• 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 invention relates to a bearing element (7) with at least one inner ring element (11) and at least one outer ring element (14), wherein between the inner ring element (11) and the outer ring element (14) a sliding bearing (17) is formed is formed by at least two sliding bearings (19). The plain bearings (19) have a sliding surface (24). When new of the sliding bearing (19), the sliding surface (24) of the sliding bearing (19) seen in cross-section at least a first portion (30) and a second portion (31), wherein a to the first portion (30) applied tangent (32 ) at a first angle (33) and a second part (31) applied to the tangent (34) at a second angle (35) to the central longitudinal axis (22), wherein the first angle (33) is different in size from the second Angle (35), wherein the first portion (30) and the second portion (31) are formed in cross section by straight lines which are interconnected by a transition radius (42).
    公开号:AT519288A1
    申请号:T50969/2016
    申请日:2016-10-21
    公开日:2018-05-15
    发明作者:
    申请人:Miba Gleitlager Austria Gmbh；
    IPC主号:
    专利说明:

    Summary
    The invention relates to a bearing element (7) with at least one inner ring element (11) and at least one outer ring element (14), a sliding bearing (17) being formed between the inner ring element (11) and the outer ring element (14) is formed by at least plain bearings (19). The sliding bearings (19) have a sliding surface (24) which interacts with a running surface (25) of the opposite ring element (11, 14). When the slide bearing (19) is in new condition, the slide surface (24) of the slide bearing (19) has at least a first section (30) and a second section (31) in cross section, with a tangent (32) applied to the first section (30) ) is arranged at a first angle (33) with respect to the central longitudinal axis (22) and a tangent (34) applied to the second section (31) is arranged at a second angle (35) with respect to the central longitudinal axis (22), the first angle (33) being different in size from the second angle (35).
    Fig. 2/28
    N2016 / 22900 AT-00
    The invention relates to a bearing element for storing a component.
    A bearing element for mounting the rotor hub of a wind turbine is known from AT 509 625 B1. The bearing element comprises an outer ring, an inner ring and a plurality of slide bearing pads, which are arranged between the outer ring and the inner ring. The bearing element is designed for a radial or an axial load and can only partially absorb a superimposed tilting moment.
    The object of the present invention was to overcome the disadvantages of the prior art and to provide a bearing element by means of which a component loaded with a radial force, an axial force and a tilting moment can be supported.
    This object is achieved by a device according to the claims.
    According to the invention, a bearing element, in particular rotor hub bearing, is designed for the bearing of a component to be loaded with a radial force, an axial force and a tilting moment. The bearing element comprises at least one inner ring element and at least one outer ring element, which in the unloaded state are arranged coaxially with respect to a central longitudinal axis, a slide bearing being formed between the inner ring element and the outer ring element, which is formed by at least two slide bearings arranged at an axial distance from one another is formed. The slide bearings are coupled on one receiving side to one of the ring elements and, opposite the receiving side, a sliding surface is formed, which with a running surface of the / 28
    N2016 / 22900-AT-00 opposite ring element interacts. When the slide bearing is new, the slide surface of the slide bearing has at least a first section and a second section in cross section, a tangent applied to the first section being arranged at a first angle with respect to the central longitudinal axis and a tangent applied to the second section in Reference to the central longitudinal axis is arranged at a second angle, wherein the first angle is different in size than the second angle.
    An advantage of the design of the bearing element according to the invention is that the first section can be designed such that an axial force or a radial force acting on the bearing element can be well absorbed and the second section of the slide bearing can be designed such that a tilting moment acting on the bearing element can be well received. In contrast to conventional plain bearings, the bearing element according to the invention does not cause a point load when the inner ring element is tilted relative to the outer ring element, but at least a linear contact of the sliding surface on the running surface can also be achieved when the inner ring element is tilted relative to the outer ring element become. As a result, the surface pressure can be minimized compared to conventional bearing elements, whereby the wear on the bearing elements can also be minimized.
    Furthermore, it may be expedient if a tangent, which is applied to the running surface of the ring element interacting with the slide bearing, is arranged at a third angle with respect to the central longitudinal axis, the third angle of the running surface being the same size as the first in the unloaded state Angle of the first section of the sliding surface. The advantage here is that a linear contact can be formed by this measure in a bearing element loaded with a radial force or axial force, which has no tilting between the inner ring element and the outer ring element and is not loaded with tilting moments.
    It can further be provided that the slide bearing is coupled to the outer ring element and the slide surface is formed on the inside of the slide bearing / 28
    N2016 / 22900-AT-00 and the tread is formed on the outside of the inner ring element. Such a design of the bearing element is advantageous if the outer ring element is designed as a rotating component and the inner ring element is designed as a stationary component, since this leads to reduced wear on the bearing element.
    In an alternative embodiment variant it can be provided that the sliding bearing is coupled to the inner ring element and the sliding surface is formed on the outside of the sliding bearing and the running surface is formed on the inside of the outer ring element. Such a design of the bearing element is advantageous if the inner ring element is designed as a rotating component and the outer ring element is designed as a stationary component, since this leads to reduced wear on the bearing element.
    In addition, it can be provided that at least one of the slide bearings is formed by slide bearing pads arranged distributed in the circumferential direction. The advantage here is that such plain bearing pads are easy to change or remove in the event of maintenance, without having to disassemble the entire bearing element.
    Also advantageous is a configuration according to which it can be provided that, in the case of a plain bearing with a sliding surface arranged on the inside, the first angle of the tangent applied to the first partial section is smaller in relation to the central longitudinal axis than the second angle of the applied to the second partial section Tangent in relation to the central longitudinal axis and that in the case of a plain bearing with a sliding surface arranged on the outside, the first angle of the tangent applied to the first section with respect to the central longitudinal axis is greater than the second angle of the tangent applied to the second section in relation to the central one longitudinal axis.
    According to a further development, it is possible that in the case of a bearing element loaded by a radial force or an axial force, the running surface of the ring element bears against the first partial section of the sliding surface of the slide bearing, in particular along a first contact line, and the ring element and the slide bearing around / 28
    N2016 / 22900-AT-00 the central longitudinal axis can be rotated relative to one another and that in the case of a bearing element loaded by a tilting moment, the running surface of the ring element rests on the second partial section of the sliding surface of the sliding bearing, in particular along a second contact line, and the ring element and the sliding bearing about the central longitudinal axis are relatively rotatable to each other. The advantage here is that each of the two sections is designed to take up a special load condition and the possible service life of the bearing element can thereby be increased.
    Furthermore, it can be expedient if the tangent of the second section is designed or has such an angle that, when the bearing element is not loaded, the tangent of the running surface around the center of the bearing element is congruent with the tangent of the second section. The advantage here is that when the bearing element is loaded with a tilting moment and therefore in the tilted state of the outer ring element relative to the inner ring element, the running surface and the sliding surface lie against one another at a second contact line.
    In addition, it can be provided that the first section and the second section are seen in cross section by straight lines which are connected to one another by a transition radius. It is advantageous here that the partial sections formed by straight lines in cross section can interact with corresponding counter surfaces also formed in straight lines seen in cross section, and a linear contact is formed in the process. The transition radius is preferably chosen to be as small as possible. The transition radius can preferably be approximately zero and the straight lines therefore intersect directly with one another and form a tip.
    It can further be provided that an opening angle between the tangent applied to the first section and the tangent applied to the second section is between 175 ° and 179.99 °, in particular between 178 ° and 179.99 °, preferably between 179 ° and 179, 99 °. The advantage here is that correspondingly small bearing clearances can be achieved by realizing such an opening angle.
    / 28
    N2016 / 22900 AT-00
    Furthermore, it can be provided that a wind turbine is designed with a rotor hub and a nacelle, the rotor hub being mounted on the nacelle by means of the described bearing element.
    A tangent can be applied to a curved curve, such as a circle, or to a straight line. In the special case of a straight line, the tangent to the straight line lies on the straight line over the entire length.
    The bearing element has the geometric design when new. This is particularly advantageous because it prevents excessive wear of the plain bearing.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    Each show in a highly simplified, schematic representation:
    Figure 1 shows an embodiment of a wind turbine.
    2 shows a cross-sectional illustration of a first exemplary embodiment of a bearing element in the unloaded state;
    3 shows a cross-sectional illustration of the first exemplary embodiment of the bearing element in the state loaded with a tilting moment;
    4 shows a schematic detailed illustration of the first exemplary embodiment of the bearing element in the unloaded state;
    5 shows a schematic detailed illustration of the first exemplary embodiment of the bearing element in the state loaded with an axial force and / or a radial force;
    6 shows a schematic detailed illustration of the first exemplary embodiment of the bearing element in the state loaded with a tilting moment;
    7 shows a schematic detailed illustration of a second exemplary embodiment of the bearing element in the unloaded state;
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    N2016 / 22900 AT-00
    8 shows a schematic detailed illustration of the second exemplary embodiment of the bearing element in the state loaded with an axial force and / or a radial force;
    9 shows a schematic detailed illustration of the second exemplary embodiment of the bearing element in the state loaded with a tilting moment.
    In the introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, and the disclosures contained in the entire description can be applied analogously to the same parts with the same reference numerals or the same component names. The location information selected in the description, e.g. above, below, to the side, etc., referring to the figure described and illustrated immediately, and if the position is changed, these are to be applied accordingly to the new position.
    Fig. 1 shows a schematic representation of a wind turbine 1 for generating electrical energy from wind energy. The wind turbine 1 comprises a nacelle 2 which is rotatably received on a tower 3. The electrical components, such as the generator of the wind turbine 1, are arranged in the nacelle 2.
    Furthermore, a rotor 4 is formed, which has a rotor hub 5 with rotor blades 6 arranged thereon. In particular, it is provided that the rotor hub 5 is rotatably received on the nacelle 2 by means of a bearing element 7.
    It is particularly advantageous if the bearing element 7 is designed in accordance with the designs described in this document, since especially when only one bearing element 7 is used to mount the rotor hub 5 on the nacelle 2, both a radial force 8 and an axial force 9 and a tilting moment 10 must be taken up by the bearing element 7. The axial force 9 results from the force of the wind. The radial force 8 corresponds to the weight of the rotor 4 and acts on the center of gravity of the rotor 4. Since the center of gravity of the rotor 4 lies outside the bearing element 7, the / 28
    N2016 / 22900 AT-00
    Radial force 8 caused the tilting moment 10. The tilting moment 10 can also be caused by an uneven load on the rotor blades 6.
    As an alternative to using the bearing element 7 in a wind power plant 1, it is also conceivable that a bearing element 7 designed in this way is used, for example, on a slewing ring of an excavator or in another application where both a radial force 8 and / or an axial force 9 and a tilting moment 10 act on the bearing element 7.
    The bearing elements 7 according to the invention can for example have a diameter between 0.5 m and 5 m. Of course, it is also conceivable that the bearing elements 7 are smaller or larger.
    2 shows a first exemplary embodiment of the bearing element 7 in an unloaded state. FIG. 3 shows the first exemplary embodiment of the bearing element 7 from FIG. 2 in a state loaded with a tilting moment 10, the same reference numerals or component designations being used for the same parts as in the previous FIG. 2. In order to avoid unnecessary repetitions, the bearing element 7 is described on the basis of an overview of FIGS. 2 and 3.
    The bearing element 7 comprises at least one inner ring element 11, which has an inner side 12 and an outer side 13. Furthermore, an outer ring element 14 is provided, which has an inner side 15 and an outer side 16. In addition, a slide bearing 17 is formed between the inner ring element 11 and the outer ring element 14, which comprises at least two slide bearings 19 spaced apart at an axial distance 18. The two slide bearings 19 each have an inside 20 and an outside 21.
    2, the bearing element 7 is shown in an unloaded state. In this case, the unloaded state is defined as the state in which no forces and therefore no gravitational forces act on the bearing element 7. This state is fictional and is therefore only for illustration / 28
    N2016 / 22900-AT-00 of the components or the function of the bearing element 7 shown. As can be seen from FIG. 2, in the unloaded state of the bearing element 7, the inner ring element 11 and the outer ring element 14 and the slide bearings 19 are arranged concentrically with respect to a common central longitudinal axis 22.
    In the first exemplary embodiment of the bearing element 7, as shown in FIGS. 2 to, the slide bearings 19 are coupled to the outer ring element 14. The side of the slide bearing 19, which is coupled to the outer ring element 14, is referred to in the present exemplary embodiment as the receiving side 23 of the slide bearing. There is no relative movement between the slide bearing 19 and the outer ring element 14 on the receiving side 23 of the slide bearing 19. Such coupling of the slide bearing 19 to the outer ring element 14 can be achieved, for example, by measures such as those already described in AT 509 625 B1.
    Furthermore, it is also conceivable for the slide bearing 19 to be accommodated in the outer ring element 14, for example by means of an adhesive connection. In yet another exemplary embodiment, it is also possible for the sliding bearing 19 to be received in the outer ring element 14 in a form-fitting manner, for example.
    The slide bearing 19 can be divided into several ring segments distributed over the circumference. Furthermore, it is also conceivable that the slide bearing 19 is designed as a single circumferential ring. Such a circumferential ring can, for example, be inserted into the outer ring element 14, wherein a frictional connection prevents the sliding bearing 19 from rotating relative to the outer ring element 14.
    Opposite the receiving side 23 of the sliding bearing 19, a sliding surface 24 is formed, which cooperates with a running surface 25 of the inner ring element 11. In the first exemplary embodiment, the outer side 13 of the inner ring element 11 is designed as a running surface 25.
    / 28
    N2016 / 22900 AT-00
    In particular, the first exemplary embodiment provides that the slide bearing 19 rotates relative to the inner ring element 11 and that a sliding movement between the sliding surface 24 of the slide bearing 19 and the running surface 25 of the inner ring element 11 is made possible. The function of the bearing element 7 can thereby be realized. The exact function or the exact relationships of the bearing element 7 are shown in detail in FIGS. 4 to 6 or serve these representations to supplement the understanding of the first exemplary embodiment of the bearing element 7.
    As shown in FIG. 2, a bearing clearance 26 is formed between the inner ring element 11 and the slide bearing 19.
    At this point it should be mentioned that both in FIGS. 2 and 3 and also in FIGS. 4 to 6 and 7 to 9, the bearing play 26 is exaggerated for illustration. In particular in FIGS. 4 to 6 and 7 to 9, the geometry of the slide bearing is also shown in a greatly exaggerated manner in order to be able to clearly illustrate the function and the technical effects.
    As can be seen from FIG. 2, it can be provided that two inner ring elements 11 are formed, which are arranged at a distance 27 from one another. The outer sides 13 of the inner ring elements 11 are each conical and face one another. The bearing clearance 26 can be adjusted by the distance 27 of the two inner ring elements 11 from one another.
    The tread 25 is a surface which is rotationally symmetrical with respect to the central longitudinal axis 22 and which can have the special shape of a truncated cone. Seen in cross section of the bearing element 7, as shown in Fig. 2, the tread 25 forms a straight line. If a tangent 28 is placed on the tread 25, this tangent 28 is formed at an angle 29 with respect to the central longitudinal axis 22.
    As can be seen from FIG. 2 and particularly well in the exaggerated representation according to FIG. 4, it is provided that the sliding bearing 19 has a first partial section 30 and a second partial section 31 on its sliding surface 24.
    / 28
    N2016 / 22900 AT-00
    A tangent 32 applied to the first partial section 30 is arranged at an angle 33 to the central longitudinal axis 22. A tangent 34 applied to the second section 31 is arranged at an angle 35 to the central longitudinal axis 22.
    In particular, it is provided that the angle 35 of the second section 32 and the angle 33 of the first section 30 are of different sizes. Furthermore, it is provided that the angle 29 of the tread 25 and the angle 33 of the first section 30 are of the same size and thus the tangent 28 of the tread 25 and the tangent 32 of the first section 30 are parallel to one another in the unloaded state of the bearing element 7. Viewed in the three-dimensional representation, the running surface 25 and the first partial section 30 therefore have a lateral surface of a truncated cone with the same opening angle.
    If, as shown in FIG. 5, the bearing element 7 is loaded with an axial force 9 and / or a radial force 8, the first subsection 30 of the sliding surface 24 of the sliding bearing 19 and the running surface 25 of the inner ring element 11 come to a first contact line 36 to care about each other. The sliding surface 24 of the sliding bearing 19 and the running surface 25 of the inner ring element 11 therefore touch each other at the first contact line 36, since the radial force 8 or the axial force 9 cause the two components to move parallel to one another. The parallel shift is of course in the hundredth to tenth of a millimeter range and is depicted as exaggerated.
    However, if a tilting moment 10 is introduced into the bearing element 7, as shown in FIGS. 3 and 6, the outer ring element 14 is tilted relative to the inner ring element 11, as a result of which the second section 31 of the sliding surface 24 of the sliding bearing 19 on the Tread 25 of the inner ring member 11 abuts a second contact line 37.
    3, the two slide bearings 19 lie diagonally opposite one another on the inner ring elements 11. In the case of this tilting described, the outer ring element / 28 is twisted in particular
    N2016 / 22900-AT-00 relative to the inner ring element 11 with respect to a pivot point 38, which lies at the intersection between the central longitudinal axis 22 and a longitudinal central axis 39.
    It is, of course, ideal if, after the tilting of the outer ring element 14, the tangent 28 of the running surface 25 and the tangent 34 of the second section 31 of the sliding surface 24 of the sliding bearing 19 lie congruently on one another. This results in a linear contact between the sliding surface 24 and the running surface 25 even when the bearing element 7 is loaded by a tilting moment 10, as a result of which the surface pressure and thus the wear on the sliding surface 24 can be reduced.
    The congruence of the tangent 24 of the second section 31 and the tangent 28 of the tread 25 after tilting can be achieved in that the tangent 28 is taken to the tread 25 in the construction of the plain bearing 19 in the unloaded state according to FIG The pivot point 38 is rotated by a certain angle so that it forms the tangent 34 of the second section 31 and intersects with the tangent 32 of the first section 30 approximately in the middle of the slide bearing 19. The size of this angle, by which the tangent 28 to the running surface 25 is rotated in the construction of the slide bearing 19, then determines the maximum deflection angle 40.
    An opening angle 41 is formed between the tangent 34 of the second section 31 and the tangent 32 of the first section 30, which corresponds to an angle of 180 ° minus the maximum deflection angle 40. With a correspondingly small bearing play 26, which moves in the hundredth of a millimeter to a tenth of a millimeter range, the maximum deflection angle 40 is accordingly also located in the hundredth to tenth of a degree range.
    Furthermore, it can be provided that a transition radius 42 is formed between the first section 30 and the second section 31, which is production-related. The transition radius 42 is preferably as small as possible, so that the first contact line 36 and the second contact line 37 are as possible / 28
    N2016 / 22900-AT-00 are long and thus the lowest possible surface pressure occurs between the sliding surface 24 of the sliding bearing 19 and the running surface 25 of the inner ring element 11. In other words, in the ideal case, the first section 30 and the second section 31 are connected to one another directly or, if possible, without a transition radius 42.
    FIGS. 7 to 9 show a further and possibly independent embodiment of the bearing element 7 in a second exemplary embodiment, the same reference numbers or component designations as in the previous FIGS. 2 to 6 being used for the same parts. In order to avoid unnecessary repetitions, reference is made to the detailed description in the preceding FIGS. 2 to 6.
    In the second exemplary embodiment of the bearing element 7 it can be provided that the slide bearing 19 is coupled to the inner ring element 11 and a sliding movement takes place between the slide bearing 19 and the outer ring element 14.
    As can be seen from the second exemplary embodiment, the slide bearing 19 can be coupled to the inner ring element 11 and thus the receiving side 23 of the slide bearing 19 can be formed on the inside 20 thereof. Correspondingly, in this exemplary embodiment, the sliding surface 24 of the sliding bearing 19 is formed on the outer side 21 thereof and cooperate with the inner side 15 of the outer ring element 14, which is designed as a running surface 25 in this exemplary embodiment.
    The relationships between the first partial section 30 and the second partial section 31 of the sliding surface 24 of the sliding bearing 19 and the cooperating running surface 25 of the outer ring element 14 behave analogously to the first exemplary embodiment already described in FIGS. 2 to 6. For the sake of brevity, the second exemplary embodiment is therefore not described in detail separately, but the function can be clearly seen by the person skilled in the art on the basis of the description of the first exemplary embodiment described in FIGS. 2 to 6 or on the basis of FIGS. 7 to 9.
    / 28
    N2016 / 22900 AT-00
    Such a second embodiment of the bearing element 7 with an inner slide bearing 19, as shown in FIGS. 7 to 9, is preferably used when the outer ring element 14 is stationary and the inner ring element 11 together with the slide bearing element 19 relative to outer ring member 14 is rotatable.
    The exemplary embodiments show possible design variants, it being noted at this point that the invention is not limited to the specially illustrated design variants of the same, but rather also various combinations of the individual design variants with one another are possible and this variation possibility is based on the teaching of technical action through the present invention Ability of the specialist working in this technical field.
    The scope of protection is determined by the claims. However, the description and drawings are to be used to interpret the claims. Individual features or combinations of features from the different exemplary embodiments shown and described can represent independent inventive solutions. The object on which the independent inventive solutions are based can be found in the description.
    All information on value ranges in the objective description is to be understood so that it includes any and all sub-areas, e.g. the information 1 to 10 is to be understood so that all sub-areas, starting from the lower limit 1 and the upper limit 10, are included, i.e. all sections start with a lower limit of 1 or greater and end with an upper limit of 10 or less, e.g. 1 to 1.7, or 3.2 to 8.1, or 5.5 to 10.
    For the sake of order, it should finally be pointed out that, for a better understanding of the structure, elements have sometimes been shown to scale and / or enlarged and / or reduced.
    / 28
    N2016 / 22900 AT-00
    LIST OF REFERENCE NUMBERS
    1 Wind turbine 27 Distance inner ring elements 2 gondola 28 Tangent tread 3 tower 29 Tread angle 4 rotor 30 first section 5 rotor hub 31 second section 6 rotor blade 32 Tangent first section 7 bearing element 33 First section angle 8th radial force 34 Tangent second section 9 axial force 35 Second section angle 10 overturning moment 36 first contact line 11 inner ring element 37 second contact line 12 Inside inner ring 38 pivot pointment 39 Longitudinal central axis 13 Outside inner ring 40 maximum deflection anglement 41 opening angle 14 outer ring element 42 Transition radius 15 Inside outer ring ment 16 Outside outer ring ment 17 plain bearing 18 axial distance 19 bearings 20 Inside slide bearing 21 Outside slide bearing 22 central longitudinal axis 23 Placement side slide bearing 24 Slide bearing 25 tread 26 bearing clearance
    / 28
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    权利要求:
    Claims (10)
    [1]
    claims
    1. Bearing element (7), in particular rotor hub bearing, for mounting a component to be loaded with a radial force (8) and / or an axial force (9) and a tilting moment (10), with at least one inner ring element (11) and at least one outer one Ring element (14), which are arranged coaxially with respect to a central longitudinal axis (22) to each other in the unloaded state, wherein a sliding bearing (17) is formed between the inner ring element (11) and the outer ring element (14), which by at least two in the axial A spacing (18) from one another is formed, the sliding bearing (19) being formed, the sliding bearing (19) being coupled on one receiving side (23) to one of the ring elements (11, 14) and a sliding surface (24) being formed opposite the receiving side (23) , which cooperates with a running surface (25) of the opposite ring element (11, 14), characterized in that, when the plain bearing (19) is new, the sliding surface (24) of the plain bearing ( 19) seen in cross section has at least a first section (30) and a second section (31), a tangent (32) applied to the first section (30) with respect to the central longitudinal axis (22) at a first angle (33) is arranged and a tangent (34) applied to the second section (31) is arranged at a second angle (35) with respect to the central longitudinal axis (22), the first angle (33) being different in size from the second angle (35 ).
    [2]
    2. Bearing element according to claim 1, characterized in that a tangent (28) which is applied to the running surface (25) of the ring element (11, 14) cooperating with the slide bearing (19) in relation to the central longitudinal axis (22) in a third angle (29) is arranged, the third angle (29) of the tread (25) being equal to the first angle (33) of the first section (30) of the sliding surface (24) in the unloaded state.
    [3]
    3. Bearing element according to claim 1 or 2, characterized in that the slide bearing (19) is coupled to the outer ring element (14) and the slide
    16/28
    N2016 / 22900-AT-00 surface (24) is formed on the inside (20) of the slide bearing (19) and the running surface (25) is formed on the outside (13) of the inner ring element (11).
    [4]
    4. Bearing element according to one of the preceding claims, characterized in that at least one of the slide bearings (19) is formed by slide bearing pads arranged distributed in the circumferential direction.
    [5]
    5. Bearing element according to one of the preceding claims, characterized in that in the case of a plain bearing (19) with a sliding surface (24) arranged on the inside (20), the first angle (33) of the tangent (32) applied to the first partial section (30) ) in relation to the central longitudinal axis (22) is smaller than the second angle (35) of the tangent (34) applied to the second section (31) in relation to the central longitudinal axis (22) and that in the case of a plain bearing (19) with a the sliding surface (24) arranged on the outside (21), the first angle (33) of the tangent (32) applied to the first section (30) with respect to the central longitudinal axis (22) is greater than the second angle (35) that to the second Section (31) created tangent (34) with respect to the central longitudinal axis (22).
    [6]
    6. Bearing element according to one of the preceding claims, characterized in that in the case of a bearing element (7) loaded by a radial force (8) or an axial force (9), the tread (25) of the ring element (11, 14) on the first section (30) the sliding surface (24) of the sliding bearing (19), in particular along a first contact line (36), and the ring element (11, 14) and the sliding bearing (19) can be rotated relative to one another about the central longitudinal axis (22), and that in one a tilting moment (10) loads bearing element (7), the tread (25) of the ring element (11, 14) on the second section (31) of the sliding surface (24) of the sliding bearing (19), in particular along a second contact line (37), and the ring element (11, 14) and the slide bearing (19) can be rotated relative to one another about the central longitudinal axis (22).
    17/28
    N2016 / 22900 AT-00
    [7]
    7. Bearing element according to one of the preceding claims, characterized in that the tangent (34) of the second section (31) is formed or has such an angle (35) that the tangent (28) in the unloaded state of the bearing element (7) the tread (25) rotated around the center of the bearing element (7) is congruent with the tangent (34) of the second section (31).
    [8]
    8. Bearing element according to one of the preceding claims, characterized in that the first partial section (30) and the second partial section (31), seen in cross section, is formed by straight lines which are connected to one another by a transition radius (42).
    [9]
    9. Bearing element according to one of the preceding claims, characterized in that an opening angle (41) between the tangent (32) applied to the first subsection (30) and the tangent (34) applied to the second subsection (31) is between 175 ° and 179.99 °, in particular between 178 ° and 179.99 °, preferably between 179 ° and 179.99 °.
    [10]
    10. Wind power plant (1) with a rotor hub (5) and a nacelle (2), the rotor hub (5) being mounted on the nacelle (2) by means of a bearing element (7), characterized in that the bearing element (7) follows one of the preceding claims is formed.
    18/28
    N2016 / 22900 AT-00
    Miba Gleitlager Austria GmbH
    19/28
    Miba Gleitlager Austria GmbH
    20/28
    39th
    21/28 m
    Miba Gleitlager Austria GmbH
    22/28
    C7>
    ι_η
    Miba Gleitlager Austria GmbH
    23/28 Austrian
    Patent Office
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    WO2018050736A1|2018-03-22|Method for ascertaining operating loads and for designing tower structures, tower structure, and wind turbine
    DE102013215244A1|2015-02-05|Safety bearing for catching a rotor shaft of a machine and machine
    同族专利:
    公开号 | 公开日
    EP3529508A1|2019-08-28|
    DK3529508T3|2020-10-19|
    JP2019534428A|2019-11-28|
    JP6970195B2|2021-11-24|
    KR20190067883A|2019-06-17|
    WO2018071941A1|2018-04-26|
    US10598214B2|2020-03-24|
    US20190234457A1|2019-08-01|
    CN109790866B|2020-12-22|
    ES2846974T3|2021-07-30|
    CN109790866A|2019-05-21|
    AT519288B1|2018-07-15|
    EP3529508B1|2020-08-12|
    引用文献:
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    EP2921728A1|2014-03-20|2015-09-23|Areva Wind GmbH|Hybrid shaft bearing with a hydrodynamic bearing and a rolling bearing, wind generator comprising a hybrid shaft bearing, use of the hybrid shaft bearing and method of operating the hybrid shaft bearing|
    ES2765403T3|2015-05-07|2020-06-09|Flender Gmbh|Planetary transmission mechanism|
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    DK3514397T3|2018-01-18|2020-10-26|Siemens Gamesa Renewable Energy As|Rental equipment and wind turbine|AT522155B1|2019-03-07|2020-09-15|Miba Gleitlager Austria Gmbh|Plain bearing|
    AT522476B1|2019-05-21|2020-11-15|Miba Gleitlager Austria Gmbh|Gondola for a wind turbine|
    DE102020112765A1|2020-05-12|2021-11-18|Miba Gleitlager Austria Gmbh|Main rotor bearing of a nacelle for a wind turbine|
    DE102020116588A1|2020-06-24|2021-12-30|Schaeffler Technologies AG & Co. KG|Angular contact sliding bearing|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50969/2016A|AT519288B1|2016-10-21|2016-10-21|bearing element|ATA50969/2016A| AT519288B1|2016-10-21|2016-10-21|bearing element|
    PCT/AT2017/060273| WO2018071941A1|2016-10-21|2017-10-19|Bearing element|
    EP17811827.9A| EP3529508B1|2016-10-21|2017-10-19|Bearing element|
    KR1020197014327A| KR20190067883A|2016-10-21|2017-10-19|Bearing member|
    ES17811827T| ES2846974T3|2016-10-21|2017-10-19|Bearing element|
    DK17811827.9T| DK3529508T3|2016-10-21|2017-10-19|Rental element|
    JP2019521151A| JP6970195B2|2016-10-21|2017-10-19|Bearing member|
    US16/334,390| US10598214B2|2016-10-21|2017-10-19|Bearing element|
    CN201780059498.0A| CN109790866B|2016-10-21|2017-10-19|Supporting element|
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