CN113312716B - Checking method of turntable bearing - Google Patents

Checking method of turntable bearing Download PDF

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CN113312716B
CN113312716B CN202110529725.XA CN202110529725A CN113312716B CN 113312716 B CN113312716 B CN 113312716B CN 202110529725 A CN202110529725 A CN 202110529725A CN 113312716 B CN113312716 B CN 113312716B
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pin shaft
stress
ring
checking
turntable bearing
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CN113312716A (en
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王高峰
刘攀
李铮
李培培
楚德娜
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Luoyang Bearing Research Institute Co Ltd
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Luoyang Bearing Research Institute Co Ltd
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    • G06—COMPUTING; CALCULATING OR COUNTING
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    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
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    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
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Abstract

The utility model relates to a transferThe checking method of the disc bearing comprises the following steps: 1) Calculating the maximum stress F of a single pin caused by the overturning moment 1 Taking the pin shaft with the largest stress as a checking object, and calculating the stress F of the pin shaft caused by the axial force 2 Wherein F is 1 And F 2 The direction is the same, the resultant force born by the pin shaft is F max ＝F 1 +F 2 The method comprises the steps of carrying out a first treatment on the surface of the 2) Checking the shearing stress tau born by the pin shaft by the resultant force max Bending stress delta max Checking whether the compressive stress delta born by the seat ring at the pin shaft is smaller than the corresponding allowable stress f Compressive stress delta borne by the support ring r Whether less than the corresponding allowable stress. The turntable bearing provided by the utility model selects the pin shaft with the largest bearing force as a checking object, and the checking result is more accurate.

Description

Checking method of turntable bearing
Technical Field
The utility model relates to a checking method of a turntable bearing.
Background
Along with the increasing installation requirements of domestic high-power wind generators, large petrochemical equipment and nuclear power equipment, the requirements on kiloton-level crawler cranes are also more and more vigorous. Because the volume and the weight of the kiloton crawler crane are large, the complete machine transfer transportation of the kiloton crawler crane is difficult. Compared with the traditional mode that the turntable bearing is connected and fixed with the crane through bolts, the multi-row cylindrical roller turntable bearing is designed into a quick-dismantling structure, so that split transition transportation after the large crane is disassembled is realized, and the novel technical direction is changed.
The structure of the prior art turntable bearing is shown in Chinese patent publication No. CN212744706U and fig. 1, the turntable bearing comprises a middle ring 1 and a seat ring 2 arranged on the middle ring 1 through a main thrust roller retainer 13 and a main thrust roller 3, an outer gear ring 4 is arranged on the outer side of the middle ring 1 through a secondary thrust roller retainer 10 and a secondary thrust roller 9, a first inner ring 5 and a second inner ring 6 are arranged on the inner side of the middle ring 1 through the secondary thrust roller retainer 10 and the secondary thrust roller 9, the outer gear ring 4 is connected with the seat ring 2 through bolts 8, and the first inner ring 5, the second inner ring 6 and the seat ring 2 are connected through bolts 8. And radial rollers 11 and isolating blocks 12 are also arranged among the first inner ring 5, the second inner ring 6 and the middle ring 1. A support ring 14 is mounted on the seat 2, the support ring 14 being intended to be mechanically connected to the base. The seat ring 2 and the supporting ring 14 are connected through a pin shaft 7 extending along the radial direction of the turntable bearing, and a plurality of pin shafts 7 are uniformly distributed along the circumferential direction of the turntable bearing. When the pin shaft 7 is required to be disassembled and assembled, the pin shaft 7 is canceled, so that the upper and lower split can be realized. Wherein the seat ring 2, the support ring 14 and the pins 7 together form a quick release structure.
When the kiloton crawler crane works, the turntable bearing roller way and the quick-dismantling structure in the turntable bearing roller way bear larger axial force and overturning moment, and at present, the checking calculation of the turntable bearing roller way in China is mature, but no method for checking the quick-dismantling structure exists.
Disclosure of Invention
The utility model aims to provide a checking method of a turntable bearing, which is used for checking and calculating a quick-dismantling structure in the turntable bearing.
In order to achieve the above purpose, the technical scheme of the checking method of the turntable bearing provided by the utility model is as follows: a checking method of a turntable bearing is characterized in that: the method comprises the following steps:
1) Calculating the maximum stress F1 of a single pin shaft caused by the overturning moment, taking the pin shaft with the maximum stress as a checking object, and calculating the stress F of the pin shaft caused by the axial force 2 Wherein F is 1 And F 2 The direction is the same, the resultant force born by the pin shaft is F max ＝F 1 +F 2 ；
2) Checking the shearing stress tau born by the pin shaft by the resultant force max Bending stress delta max Checking whether the compressive stress delta born by the seat ring at the pin shaft is smaller than the corresponding allowable stress f Compressive stress delta borne by the support ring r Whether less than the corresponding allowable stress.
The beneficial effects are that: when the turntable bearing bears the overturning moment, the acting forces borne by the pin shafts and caused by the overturning moment are different, the maximum force borne by a single pin shaft is calculated firstly, then the pin shaft corresponding to the maximum force is used as a checking object, the acting forces caused by the axial force in the same direction are overlapped, and as long as all the parameters of the pin shaft meet the design requirements, other pin shafts meet the design requirements. The turntable bearing provided by the utility model selects the pin shaft with the largest bearing force as a checking object, and the checking result is more accurate. Through checking main round pin axle, seat circle and the backup ring in the quick detach structure, can judge whether quick detach knot can satisfy the operation requirement.
Preferably, in step 1), the process comprises,
Figure BDA0003066907990000021
wherein: m represents the bending moment born by the pin shaft;
w represents the flexural modulus of the cross section,
Figure BDA0003066907990000022
wherein F is Z For applying axial force to the turntable bearing, M Z In order to apply overturning moment to the turntable bearing, n is the number of pin shafts, and d is the effective area of the pin shafts.
Preferably, the seat ring and the supporting ring of the turntable bearing comprise two connecting rings, the two connecting rings of the supporting ring are inserted between the two connecting rings of the seat ring, each connecting ring is provided with a pin shaft perforation, and the pin shaft perforation is used for the pin shaft to pass through in an adapting way;
wherein the bending moment born by the pin roll
Figure BDA0003066907990000023
Compressive stress to which the seat ring is subjected>
Figure BDA0003066907990000024
Support ring bearing
Is subjected to compressive stress
Figure BDA0003066907990000025
Wherein T is f T is the thickness of the connecting ring of the race in the radial direction of the turntable bearing r The thickness of the connecting ring which is the supporting ring along the radial direction of the turntable bearing.
Preferably, according to the shear stress τ max Bending stress delta max Compressive stress delta of seat ring f Compressive stress delta of support ring r Calculating a safety coefficient;
wherein the shear safety coefficient of the pin shaft is
Figure BDA0003066907990000031
Pin roll bending-resistant safety coefficient ∈>
Figure BDA0003066907990000032
Anti-crushing safety coefficient of seat ring>
Figure BDA0003066907990000033
The anti-crushing safety coefficient of the supporting ring>
Figure BDA0003066907990000034
And comparing and judging the calculated safety coefficient with the safety coefficient required by the design to obtain a final checking result. After the safety coefficient is calculated, the safety coefficient can be used for judging whether the design of the quick-dismantling structure is reasonable or not, and can reflect the safety margin of the quick-dismantling structure.
Drawings
FIG. 1 is a schematic view of a prior art turntable bearing;
FIG. 2 is a schematic diagram showing main parameters of a quick release structure in an embodiment of a method for checking a turntable bearing according to the present utility model;
reference numerals illustrate:
1. a middle ring; 2. a seat ring; 3. a main thrust roller; 4. an outer ring gear; 5. a first inner ring; 6. a second inner ring; 7. a pin shaft; 8. a bolt; 9. a secondary thrust roller; 10. a secondary thrust roller cage; 11. radial rollers; 12. a spacer block; 13. a main thrust roller cage; 14. and a support ring.
Detailed Description
The present utility model will be described in further detail with reference to the drawings and examples, in order to make the objects, technical solutions and advantages of the present utility model more apparent. It should be understood that the particular embodiments described herein are illustrative only and are not intended to limit the utility model, i.e., the embodiments described are merely some, but not all, of the embodiments of the utility model. The components of the embodiments of the present utility model generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the utility model, as presented in the figures, is not intended to limit the scope of the utility model, as claimed, but is merely representative of selected embodiments of the utility model. All other embodiments, which can be made by a person skilled in the art without making any inventive effort, are intended to be within the scope of the present utility model.
It is noted that relational terms such as "first" and "second", and the like, are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" is not intended to exclude processes, methods comprising such element.
In the description of the present utility model, the terms "mounted," "connected," "coupled," and "connected," as may be used broadly, and may be connected, for example, fixedly, detachably, or integrally, unless otherwise specifically defined and limited; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present utility model can be understood by those skilled in the art in specific cases.
In the description of the present utility model, it should be noted that, unless explicitly stated and limited otherwise, the term "provided" may be interpreted broadly, and for example, an object "provided" may be a part of a body, may be separately disposed from the body, and may be connected to the body, where the connection may be a detachable connection or an undetachable connection. The specific meaning of the above terms in the present utility model can be understood by those skilled in the art in specific cases.
The present utility model is described in further detail below with reference to examples.
The utility model provides a specific embodiment of a checking method of a turntable bearing:
as shown in fig. 2, the checking method of the turntable bearing is used for checking the pin shaft 7, the seat ring 2 and the supporting ring 14 in the quick-dismantling structure, and specific checking indexes are bending stress and shearing stress of the pin shaft 7 and compressive stress of the seat ring 2 and the supporting ring 14. In this embodiment, the seat ring 2 and the supporting ring 14 each include two connection rings, the two connection rings of the supporting ring 14 are inserted into the two connection rings of the seat ring 2, pin shaft holes are formed in the four connection rings, and the pin shaft 7 is penetrated through the four pin shaft holes in an adapting manner, so that the seat ring 2 and the supporting ring 14 are assembled together.
The checking method of the turntable bearing comprises the following steps:
step 1: and determining parameters required by checking calculation. Axial force F applied to the turntable bearing z =30000 kN, overturning moment M z =50000 kN; the number n=30 of the pin shafts 7, and the effective diameter d=110 mm of the pin shafts 7, wherein the effective diameter refers to the diameter of the matched position of the pin shafts 7, the supporting ring 14 and the seat ring 2. Inner diameter d=2600 mm of race 2, thickness T of the connecting ring in race 2 f Thickness T of the connection ring in support ring 14 =50 mm r Material of pin 7 is 42CrMo, =50 mm, allowable shear stress [ τ ] of pin 7]Allowable bending stress [ delta ] of pin 7 of =450 MPa]500MPa, the material of the support ring 14 is42CrMo, allowable stress [ delta ] of support ring 14 r ]650MPa, 42CrMo as material for the race 2, allowable stress [ delta ] of the support ring 14 f ]＝650MPa。
Step 2: calculating the overturning moment M Z Maximum stress of single pin
Figure BDA0003066907990000051
Step 3: calculating the axial force F z The stress of the single pin shaft
Figure BDA0003066907990000052
Step 4: calculating the maximum resultant force F born by the pin shaft with the maximum stress max ＝F 1 +F 2 ＝3564kN；
Step 5: calculating the shearing stress of the pin shaft 7 with the largest stress
Figure BDA0003066907990000053
Wherein A represents the cross-sectional area of the pin 7;
step 6: calculating the maximum bending stress of the pin shaft 7 with the maximum stress
Figure BDA0003066907990000054
Wherein M represents the bending moment born by the pin 7, < ->
Figure BDA0003066907990000055
W represents the flexural modulus of the cross section,
Figure BDA0003066907990000056
step 7: calculating the compressive stress to which the race 2 is subjected
Figure BDA0003066907990000057
Step 8: calculating the compressive stress to which the support ring 14 is subjected
Figure BDA0003066907990000058
And 9, calculating a safety coefficient. The shear-resistant safety coefficient of the pin shaft is
Figure BDA0003066907990000059
Bending-resistant safety coefficient of pin shaft
Figure BDA00030669079900000510
Anti-crushing safety coefficient of seat ring>
Figure BDA00030669079900000511
Anti-crush safety coefficient of support ring
Figure BDA00030669079900000512
According to the calculation, the safety coefficient is larger than 1, and the quick-dismantling structure parameter meets the design requirement.
The safety coefficient calculated by the checking method of the embodiment not only can be used for judging whether the design of the quick-dismantling structure is reasonable, but also can reflect the safety margin of the quick-dismantling structure.
The above is only one group of data, and when in actual checking, whether the parameters of the quick-dismantling structure can meet the design requirements can be checked according to the known parameters and the steps.
In this embodiment, the seat ring and the support ring each include two connection rings, and the two connection rings of the support ring are inserted into the two connection rings of the seat ring. In other embodiments, the seat ring includes two connection rings, two connection rings are not disposed in the support ring, a complete annular protrusion is disposed in the support ring, and a pin shaft through hole is disposed in the annular protrusion, so that the bending moment born by the pin shaft, the compressive stress born by the seat ring and the compressive stress calculation formula born by the support ring need to be changed accordingly.
In the embodiment, each safety coefficient is obtained through calculation, so that whether the design is reasonable or not can be judged, and the safety margin can be seen. In other embodiments, the safety factor may not be calculated any more, and only the magnitude relation between the calculated stress and the allowable stress may be compared.
It should be noted that the above description is only a preferred embodiment of the present utility model, and the present utility model is not limited to the above embodiment, but may be modified without inventive effort or equivalent substitution of some technical features thereof by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model should be included in the protection scope of the present utility model.

Claims (2)

1. A checking method of a turntable bearing is characterized in that: the method comprises the following steps:
1) Calculating the maximum stress F of the individual pins (7) caused by the overturning moment 1 Taking the pin shaft (7) with the largest stress as a checking object, calculating the stress F of the pin shaft (7) caused by axial force 2 Wherein F is 1 And F 2 In the same direction, the resultant force born by the pin shaft (7) is F max ＝F 1 +F 2 ；
2) Checking the shearing stress tau borne by the pin (7) by the resultant force max Bending stress delta max Checking whether the compressive stress delta born by the seat ring (2) at the pin shaft (7) is smaller than the corresponding allowable stress f Compressive stress delta borne by the support ring (14) r Whether less than the corresponding allowable stress;
in the step (1) of the process,
Figure FDA0004159909490000011
wherein: m represents the bending moment born by the pin shaft (7);
w represents the flexural modulus of the cross section,
Figure FDA0004159909490000012
wherein F is Z For applying axial force to the turntable bearing, M Z In order to apply a tilting moment to the turntable bearing, n is the number of pins (7), and d is the effective area of the pins (7)D is the inner diameter of the seat ring (2), A is the cross-sectional area of the pin shaft (7); the seat ring (2) and the supporting ring (14) of the turntable bearing comprise two connecting rings, the two connecting rings of the supporting ring (14) are inserted between the two connecting rings of the seat ring (2), pin shaft perforations are arranged in each connecting ring, and the pin shaft perforations are used for the pin shafts (7) to be penetrated in an adapting way;
wherein, the bending moment born by the pin shaft (7)
Figure FDA0004159909490000013
The seat ring (2) is subjected to compressive stress>
Figure FDA0004159909490000014
The support ring (14) is subjected to compressive stress>
Figure FDA0004159909490000015
Wherein T is f Is the thickness of the connecting ring of the seat ring (2) along the radial direction of the turntable bearing, T r Is the thickness of the connecting ring of the support ring (14) along the radial direction of the turntable bearing.
2. The method of checking a turntable bearing according to claim 1, wherein: according to the shear stress tau max Bending stress delta max Compressive stress delta of the seat ring (2) f Compressive stress delta of the support ring (14) r Calculating a safety coefficient;
wherein the shear safety coefficient of the pin shaft (7) is
Figure FDA0004159909490000016
Bending-resistant safety coefficient of pin shaft (7)>
Figure FDA0004159909490000017
The anti-crushing safety coefficient of the seat ring (2)>
Figure FDA0004159909490000018
The support ring (14) has a crush safety factor>
Figure FDA0004159909490000019
And comparing and judging the calculated safety coefficient with the safety coefficient required by the design to obtain a final checking result.
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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN212744706U (en) * 2020-06-29 2021-03-19 瓦房店轴承集团国家轴承工程技术研究中心有限公司 Multi-row roller turntable bearing

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JP6013314B2 (en) * 2013-12-20 2016-10-25 株式会社神戸製鋼所 Calibration method for thrust load measuring device of closed kneader
CN104732020B (en) * 2015-03-13 2018-02-02 河南科技大学 The check method of six row roller turntable bearings of kiloton the full Terrain Cranes
CN110848250B (en) * 2019-11-28 2021-06-01 洛阳轴承研究所有限公司 Joint bearing for main driving assembly of shield tunneling machine and checking method thereof
CN111914428A (en) * 2020-08-11 2020-11-10 一重集团大连工程技术有限公司 Design checking method for hoisting and hanging cover of large container

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN212744706U (en) * 2020-06-29 2021-03-19 瓦房店轴承集团国家轴承工程技术研究中心有限公司 Multi-row roller turntable bearing

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