CN107657122B - Method for designing cylindrical roller bearing of machine tool spindle - Google Patents

Method for designing cylindrical roller bearing of machine tool spindle Download PDF

Info

Publication number
CN107657122B
CN107657122B CN201710910300.7A CN201710910300A CN107657122B CN 107657122 B CN107657122 B CN 107657122B CN 201710910300 A CN201710910300 A CN 201710910300A CN 107657122 B CN107657122 B CN 107657122B
Authority
CN
China
Prior art keywords
bearing
cylindrical roller
roller bearing
machine tool
tool spindle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201710910300.7A
Other languages
Chinese (zh)
Other versions
CN107657122A (en
Inventor
沈立言
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
WUXI SANLI BEARINGS CO Ltd
Original Assignee
WUXI SANLI BEARINGS CO Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by WUXI SANLI BEARINGS CO Ltd filed Critical WUXI SANLI BEARINGS CO Ltd
Priority to CN201710910300.7A priority Critical patent/CN107657122B/en
Publication of CN107657122A publication Critical patent/CN107657122A/en
Application granted granted Critical
Publication of CN107657122B publication Critical patent/CN107657122B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design

Landscapes

  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Engineering & Computer Science (AREA)
  • Theoretical Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Pure & Applied Mathematics (AREA)
  • Mathematical Optimization (AREA)
  • Mathematical Analysis (AREA)
  • Computer Hardware Design (AREA)
  • Evolutionary Computation (AREA)
  • General Engineering & Computer Science (AREA)
  • Computational Mathematics (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

The invention discloses a method for designing a cylindrical roller bearing of a machine tool spindle, which comprises the following steps: determining main parameters of basic external dimensions of the bearing: the basic physical dimensions D, D, B, r and r1 of cylindrical roller bearings selected in accordance with GB283-87 and GB 274-82; optimization design of main parameters: optimizing by taking the rated dynamic load of the bearing as a target function; designing rated load, and establishing a radial rated dynamic load and radial rated static load calculation formula; fourthly, the diameter of the central circle of the roller and the design of the roller establish 4 calculation formulas; designing an inner ring and an outer ring, and establishing 2 calculation formulas; retainer design, 3 calculation formulas are established. Compared with the bearing in the prior art, the service life of the cylindrical roller bearing of the machine tool spindle is prolonged by 25%, the precision and the rigidity are high, and the product is suitable for the machine tool spindle and has good use performance.

Description

Method for designing cylindrical roller bearing of machine tool spindle
Technical Field
The invention relates to the field of cylindrical roller bearings, in particular to a design method of a cylindrical roller bearing of a main shaft of a machine tool.
Background
The cylindrical roller bearing is a bearing with cylindrical rollers and raceways in linear contact, has large load capacity, mainly bears radial load, has small friction between a rolling body and a flange of a ferrule, is suitable for bearing heavy load and impact load and high-speed rotation, improves the lubricating condition of the contact area of the end surfaces of the rollers and the flange, improves the service performance of the bearing, and is generally suitable for large and medium-sized motors, rolling stocks, machine tool spindles, internal combustion engines, generators, gas turbines, reduction boxes, steel rolling mills, vibrating screens, hoisting and transportation machinery and the like. The cylindrical roller bearing is one of important parts in modern production equipment, and is widely applied to ultrahigh-load and medium-speed equipment such as metallurgical machinery due to the fact that the cylindrical roller bearing can bear high radial load.
The performance of a spindle, which is a key component of a machine tool, directly affects parameters such as rotation precision, rotation speed, rigidity, temperature rise and noise of the machine tool, and further affects the machining quality of a workpiece, such as indexes of dimensional precision, surface roughness and the like of a part.
Disclosure of Invention
In order to overcome the defect that the spindle cylindrical roller bearing selected by the existing machine tool spindle is insufficient, the invention provides a design method of the spindle cylindrical roller bearing of the machine tool spindle, the service life of the product is prolonged by 25% compared with the service life of the bearing in the prior art by the main parameters of the basic appearance size of the bearing, the optimized design of the main parameters, the rated load design, the diameter of the central circle of the roller, the design of the inner ring and the outer ring and the design of the retainer, the precision and the rigidity are high, the product is suitable for the spindle of the machine tool, and the.
In order to achieve the purpose, the invention provides a technical scheme that:
a design method of a cylindrical roller bearing of a machine tool spindle is characterized by comprising the following steps: the method comprises the following steps:
determining main parameters of basic external dimensions of the bearing: the basic physical dimensions D, D, B, r and r1 of cylindrical roller bearings selected in accordance with GB283-87 and GB 274-82;
optimization design of main parameters: optimizing the main parameters by taking the rated dynamic load of the bearing as a target function;
designing rated load, 2 calculation formulas are established:
the calculation formula of the radial rated dynamic load is as follows: cr fc Lwe7/9·Z3/4·Dwe29/27；
The calculation formula of the radial rated static load is as follows: cor is 21.6 · Z · Lwe · Dwe;
where fc is a coefficient relating to the geometry, manufacturing accuracy and material of the bearing part;
fourthly, designing the diameter of the central circle of the roller and the roller, and establishing 4 calculation formulas:
Dpw＝di+Dwe；
dwe is KD (D-D), and the coefficient KD is 0.24-0.29;
the Lw is KL-Dwe, and the coefficient KL is 1-1.67;
Figure GDA0002779108400000021
designing an inner ring and an outer ring:
(a) the calculation formula of the inner ring raceway diameter di is as follows: di-Dpw-Dwe;
(b) the calculation formula of the outer ring raceway diameter De is as follows: de ═ di +2 Dwe;
sixthly, designing the retainer, and establishing 3 calculation formulas:
calculation formula of the center circle diameter Dcp of the retainer: dcp ═ Dpw;
the calculation formula of the thickness Sc of the inner beam of the steel plate of the retainer is as follows: sc is Ks multiplied by Dwe, wherein Ks is 0.23-0.27;
calculation formula of the outer diameter Dc of the cage: dc is Dcp + Kc × Dwe, and Kc is 0.33-0.75; wherein:
d-bearing inner diameter D-bearing outer diameter
B-bearing width r-bearing inner and outer ring chamfer size.
r 1-narrow end face chamfer size of inner and outer rings of bearing Lwe-effective length of roller
di-inner ring raceway diameter De-outer ring raceway diameter
Dpw roller center circle diameter Dwe roller diameter
Lw-roller length Z-roller number
Dwe-roller outer diameter.
Further, the method also comprises roller convexity design, wherein the roller adopts arc correction line bus modification, and the convexity is calculated according to the formula: delta 3.83 x 10-5(5Pr/Z)0.9/(Lw-2Lm)0.8And Pr is the bearing equivalent radial load, and Lm is the partial length of the corrected bus convexity from the end measuring point.
Preferably, when the cylindrical roller bearing of the machine tool spindle is an NJ type cylindrical roller bearing with an inner ring and a single flange or an NH type (NJ + HJ) cylindrical roller bearing with an inner ring and a single flange and an inclined retainer ring, KD is 0.24-0.28; when the cylindrical roller bearing of the machine tool spindle is an NUP type cylindrical roller bearing with an inner ring and a flat retainer ring or an NF type cylindrical roller bearing with an outer ring and a single retainer ring, KD is 0.25-0.29.
Preferably, when the cylindrical roller bearing of the machine tool spindle is an NJ type inner ring single-flange cylindrical roller bearing or an NH type (NJ + HJ) inner ring single-flange cylindrical roller bearing with an inclined retainer ring, KL is 1-1.2; when the cylindrical roller bearing of the machine tool spindle is a NUP type cylindrical roller bearing with an inner ring and a flat retainer ring or an NF type cylindrical roller bearing with an outer ring and a single retainer ring, KL is 1.36-1.67.
Further, 3 calculation formulas are established:
the calculation formula of the outer ring raceway width E is as follows: e ═ Lw;
calculation formula of inner ring raceway width E1: e1 ═ B-2 (B-E);
inner ring flange inner diameter: d2＝KD2X Dwe +0.3, wherein KD2The value is 0.3-0.4.
Further, by utilizing a relation formula of the roller bearing and the service life, the service life values of the bearing under a certain load and different clearances are calculated, a relation curve of the service life and the clearances is drawn, and a negative clearance is obtained, so that the service life can be prolonged.
The beneficial technical effects of the invention are as follows:
1. according to the invention, through the optimization design of the main parameters and the main parameters of the basic overall dimension of the bearing, the design of the rated load, the diameter of the central circle of the roller and the roller, the design of the inner ring and the outer ring and the design of the retainer, the service life of the product is prolonged by 25% compared with the service life of the bearing in the prior art, the precision and the rigidity are high, and the product is suitable for a machine tool spindle and has good use performance.
2. The cylindrical roller bearing adopts the negative clearance, when the bearing conditions of the bearing are the same, the bearing load distribution angle is increased along with the reduction of the radial clearance, the number of the bearing rollers is increased, the maximum contact load of the rollers is reduced, the relative radial displacement of the inner ring and the outer ring is reduced, and the high-rigidity, high-precision and high-rotating-speed rotation of a machine tool roller can be realized; on the other hand, by utilizing a relation formula of the roller bearing clearance and the service life, the service life numerical values of different clearances of a plurality of groups of bearings under certain load are calculated, a relation curve of the service life and the clearances is drawn, and the adopted negative clearances are obtained, so that the service life can be prolonged.
3. In the integral structure of the cylindrical roller bearing, the roller is an important component, and the quality of the roller is the important factor of the quality of the cylindrical roller bearing.
4. The cylindrical roller is in line contact with the roller path, has large radial load capacity, and is suitable for bearing heavy load and impact load and high-speed rotation. The roller path and the rolling body of the cylindrical roller bearing are in geometric shapes, the bearing has higher bearing capacity after improved design, and the novel structural design of the flange and the roller end surface not only improves the axial bearing capacity of the bearing, but also improves the lubricating strips in the contact area of the roller end surface and the flange.
Drawings
FIG. 1 is a schematic diagram of a design process of a method for designing a cylindrical roller bearing of a spindle of a machine tool
Fig. 2 simulated contact stress diagram.
Detailed Description
The following description of the embodiments refers to the accompanying drawings for illustrating the specific embodiments in which the invention may be practiced. Now, a method for designing a cylindrical roller bearing of a machine tool spindle according to an embodiment of the present invention will be further described with reference to the accompanying drawings, which are schematic design flow diagrams of the method for designing a cylindrical roller bearing of a machine tool spindle shown in fig. 1.
A design method of a cylindrical roller bearing of a machine tool spindle comprises the following design steps:
the basic overall dimension main parameters of the bearing are as follows: the basic dimensions D, B, r and r1 of a cylindrical roller bearing according to GB283-87 and GB274-82, wherein: d-bearing inner diameter, D-bearing outer diameter, B-bearing width, r-bearing inner and outer ring chamfer size, r 1-bearing inner and outer ring narrow end face chamfer size.
Optimization design of main parameters: the maximum service life is taken as an optimization target in the optimization design of the bearing, and the optimization design target of the cylindrical roller bearing of the machine tool spindle is the maximum rated dynamic load according to the calculation formula of the service life of the bearing, wherein the service life of the bearing depends on the magnitude of the rated dynamic load.
Designing rated load:
the calculation formula of the radial rated dynamic load is as follows: cr fc Lwe7/9·Z3/4·Dwe29/27；
The calculation formula of the radial rated static load is as follows: cor is 21.6 · Z · Lwe · Dwe;
where fc, chosen according to GB/T6391-1995, is a coefficient related to the geometry, manufacturing accuracy and material of the bearing component.
Fourthly, designing the diameter of the central circle of the roller and the roller:
and Dpw, Dwe, Lw and Z are obtained by computer optimization, the height of the outer ring is determined, and the diameter of the raceway of the inner ring is obtained according to the diameter of the roller.
Dpw＝di+Dwe
Dwe is KD (D-D), the coefficient KD is 0.. 24-0.29, when the cylindrical roller bearing of the machine tool spindle is NJ type of the inner ring single-flange cylindrical roller bearing or NH type (NJ + HJ) of the inner ring single-flange cylindrical roller bearing with an inclined retainer ring, the KD is 0.24-0.28; when the cylindrical roller bearing of the machine tool spindle is an NUP type cylindrical roller bearing with an inner ring and a flat retainer ring or an NF type cylindrical roller bearing with an outer ring and a single retainer ring, KD is 0.25-0.29.
When the Lw is KL-Dwe, the coefficient KL is 1-1.67, and the cylindrical roller bearing of the machine tool spindle is an inner ring single-flange cylindrical roller bearing NJ type or an inner ring single-flange cylindrical roller bearing NH type (NJ + HJ) with an inclined retainer ring, the KL is 1-1.2; when the cylindrical roller bearing of the machine tool spindle is a NUP type cylindrical roller bearing with an inner ring and a single flange and a flat check ring or a NF type cylindrical roller bearing with an outer ring and a single flange, KL is 1.36-1.67
Figure GDA0002779108400000061
Wherein: dpw-roller center circle diameter, Dwe-roller diameter, Lw-roller length, and Z-roller number;
the invention selects the relatively smaller diameter specification of the rollers, more rollers and better rigidity.
The roller convexity modification design can adopt logarithmic bus modification and also can adopt circular arc modification line bus modificationObviously adopting the calculation formula of the arc correction line bus correction type and the convexity degree: delta 3.83 x 10-5(5Pr/Z)0.9/(Lw-2Lm)0.8And Pr is the bearing equivalent radial load, and Lm is the partial length of the corrected bus convexity from the end measuring point.
The calculation formula of the outer ring raceway width E is as follows: e ═ Lw;
calculation formula of inner ring raceway width E1: e1 ═ B-2 (B-E);
inner ring flange inner diameter: d2＝KD2X Dwe +0.3, wherein KD2The value is 0.3-0.4.
Designing an inner ring and an outer ring:
(a) the calculation formula of the inner ring raceway diameter di (the value precision is 0.001): : di-Dpw-Dwe;
(b) the calculation formula of the outer ring raceway diameter De (the value precision is 0.001): de ═ di +2 Dwe;
wherein: di-inner ring raceway diameter, De-outer ring raceway diameter;
sixthly, designing the retainer, and establishing 3 calculation formulas:
calculation formula of the center circle diameter Dcp of the retainer: dcp ═ Dpw;
the calculation formula of the thickness Sc of the inner beam of the steel plate of the retainer is as follows: sc is Ks multiplied by Dwe, wherein Ks is 0.23-0.27;
calculation formula of the outer diameter Dc of the cage: dc is Dcp + Kc × Dwe, wherein Kc is 0.33-0.75;
the optimization process comprises the following steps of 1, inputting the following parameters of the bearing into a computer:
the roller bearing load Q is 14670N, the roller diameter Dwe is 9.0mm, the roller effective length Lwe is 8.6mm, the roller length Lw is 10mm, the inner ring raceway diameter di is 86mm, the outer ring raceway diameter De is 104mm, the bearing play Ur is 0.04mm, the number of rollers Z is 25, and the distance to the end measuring point Lm is 0.9 mm.
And 2, calculating the contact stress condition of the roller with the inner and outer rings under the load by using a computer and giving optimized logarithmic contour curve data and a simulated contact stress graph:
(1) the number of loaded rollers simultaneously is: 9
(2) Analyzing the loading condition of each roller in the bearing:
Figure GDA0002779108400000071
(3) convexity of the roller at the measured point position:
the amount of convexity at a distance of 0.900mm from the end of the logarithmic roller was 4.352080 μm
(4) Maximum contact stress between each loaded roller and the inner ring in the bearing:
the maximum contact stress of the loaded roller 1 is: 1.768663Gpa
The maximum contact stress of the loaded roller 2 is: 1.726726GPa
The maximum contact stress of the loaded roller 3 is: 1.602858GPa
The maximum contact stress of the loaded roller 4 is: 1.378764GPa
The maximum contact stress of the loaded roller 5 is: 1.015120GPa
(5) Maximum contact stress between each loaded roller and the outer ring in the bearing:
the maximum contact stress of the loaded roller 1 is: 1.612892GPa
The maximum contact stress of the loaded roller 2 is: 1.574735GPa
The maximum contact stress of the loaded roller 3 is: 1.458751GPa
The maximum contact stress of the loaded roller 4 is: 1.256256GPa
The maximum contact stress of the loaded roller 5 is: 0.9223952Pa
The invention utilizes a relation formula of the roller bearing and the service life to calculate the service life values of the bearing under a certain load and draw a relation curve of the service life and the play to obtain that the negative play is adopted, so that the service life can be prolonged.
The above embodiments are merely illustrative of the technical concept and features of the present invention, and the present invention is not limited thereto, and any equivalent changes or modifications made according to the spirit of the present invention should be included in the scope of the present invention.

Claims (6)

1. A design method of a cylindrical roller bearing of a machine tool spindle is characterized by comprising the following steps: the method comprises the following steps:
determining main parameters of basic external dimensions of the bearing: the basic physical dimensions D, D, B, r and r1 of cylindrical roller bearings selected in accordance with GB283-87 and GB 274-82;
optimization design of main parameters: optimizing the main parameters by taking the rated dynamic load of the bearing as a target function;
designing rated load, 2 calculation formulas are established:
the calculation formula of the radial rated dynamic load is as follows: cr fc Lwe7/9·Z3/4·Dwe29/27；
The calculation formula of the radial rated static load is as follows: cor is 21.6 · Z · Lwe · Dwe;
where fc is a coefficient relating to the geometry, manufacturing accuracy and material of the bearing part;
fourthly, designing the diameter of the central circle of the roller and the roller, and establishing 4 calculation formulas:
Dpw＝di+Dwe；
dwe is KD (D-D), and the coefficient KD is 0.24-0.29;
the Lw is KL-Dwe, and the coefficient KL is 1-1.67;
Figure FDA0002779108390000011
designing an inner ring and an outer ring:
(a) the calculation formula of the inner ring raceway diameter di is as follows: di-Dpw-Dwe;
(b) the calculation formula of the outer ring raceway diameter De is as follows: de ═ di +2 Dwe;
sixthly, designing the retainer, and establishing 3 calculation formulas:
calculation formula of the center circle diameter Dcp of the retainer: dcp ═ Dpw;
the calculation formula of the thickness Sc of the inner beam of the steel plate of the retainer is as follows: sc is Ks multiplied by Dwe, wherein Ks is 0.23-0.27;
calculation formula of the outer diameter Dc of the cage: dc is Dcp + Kc × Dwe, and Kc is 0.33-0.75; wherein:
d-bearing inner diameter D-bearing outer diameter
B-bearing width r-bearing inner and outer ring chamfer size
r 1-narrow end face chamfer size of inner and outer rings of bearing Lwe-effective length of roller
di-inner ring raceway diameter De-outer ring raceway diameter
Dpw roller center circle diameter Dwe roller diameter
Lw-roller length Z-roller number.
2. The method for designing a cylindrical roller bearing for a machine tool spindle according to claim 1, wherein: the method further comprises the design of roller convexity, the roller adopts arc correction line bus modification, and the calculation formula of the convexity is as follows: delta 3.83 x 10-5(5Pr/Z)0.9/(Lw-2Lm)0.8And Pr is the bearing equivalent radial load, and Lm is the partial length of the corrected bus convexity from the end measuring point.
3. The method for designing a cylindrical roller bearing for a machine tool spindle according to claim 1, wherein: when the cylindrical roller bearing of the machine tool spindle is an NJ type cylindrical roller bearing with an inner ring and a single flange or an NH type (NJ + HJ) cylindrical roller bearing with an inner ring and a single flange and an inclined retainer ring, KD is 0.24-0.28; when the cylindrical roller bearing of the machine tool spindle is an NUP type cylindrical roller bearing with an inner ring and a flat retainer ring or an NF type cylindrical roller bearing with an outer ring and a single retainer ring, KD is 0.25-0.29.
4. The method for designing a cylindrical roller bearing for a machine tool spindle according to claim 1, wherein: when the cylindrical roller bearing of the machine tool spindle is an NJ type cylindrical roller bearing with an inner ring and a single flange or an NH type (NJ + HJ) cylindrical roller bearing with an inner ring and a single flange and an inclined retainer ring, KL is 1-1.2; when the cylindrical roller bearing of the machine tool spindle is a NUP type cylindrical roller bearing with an inner ring and a flat retainer ring or an NF type cylindrical roller bearing with an outer ring and a single retainer ring, KL is 1.36-1.67.
5. The method for designing a cylindrical roller bearing for a machine tool spindle according to claim 1, wherein:
3 calculation formulas are established:
the calculation formula of the outer ring raceway width E is as follows: e ═ Lw;
calculation formula of inner ring raceway width E1: e1 ═ B-2 (B-E);
inner ring flange inner diameter: d2＝KD2X Dwe +0.3, wherein KD2The value is 0.3-0.4.
6. The method for designing a cylindrical roller bearing for a machine tool spindle according to any one of claims 1 to 5, wherein: the service life values of different clearances of the bearing under a certain load are calculated by utilizing a relation formula of the roller bearing and the service life, a relation curve of the service life and the clearances is drawn, a negative clearance is obtained, the service life can be prolonged, when the bearing conditions of the bearing are the same, the bearing load distribution angle is increased along with the reduction of the radial clearance, the number of the bearing rollers is increased, the maximum contact load of the rollers is reduced, and the relative radial displacement of the inner ring and the outer ring is reduced.
CN201710910300.7A 2017-09-29 2017-09-29 Method for designing cylindrical roller bearing of machine tool spindle Active CN107657122B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201710910300.7A CN107657122B (en) 2017-09-29 2017-09-29 Method for designing cylindrical roller bearing of machine tool spindle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201710910300.7A CN107657122B (en) 2017-09-29 2017-09-29 Method for designing cylindrical roller bearing of machine tool spindle

Publications (2)

Publication Number Publication Date
CN107657122A CN107657122A (en) 2018-02-02
CN107657122B true CN107657122B (en) 2021-05-11

Family

ID=61117326

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201710910300.7A Active CN107657122B (en) 2017-09-29 2017-09-29 Method for designing cylindrical roller bearing of machine tool spindle

Country Status (1)

Country Link
CN (1) CN107657122B (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108595765B (en) * 2018-03-27 2021-12-28 明阳智慧能源集团股份公司 Wind generating set double-row tapered roller bearing load distribution and service life calculation method
CN108984968A (en) * 2018-08-22 2018-12-11 中国北方车辆研究所 A kind of optimum design method and device of bearing fit tolerance
CN113468695B (en) * 2021-07-20 2023-08-25 人本股份有限公司 Convexity optimization design method for roller
CN113588267B (en) * 2021-07-27 2022-06-14 成都飞机工业（集团）有限责任公司 Electric main shaft bearing structure parameter inference method based on vibration spectrum analysis
CN113742858B (en) * 2021-08-13 2024-04-19 钱潮轴承有限公司 Method for quickly searching borrowed roller for tapered roller bearing design

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201326645Y (en) * 2008-01-28 2009-10-14 文鉴恒 Taper roller bearing for bullet train developed through limit design and long life technique
CN102352888A (en) * 2011-09-28 2012-02-15 福建省永安轴承有限责任公司 Optimal design method of double-row tapered roller bearing with contact angle alpha of 28 degrees 48 minutes 39 seconds

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008009740A1 (en) * 2008-02-18 2009-08-20 Imo Holding Gmbh Wind turbine and method for operating the same

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201326645Y (en) * 2008-01-28 2009-10-14 文鉴恒 Taper roller bearing for bullet train developed through limit design and long life technique
CN102352888A (en) * 2011-09-28 2012-02-15 福建省永安轴承有限责任公司 Optimal design method of double-row tapered roller bearing with contact angle alpha of 28 degrees 48 minutes 39 seconds

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
基于nCode DesignLife的滚滑轴承疲劳寿命比较分析;卢黎明 等;《机械传动》;20170315;第41卷(第3期);全文 *

Also Published As

Publication number Publication date
CN107657122A (en) 2018-02-02

Similar Documents

Publication Publication Date Title
CN107657122B (en) Method for designing cylindrical roller bearing of machine tool spindle
CN106584217B (en) A kind of double half inner ring grinding techniques of band oil groove angular contact ball bearing ring
CN108266459B (en) Match the machine tool chief axis circular runout calculation method in gap based on Bearing Grinding
CN101642866B (en) Method for manufacturing needle bearing
CN110059349B (en) Method for determining rated static load of roller needle bearing installed on cantilever of bolt shaft
Jedrzejewski et al. Hybrid model of high speed machining centre headstock
KR102026075B1 (en) Combination ball bearing and main shaft device for machine tool
CN111188832A (en) Energy efficiency type tapered roller bearing
Zmarzły Influence of bearing raceway surface topography on the level of generated vibration as an example of operational heredity
JP2019074214A (en) Angular ball bearing and its manufacturing method
CN201529780U (en) Heavy caliber boring and rolling head
TWI568943B (en) Crown retainer and bevel ball bearing
CN109563879A (en) Ball bearing, main shaft device and lathe
CN112112889B (en) Micro-texture deep groove ball bearing with auxiliary contact area lubrication function and inner and outer ring machining method thereof
CN113664467A (en) Manufacturing method of engine crankshaft
CN107859688B (en) Novel radial bearing for screw drilling tool and production process thereof
JP3982246B2 (en) Roller bearing for machine tool spindle support
CN216279018U (en) Roller needle bearing outer ring and roller needle bearing of logarithmic modification
CN103352919B (en) Solid cage and reinforced solid tapered roller bearing
CN209164384U (en) The oily leaf sliding bearing of one kind six
CN206257165U (en) A kind of conical roller bearing ring
CN112836445B (en) Method for solving dynamic contact mixed lubrication parameters of rolling bearing
US20160178002A1 (en) Double-row spherical roller bearing
CN108015498A (en) A kind of angular contact ball bearing turning processing method of outer ring with elastic support
CN211343705U (en) Cylindrical roller bearing matched with main shaft of ultra-light thin and high-rotating-speed cold molding machine

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant