional view of the embodiment of Fig. 1; and Figure 3 shows an illustration of the teeth of the first shaft, the second shaft 15 and the coupling.
    DESCRIPTION OF AT LEAST ONE EMBODIMENT Fig. 1 shows, by way of example, an overview of a first embodiment of an axle joint. Referring to Fig. 1, this embodiment comprises a first shaft 1 having a first end 1-1 and a second end 1-2, and a first bearing 3 arranged in the vicinity of the first end 1-1.
    The shaft connection further comprises a second shaft 2 having a first end 2-1 and a second end 2-2, with a second bearing 4 arranged adjacent the second end 2-2. Said first axis 1 and second axis 2 are coaxially arranged, i.e. the center lines of both axes located on the same axis 5. The axes 25 are further arranged such that the second end 1-2 of the first axis 1 is opposite the first end 2-1 of the second axis 2. The first shaft 1 may be the motor shaft and the second shaft 2 may be the gear shaft as exemplified in Fig. 1.
    In addition to the said first bearing 3 and the second bearing 4, the shaft joint 30 comprises only one third bearing 8, which is provided in the vicinity of the junction of the first shaft 1 and the second shaft 2 to support the first shaft 1 and the second shaft 2. In the embodiment of Figure 1, said third bearing 8 is disposed adjacent the first end 2-1 of the second shaft 2 on the gear side. Thus, there are no more than three bearings supporting the shafts in the entire axle joint.
    20185062 prh 23 -01-2018 Fig. 2 is an enlarged cross-sectional view of the embodiment of Fig. 1. Figure 2 shows that the end surface 12 of the second end 12 of the first end 1 has a recess 6 and a projection 7 protruding from the end surface 2-1 of the first end 2 of the second shaft 2 and receiving said recess 6 so that the side surface The side surface of said projection 7 or the side surface of the recess 6, or both of said opposed surfaces, are shaped in the axial direction of the first axis 1 and the second axis 2. In this example, said projection 7 is shaped like a barrel and the side surface of said recess 10 is shaped to conform to the side surface of the projection 7, taking into account that the first axis 1 and the second axis 2 are axially mutually compatible. As used herein, the term "barrel-like" means that the diameter of the projection is at its maximum at its central portion, and as it moves axially away from the central portion, the diameter of the projection 15 is reduced.
    According to one example, the projection 7 is made barrel-shaped, and the recess 6 is made in the shape of a straight circular cylinder. It is essential for the selection of the mutual shapes of the projection 7 and the recess 6 that the first axis 1 and the second axis 2 receive mutual support in the radial 20 direction, but said axes remain supported relative to each other even if they have a slight angular error between their longitudinal axes.
    Figure 2 further shows that the shaft connection comprises a coupling 9. Said coupling 9 receives the second end 1-2 of the first shaft 1 and the first end 2-1 of the second shaft 2 and engages them non-rotatably to transmit a force 25 to said first shaft 1 and 1. between the second axis 2.
    In the embodiment of Fig. 2, said coupling 9 surrounds the second end 1-2 of the first shaft 1 and the first end 2-1 of the second shaft 2. The outer surface 1-2 of the second end 1-2 of the first shaft 1 is formed as a counterpart to the inner surface of the switch 9 to prevent their mutual rotation, and correspondingly, the outer surface of the first 2-1 ends of the second shaft 2 is formed. The clutch 9 forms a groove shaft connection between the first axis 1 and the second axis 2.
    2 is characterized in that the coupling 9 transmits the torque between the first shaft 1 and the second shaft 2, i.e. the rotation of the axes 35 is prevented. There is a characteristic between the second end 1-2 of the first shaft and the first end 2-1 of the second shaft which are arranged together,
    20185062 prh 23 -01-2018 that their adapter for the projection 7 and the recess 6 are prevented from radial displacement.
    Typically, such an axle joint comprises four bearings. However, in the embodiment shown in Figures 1 and 2, a fourth bearing is not required. The support arrangement of the three bearings, together with the design of the second end 1-2 of the first shaft 1 and the first end 2-1 of the second shaft 2, allows a slightly greater radial error between the shafts without overloading said coupling and / or bearings. This in turn extends the life of the equipment and reduces downtime and the amount of alignment work on the shafts 10 during installation. In the embodiment of Figure 2, the connection between the first shaft and the second shaft 2 further comprises a first O-ring 10 and a second O-ring 11 to ensure tightness of the shaft connection. The first O-ring 10 is arranged near the second end 1-2 of the first shaft 1 and the second O-ring 11 is arranged near the first end 2-1 of the second shaft 2.
    The joint further comprises a retaining ring 12 between the first shaft 1 and the second shaft.
    The bearings of the first axle 1 and the second axle 2 are each provided with one bearing which receives an axial load. Therefore, the axial joint is not subjected to high axial force. The axial joint has a small axial clearance, whereby a small axial movement is allowed between the second end 1-2 of the first shaft and the first end of the second shaft. This small play takes into account the manufacturing precision of the shafts, the accuracy of the fitting, the heat movements, etc. After assembly, there is an axial play between the shaft faces slightly greater than the thickness of the 25 retaining rings. This way the shafts do not touch each other even through the cutting ring at the front surfaces. The object is that the shafts are in contact with each other only through the cylindrical or almost cylindrical side surfaces of the projection and recess, for example barrel-like.
    Said O-rings seal the lubrication housing enclosed in the joint area. 30 During assembly, Vaseline is reserved in the lubrication chamber to provide grease lubrication. A securing ring 12 is provided between the second end 1-2 of the first shaft 1 and the first end 2-1 of the second shaft 2 to secure the position of the switch 9 in the axial direction so that the switch 9 does not move axially to the O-rings and 35 opportunities for cutting. The securing ring 12 is an inner ring having an internally circumferential groove 13 in the manufacture of the coupling 9
    20185062 prh 23 -01- 2018 inside surface. The depth of the groove 13 extends slightly into the inner tooth but the profile of the groove 13 does not extend from the inside to the outside so as to extend to the bottom of the groove in the axial tooth.
    Fig. 3 shows, by way of example, an illustration of the teeth of the first 5 axes 1, the second axis 2 and the coupling 9. Figure 3 is not to scale and the parts shown may deviate from that shown. In the example of Figure 3, the second end 1-2 of the first shaft 1 comprises a first tooth 14, the first end 2-1 of the second shaft 2 comprises a second tooth 15 and the inner surface of the switch 9 comprises a third tooth 16. .
    The coupling to be coupled with the coupling has the advantage that it is balanced with respect to rotation, unlike, for example, a coupling arranged with a flat wedge, which is unbalanced with respect to rotation. A particular advantage of the coupling to be coupled with the coupling is that the coupling shafts can be rotated in the 15 rpm range. For example, an arrangement whereby the shafts are connected by means of a claw coupling and whose rotation at 4500 RPM has caused damage at axle diameters of 80 to 100 mm is known in the prior art. The stand-alone solution and the shaft connection successfully operate in the 9000 RPM range.
    Preferably, the coupling is fabricated by opening to provide internal axial engagement. When opening, a long tool is pulled through the coupling, which planes the necessary teeth, preferably with one stroke. The tool has a tooth shape, but the tool teeth are negative for the switch teeth. It is customary for a tooth to have a trapezoidal 25 tooth with 30 degree lateral angles.
    In the motor shaft and gear shaft shaft joints, it is previously known to provide flanges for bearings located near one end of the motor shaft and the first end of the gear shaft at both the engine and gear side. However, the embodiment 30 shown in Fig. 1 comprises only one flange 17 comprising a third bearing 8. Said flange 17 is provided only on the gear side near the first end 2-1 of the second shaft 2 and thus has no flange at the motor side. Alternatively, however, said flange could also be provided on the motor side, whereby the third bearing would be located near the second end of the first shaft 35 and accordingly the gear would not comprise the flange at all.
    20185062 prh 23 -01- 2018
    It is advantageous to remove the second flange, as this reduces the overall dimension of the shaft joint and saves space.
    It is also assumed in the first embodiment shown that the first shaft is the motor shaft and the second shaft is the gear shaft.
    Alternatively, the first shaft could be the gear shaft and the second shaft the motor shaft. The figures also show that the shaft connection is on the motor side. However, the junction may also be located, for example, on the gear side. In a further embodiment, the coupling is arranged to surround the junction between the first shaft and the second shaft. Alternatively, the clutch 10 may only partially surround said axes or be located between the axes.
    The most preferred bearing arrangement is one in which two bearings are located on the gear side and one on the electric motor. Thus, any error resulting from arranging the shaft coupling by coupling the shafts to the coupling is formed with respect to the coupling at the outer end of the electric motor shaft, i.e. the air gap 15. In this way, the effect of the error can be shifted to a point where it does not suffer much.
    An alternative way is to place two bearings in the electric motor, and one in the gear near the shaft connection, and any misalignment in the shaft moves to the gear further away from the shaft connection. Here, the gearbox shaft, at a farther distance 20 relative to the shaft joint, may have a gear wheel tooth contact, but not much deviation will occur because the small displacement (i.e. error) of that gear shaft is relatively far, i.e. at the shaft end.
    When the motor and gear are assembled together, the arrangement of the various diameters 25 is designed so that the assembly succeeds in stages as the axial parts are brought closer together. In axial direction, the coupling is fitted to either end of the shaft, the shafts are then brought together and, lastly, the flange connections of the electric motor and gear unit are connected.
    Typical materials for the shafts are selected such that the hardest material 30 is in the gear shaft and this may be, for example, carbon steel. Secondly, the hardest material is on the shaft of the electric motor and this can be for example of tempering steel, for example 42CrMo4. The coupling is made of mild steel such as structural steel.
    The shaft joint according to independent claim 1 is applied to at least 35 axes of diameter in the range of 10-30 mm. By means of this shaft connection, the two axles of the transmission can be connected to each other so that the effect of their mutual angular or radial error can be practically canceled. In the prior art solutions, for example in the size class where the shaft diameter is less than 20 mm, a radial error of less than 0.05 mm should be achieved. In the order of magnitude 0.1 mm, the radial error causes so much stress in the coupling joint that the transmission fails in a relatively short period of time. It will be obvious to a person skilled in the art that as technology advances, the basic idea of the invention can be implemented in many different ways. The shaft coupling and its embodiments are thus not limited to the examples described above, but may vary within the scope of the claims.
    权利要求:
    Claims (11)
    [1]
    The claims
    An axle joint comprising a first shaft (1) having a first end (1-1) and a second end (1-2), and having a first shaft (1-1) arranged in its vicinity.
    A bearing (3), and a second shaft (2) having a first end (2-1) and a second end (2-2), and a second bearing (4) being arranged in the vicinity of one end (2-2), and said first axis (1) and the second axis (2) being coaxially arranged such that one end (1-2) of the first axis (1) is opposite to the first end (2-1) of the second axis (2), characterized in that: the end surface of the second end (1-2) of the first shaft (1) has a recess (6) and a projection (7) protruding from the end surface of the first end (2-1) of the second shaft (2) and that said recess (6) receives said protrusion (7) such that the side surface of the projection (7) and the side surface of the recess (6) are facing each other, and that the side surface of the projection (7) or the side surface of the recess (6), or both of said opposing surfaces 2) axially shaped to be curved, and to support the first axis (1) and the second axis (2) In addition to said first bearing (3) and second bearing (4), the shaft coupling 20 comprises only one third bearing (8) disposed adjacent the junction of the first shaft (1) and the second shaft (2), and the shaft coupling further comprises a coupling (9). which receives the second end (1-2) of the first shaft (1) and the first end 25 (2-1) of the second shaft (2) and engages them non-rotatably to transmit a force to said first shaft (1) and the second shaft (2). between.
    [2]
    Shaft coupling according to claim 1, characterized in that said third bearing (8) is arranged in the vicinity of the second end (1-2) of the first shaft (1).
    30
    [3]
    Shaft coupling according to claim 1, characterized in that said third bearing (8) is arranged in the vicinity of the first end (2-1) of the second shaft (2).
    [4]
    Axle joint according to one of the preceding claims, characterized in that
    20185062 prh 23 -01- 2018 The outer surface of the second end (1-2) of the first shaft (1) is formed as a counterpart to the inner surface of the coupling (9) to prevent rotation between them, and the outer surface of the first end (2-1) of the second shaft (2)
    [5]
    5 on the inner surface of the coupling (9) to prevent them from rotating.
    Shaft coupling according to one of the preceding claims, characterized in that said coupling (9) at least partially surrounds the first shaft (1) and the second shaft (2).
    [6]
    Shaft joint according to one of the preceding claims, characterized in that the joint of the first shaft (1) and the second shaft (2) comprises a first O-ring (10) and a second O-ring (11) to ensure tightness of the shaft joint.
    [7]
    Axle joint according to Claim 6, characterized in that the first O-ring (10) is arranged near the second end (1-2) of the first shaft (1) and the second O-ring (11) is arranged at the first end of the second shaft (2). (2-1) in the vicinity.
    20
    [8]
    Shaft coupling according to one of the preceding claims, characterized in that the shaft coupling comprises a retaining ring (12) between the first shaft (1) and the second shaft (2).
    [9]
    Axle joint according to one of the preceding claims, characterized in that the first shaft (1) is a motor shaft and the second shaft (2) is a gear shaft.
    [10]
    Axle joint according to one of the preceding claims, characterized in that
    30 the first shaft (1) is a gear shaft and the second shaft (2) is a motor shaft.
    [11]
    Axle joint according to one of the preceding claims, characterized in that the second end (1-2) of the first shaft (1), the second shaft (2)
    The first end (2-1) and the inner surface of the coupling (9) comprise a tooth.
    类似技术:
    公开号 | 公开日 | 专利标题
    US4307584A|1981-12-29|Resilient coupling mechanism
    US5143477A|1992-09-01|Shaft connecting structure
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    RU2684697C2|2019-04-11|Peristaltic pump
    CN107091278A|2017-08-25|A kind of flexible thrust shaft coupling
    US4196597A|1980-04-08|Flexible shaft couplings with axially spaced diaphragms
    EP2730806B1|2019-06-19|Speed reducing device
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    JP5927262B2|2016-06-01|System and method for integrated torque transmission / rotary seal
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    GB2540860A|2017-02-01|Spragg and ratchet clutch couplings
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    US3462971A|1969-08-26|Flexible gear coupling
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    WO2021177281A1|2021-09-10|Connection structure for propeller shaft and propeller shaft having same
    KR100823941B1|2008-04-22|Reducer apparatus
    同族专利:
    公开号 | 公开日
    US20210066996A1|2021-03-04|
    KR20200110360A|2020-09-23|
    FI128065B|2019-08-30|
    BR112020014510A2|2020-12-08|
    CN111615592A|2020-09-01|
    EP3743633A1|2020-12-02|
    RU2749319C1|2021-06-08|
    WO2019145605A1|2019-08-01|
    EP3743633A4|2021-03-10|
    JP2021511472A|2021-05-06|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    GB708018A|1951-09-14|1954-04-28|Rolls Royce|Improvements in or relating to shaft couplings|
    GB770683A|1954-08-12|1957-03-20|Rolls Royce|Improvements in or relating to shaft couplings|
    DE1138686B|1959-10-16|1962-10-25|Holo Flite Internat Inc|Conveyor belt drive drum|
    DE2644414B2|1976-09-29|1979-07-19|Siemens Ag, 1000 Berlin Und 8000 Muenchen|Drive for an electric rail vehicle|
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    DE3339951C2|1983-11-04|1985-11-28|Bayerische Motoren Werke AG, 8000 München|Drive shaft for the wheels of a motor vehicle, in particular a passenger car|
    US5716279A|1995-11-21|1998-02-10|Itt Automotive Electrical Systems, Inc.|Apparatus and method for coupling an output shaft of a motor to a secondary shaft|
    DE10136240B4|2001-07-25|2006-12-07|Siemens Ag|bearing arrangement|
    CA2389483C|2002-06-06|2010-04-13|General Electric Canada Inc.|Dual shaft and rotating machine coupling|
    CN102252036A|2011-02-16|2011-11-23|吴实渊|Spatial flexible coupling|
    JP5728457B2|2012-10-31|2015-06-03|三木プーリ株式会社|Flexible shaft coupling and manufacturing method thereof|
    GB2521209A|2013-12-13|2015-06-17|Punk Couplings Ltd|Coupling|
    DE102014202279A1|2014-02-07|2015-08-13|Bühler Motor GmbH|Electromotive drive|
    DE102014223390A1|2014-11-17|2016-05-19|Volkswagen Aktiengesellschaft|Connecting arrangement between a first and a second shaft and vehicle with such a connection arrangement|CN112398268B|2020-11-25|2021-11-05|丽水学院|Inner rotor motor with adjustable output shaft angle and use method thereof|
    法律状态:
    2019-08-30| FG| Patent granted|Ref document number: 128065 Country of ref document: FI Kind code of ref document: B |
    优先权:
    申请号 | 申请日 | 专利标题
    FI20185062A|FI128065B|2018-01-23|2018-01-23|Shaft coupling|FI20185062A| FI128065B|2018-01-23|2018-01-23|Shaft coupling|
    PCT/FI2019/050050| WO2019145605A1|2018-01-23|2019-01-22|Shaft coupling|
    RU2020126692A| RU2749319C1|2018-01-23|2019-01-22|Shaft connection|
    KR1020207022463A| KR20200110360A|2018-01-23|2019-01-22|Shaft coupling|
    JP2020560602A| JP2021511472A|2018-01-23|2019-01-22|Shaft coupling|
    EP19743583.7A| EP3743633A4|2018-01-23|2019-01-22|Shaft coupling|
    CN201980008768.4A| CN111615592A|2018-01-23|2019-01-22|Coupling device|
    BR112020014510-6A| BR112020014510A2|2018-01-23|2019-01-22|AXLE COUPLING|
    US16/963,622| US20210066996A1|2018-01-23|2019-01-22|Shaft coupling|
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