CN105134782B - Bearing pad oil retainer ring - Google Patents
Bearing pad oil retainer ring Download PDFInfo
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- CN105134782B CN105134782B CN201410724732.5A CN201410724732A CN105134782B CN 105134782 B CN105134782 B CN 105134782B CN 201410724732 A CN201410724732 A CN 201410724732A CN 105134782 B CN105134782 B CN 105134782B
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- inner ring
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- oil
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- convex shoulder
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Abstract
The invention relates to a bearing pad oil retainer ring, which comprises an inner ring, an outer ring, a positioning pin and a fastening screw (7) between the inner ring and the outer ring, and is characterized in that: the fixed connection mode of the joint surface (14) of the inner ring is designed into a plug-in fixed connection mode through a bolt connection fixed mode, namely, a convex shoulder groove (9) and a convex shoulder (12) are respectively arranged on the joint surface (14) of the upper half part (2) and the lower half part (3) of the inner ring, a positioning pin (10) and a perforation pin (8) which are connected and positioned to prevent circumferential rotation are arranged, the groove width of the convex shoulder groove (9) on the inner ring is widened for preventing the perforation pin (8) from shearing and damaging, the width of the convex shoulder at the outer ring hole of the outer ring is correspondingly increased, and a weight removing groove (13) is arranged on the inner ring.
Description
Technical Field
The invention relates to the technical field of turbonators, in particular to a bearing pad oil retainer ring which can be widely applied to a 600MW turbonator.
Background
At present, the 600MW steam turbine generator units operated by generating enterprises in China are in operation, the situation that an oil retaining ring body has problems frequently occurs in operation, usually, a certain bearing bush of a shaft system suddenly has large shaft vibration, abnormal sound in a bearing box is accompanied by metal knocking sound, the internal pressure of the bearing bush is reduced due to the breakage of an inner ring of the oil retaining ring or the falling of a fastening bolt of a joint surface of the oil retaining ring in the shutdown process, and the problem of bearing bush burning loss is easily caused in the idling process. This problem cannot be solved after several changes of the inner ring of the slinger, which means that the failure is not due to the quality of the installation. The matching depth between the oil slinger inner ring radial positioning groove and the oil slinger outer ring radial positioning pin is found to have a certain problem by measuring the matching of the bearing bush oil slinger inner ring and the oil slinger outer ring, although each power plant can take some measures and can only prolong the damage period and cannot thoroughly solve the problem. The situations show that accidents such as overlarge vibration of a tile shaft of a turbine generator unit, abnormal sound in a bearing box, tile burning and the like are caused by the problem or the fault of an oil retainer ring in the operation of the turbine generator unit of a power generation enterprise. At present, a mechanical sealing device for bearing bushes of steam turbine generator units or large and medium-sized rotating machines at home and abroad usually adopts a sealing mode of matching a dynamic oil slinger and a static oil slinger, but because the static oil slinger is a straight cylinder, lubricating oil splashed onto the static ring cannot freely flow back to the bottom of the inner wall of a sealing end cover of the bearing bush, so that oil leakage or oil seepage often occurs at the joint of the sealing end cover and a rotating shaft; in addition, because the moving oil slinger and the static oil slinger are both steel parts, when the rotating machine vibrates, the moving oil slinger and the static oil slinger can generate serious friction and damage when the radial clearance of the shaft returns to zero or is matched with an excessively small clearance. However, investigation finds that the fracture problem or the fault of the outer ring positioning pin of the oil retainer ring during the operation of the steam turbine generator unit of a power generation enterprise often causes accidents such as overlarge vibration of a tile shaft of the unit, abnormal sound in a bearing box, tile burning and the like. For example, how to solve the problems that sudden shaft vibration is large, accompanied by abnormal sound in a bearing box, tile burning and the like which often occur in the running of a steam turbine generator unit is urgent to solve at present.
Disclosure of Invention
The purpose of the invention is: the bearing bush oil retainer ring is improved aiming at the existing problems, is simple in structure, can meet design requirements, is safe to operate, can effectively avoid accidents such as overlarge vibration of a certain bearing bush of a unit, abnormal sound in a bearing box, bush burning and the like caused by the fault of an inner ring of the oil retainer ring, and can be widely applied to a 600MW steam turbine generator unit.
The technical scheme adopted by the invention for solving the technical problems is as follows: the utility model provides a bearing pad oil retainer ring, includes the inner ring that the first half 2 of inner ring and inner ring lower half 3 constitute, the outer loop that the first half 1 of outer loop and outer ring lower half 4 constitute, locating pin and fastening screw 7 between inner ring and outer ring, its characterized in that: the fixed connection mode of the joint surface 14 of the inner ring upper half part 2 and the inner ring lower half part 3 is designed to be a plug-in fixed connection mode through a bolt connection fixed mode, namely, a convex shoulder groove 9 and a convex shoulder 12 are respectively arranged on the joint surface 14 of the inner ring upper half part 2 and the inner ring lower half part 3, a positioning pin 10 and a perforation pin 8 which are connected and positioned to prevent circumferential rotation are arranged, meanwhile, the groove width of the convex shoulder groove 9 on the inner ring is widened to prevent the perforation pin 8 from being sheared and damaged, and the width of the convex shoulder at the outer ring positioning piece hole of the outer ring is correspondingly increased, as shown in figures 1.
The middles of the upper half part 2 and the lower half part 3 of the inner ring are respectively provided with a deduplication groove 13, as shown in fig. 1-10. The fixed connection mode of the joint surfaces, namely the joint surfaces 14, of the upper half part 2 and the lower half part 3 of the inner ring is designed to be a splicing fixed connection mode by a bolt connection fixed mode, so that the weight of the inner ring of the oil retainer ring is increased, the fixed connection mode is re-designed to remove the weight on the basis of ensuring the strength of the oil retainer ring, namely whether the oil pressure in the bearing bush can jack the oil retainer ring to form an oil film in the running process is calculated, the weight of the inner ring of the oil retainer ring is increased by arranging the weight removing groove 13 in the middle of the inner ring, because the fixed connection mode of the joint surfaces, namely the joint surfaces 14, of the upper half part 2 and the lower half part 3 of the bearing bush is designed to be a splicing fixed connection mode by a bolt connection fixed mode, so that the weight of the inner ring of the oil retainer ring of the new bearing bush is calculated to be heavier than the inner ring of the original oil retainer ring, in the specific design and production, whether, can meet the operation safety of the power plant. The weight is calculated to meet the requirement of establishing an oil film in operation, and the safety of the unit is not influenced. The influence of redesign back axle bush oil slinger inner ring weight change to unit shafting vibration is mainly in reforming transform axle bush oil slinger ring body in-process, and the change of the back weight of key solution axle bush oil slinger inner ring reforming is to the influence that the unit axle shakes, can not influence the unit axle problem of shaking at 2 kilograms within ranges after accounting, but the prerequisite is that whether the oil pressure in the axle bush can jack up the oil slinger inner ring in service, establishes good oil film. Through practice, whether the weight change of the inner ring of the oil scraper ring after the transformation can meet the requirement of establishing a stable oil film in the operation process or not can be ensured, the safe operation of the inner ring of the oil scraper ring can be ensured under the weight calculated by the designed oil group, the safe operation of the inner ring of the oil scraper ring can be ensured under the pressure of a lubricating oil main pipe of 0.1-0.14MPa, and the problem of black gold abrasion of the inner ring of the oil scraper ring can not be caused due to the weight increase. The oil scraper ring is equivalent to a narrow circular bearing due to the structural characteristics of the oil scraper ring, the operation working condition of the oil scraper ring is opposite to that of a common bearing, the common bearing is borne by a lower bearing, and the oil scraper ring is borne by an upper half. At present, the calculation of the extreme load bearing does not have a mature calculation method at home and abroad, and the calculation result is greatly different from the actual operation state, mainly because the oil film composition of the lubricating oil is extremely complex and the specific modeling is difficult under the condition of small width. After the oil scraper ring is machined, an installation test is carried out in an existing running unit, the vibration of a rotor, the vibration of a bearing bush, the temperature change of the bearing bush and the like are strictly detected during the test, and meanwhile, whether noise exists in a bearing box or not is monitored. After about one year of operation, the rotor shaft diameter, the bearing alloy, the oil deflector ring alloy and the like are not obviously abraded, and meanwhile, the structure of the stop pin and the ring body on the oil deflector ring is stable, so that a good oil film is established between the oil deflector ring and the rotor shaft diameter in the operation process of the unit, and the oil deflector ring works normally. In addition, the material is selected to combine the inner ring with tungsten and gold, which is mainly suitable for the improvement of the bearing bush oil retainer of the 600MW steam turbine set, and certainly can also be used for the improvement of the bearing bush oil retainer of other steam turbine sets such as 300MW and the like. In addition, the inner ring formed by the upper half part 2 of the inner ring of the oil slinger and the lower half part 3 of the inner ring of the oil slinger is designed to have a shaft diameter clearance of 0.81-0.91 mm. The fault data before the power plant group is transformed is taken as an example, and the effect after the transformation process is processed is explained. The main symptoms of the oil baffle ring body which often has abnormal conditions in the running are that a certain bearing bush of a shaft system suddenly has large axial vibration, abnormal sound in a bearing box is accompanied with metal knocking sound, the internal pressure of the bearing bush is reduced due to the breakage of an inner ring of the oil baffle ring or the falling of a fastening bolt of a joint surface of the oil baffle ring in the shutdown process, and the problem of bearing bush burning loss is easily caused in the idling process. From the record data and production, after the bearing bush oil deflector inner ring and the bearing bush oil deflector outer ring designed and produced by the technology are replaced, the accidents of overlarge vibration of a certain bearing bush shaft of a unit, abnormal sound in a bearing box, tile burning and the like caused by the fault of the oil deflector inner ring can be effectively avoided in safe operation.
The beneficial effect of this technique or say that compare with prior art has the characteristics that: 1. the problems of the fracture of an inner ring of the oil deflector and the loosening strength of a connecting bolt of a joint surface are solved through design and modification; 2. the problem that the safe operation of the unit is threatened because the local vibration of a shafting of the unit exceeds the standard due to the breakage of an inner ring of an oil deflector ring and the falling of a connecting bolt of a joint surface in the operation is solved through the design and the transformation; 3. the hidden danger of unit damage and serious accidents caused by loose operation of bolts on the joint surface of the inner ring 1 of the oil deflector or excessive fragments after the inner ring of the oil deflector is suddenly broken is eliminated; 4. experiments verify that the oil deflector inner ring can establish a good oil film in operation, and the dark gold cannot be abraded due to the fact that the oil film cannot be established due to weight increase. In a word, the technology has the characteristics of simple structure, safe use, convenient installation, high strength and the like.
Drawings
Fig. 1 is an overall front view of the present invention.
Fig. 2 is a sectional view a-a of fig. 1.
Fig. 3 is a partial enlarged view D of fig. 1.
Figure 4 is a front view of the outer ring of figure 1.
Fig. 5 is a cross-sectional view of the outer ring B-B of the present invention.
Fig. 6 is a front view of the inner ring of the present invention.
FIG. 7 is a cross-sectional view of the inner ring C-C of the present invention.
Fig. 8 is a top view of the inner ring of the present invention.
Fig. 9 is an inner ring E-direction view of the present invention.
Fig. 10 is a partial enlarged view of the inner ring F of the present invention.
In the figure: the oil ring structure comprises an outer ring upper half portion (or called as a bearing bush oil slinger outer ring upper half portion) 1, an inner ring upper half portion (or called as a bearing bush oil slinger inner ring upper half portion) 2, an inner ring lower half portion 3 (or called as a bearing bush oil slinger inner ring lower half portion), an outer ring lower half portion 4 (or called as a bearing bush oil slinger outer ring lower half portion), a fixing hole 5, an oil discharge hole 6, a fastening screw 7, a perforation pin 8, a convex shoulder groove 9 (oil slinger inner ring convex shoulder positioning groove), a positioning pin 10, a pin hole 11, a convex shoulder 12 (inner ring convex shoulder), a weight removing groove 13, a.
Detailed Description
The specific implementation mode of the invention, as shown in fig. 1-10, is a bearing pad oil retainer ring, which comprises an inner ring formed by an inner ring upper half part 2 and an inner ring lower half part 3, an outer ring formed by an outer ring upper half part 1 and an outer ring lower half part 4, a positioning pin and a fastening screw 7 between the inner ring and the outer ring, and is characterized in that: the fixed connection mode of the joint surface 14 of the inner ring upper half part 2 and the inner ring lower half part 3 is designed to be a plug-in fixed connection mode through a bolt connection fixed mode, namely, a convex shoulder groove 9 and a convex shoulder 12 are respectively arranged on the joint surface 14 of the inner ring upper half part 2 and the inner ring lower half part 3, a positioning pin 10 and a perforation pin 8 which are connected and positioned to prevent circumferential rotation are arranged, meanwhile, the groove width of the convex shoulder groove 9 on the inner ring is widened to prevent the perforation pin 8 from being sheared and damaged, and the width of the convex shoulder at the outer ring positioning piece hole of the outer ring is correspondingly increased, as shown in figures 1.
The middles of the upper half part 2 and the lower half part 3 of the inner ring are respectively provided with a deduplication groove 13, as shown in fig. 1-10. In addition, the inner ring formed by the upper half part 2 of the inner ring of the oil slinger and the lower half part 3 of the inner ring of the oil slinger is designed to have a shaft diameter clearance of 0.81-0.91 mm. The fixed connection mode of the joint surfaces, namely the joint surfaces 14, of the upper half part 2 and the lower half part 3 of the inner ring is designed to be a splicing fixed connection mode by a bolt connection fixed mode, so that the weight of the inner ring of the oil retainer ring is increased, the fixed connection mode is re-designed to remove the weight on the basis of ensuring the strength of the oil retainer ring, namely whether the oil pressure in the bearing bush can jack the oil retainer ring to form an oil film in the running process is calculated, the weight of the inner ring of the oil retainer ring is increased by arranging the weight removing groove 13 in the middle of the inner ring, because the fixed connection mode of the joint surfaces, namely the joint surfaces 14, of the upper half part 2 and the lower half part 3 of the bearing bush is designed to be a splicing fixed connection mode by a bolt connection fixed mode, so that the weight of the inner ring of the oil retainer ring of the new bearing bush is calculated to be heavier than the inner ring of the original oil retainer ring, in the specific design and production, whether, can meet the operation safety of the power plant. The weight is calculated to meet the requirement of establishing an oil film in operation, and the safety of the unit is not influenced. The influence of redesign back axle bush oil slinger inner ring weight change to unit shafting vibration is mainly in reforming transform axle bush oil slinger ring body in-process, and the change of the back weight of key solution axle bush oil slinger inner ring reforming is to the influence that the unit axle shakes, can not influence the unit axle problem of shaking at 2 kilograms within ranges after accounting, but the prerequisite is that whether the oil pressure in the axle bush can jack up the oil slinger inner ring in service, establishes good oil film. Through practice, whether the weight change of the inner ring of the oil scraper ring after the transformation can meet the requirement of establishing a stable oil film in the operation process or not can be ensured, the safe operation of the inner ring of the oil scraper ring can be ensured under the weight calculated by the designed oil group, the safe operation of the inner ring of the oil scraper ring can be ensured under the pressure of a lubricating oil main pipe of 0.1-0.14MPa, and the problem of black gold abrasion of the inner ring of the oil scraper ring can not be caused due to the weight increase. The oil scraper ring is equivalent to a narrow circular bearing due to the structural characteristics of the oil scraper ring, the operation working condition of the oil scraper ring is opposite to that of a common bearing, the common bearing is borne by a lower bearing, and the oil scraper ring is borne by an upper half. At present, the calculation of the extreme load bearing does not have a mature calculation method at home and abroad, and the calculation result is greatly different from the actual operation state, mainly because the oil film composition of the lubricating oil is extremely complex and the specific modeling is difficult under the condition of small width. After the oil scraper ring is machined, an installation test is carried out in an existing running unit, the vibration of a rotor, the vibration of a bearing bush, the temperature change of the bearing bush and the like are strictly detected during the test, and meanwhile, whether noise exists in a bearing box or not is monitored. After about one year of operation, the rotor shaft diameter, the bearing alloy, the oil deflector ring alloy and the like are not obviously abraded, and meanwhile, the structure of the stop pin and the ring body on the oil deflector ring is stable, so that a good oil film is established between the oil deflector ring and the rotor shaft diameter in the operation process of the unit, and the oil deflector ring works normally. In addition, the material is selected to combine the inner ring with tungsten and gold, which is mainly suitable for the improvement of the bearing bush oil retainer of the 600MW steam turbine set, and certainly can also be used for the improvement of the bearing bush oil retainer of other steam turbine sets such as 300MW and the like.
The fault data before the power plant group is transformed is taken as an example, and the effect after the transformation process is processed is explained. The main symptoms of the oil baffle ring body which often has abnormal conditions in the running are that a certain bearing bush of a shaft system suddenly has large axial vibration, abnormal sound in a bearing box is accompanied with metal knocking sound, the internal pressure of the bearing bush is reduced due to the breakage of an inner ring of the oil baffle ring or the falling of a fastening bolt of a joint surface of the oil baffle ring in the shutdown process, and the problem of bearing bush burning loss is easily caused in the idling process. From the record data and production, after the bearing bush oil deflector inner ring and the bearing bush oil deflector outer ring designed and produced by the technology are replaced, the safe operation can be effectively avoided, and the problems of overlarge vibration of a certain bearing bush shaft of the unit, abnormal sound in a bearing box, bearing bush burning and the like caused by the fault of the oil deflector inner ring can be effectively avoided.
Claims (1)
1. The utility model provides a bearing pad oil retainer ring, includes the inner ring that the first half (2) of inner ring and inner ring lower half (3) constitute, the outer ring that the first half (1) of outer ring and outer ring lower half (4) constitute, locating pin and fastening screw (7) between inner ring and outer ring, its characterized in that: the fixed connection mode of the joint surface (14) of the upper half part (2) of the inner ring and the lower half part (3) of the inner ring is designed to be a plug-in fixed connection mode through a bolt connection fixed mode, namely, a convex shoulder groove (9) and a convex shoulder (12) are respectively arranged on the joint surface (14) of the upper half part (2) of the inner ring and the lower half part (3) of the inner ring, a positioning pin (10) and a perforation pin (8) which are connected and positioned to prevent circumferential rotation are arranged, the arrangement direction of the positioning pin (10) is axially parallel to the axial direction of the inner ring, meanwhile, the groove width of the convex shoulder groove (9) on the inner ring is widened to prevent the perforation pin (8) from being sheared and damaged;
the middles of the upper half part (2) and the lower half part (3) of the inner ring are respectively provided with a weight-removing groove (13).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410724732.5A CN105134782B (en) | 2014-12-04 | 2014-12-04 | Bearing pad oil retainer ring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410724732.5A CN105134782B (en) | 2014-12-04 | 2014-12-04 | Bearing pad oil retainer ring |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105134782A CN105134782A (en) | 2015-12-09 |
| CN105134782B true CN105134782B (en) | 2020-06-12 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410724732.5A Active CN105134782B (en) | 2014-12-04 | 2014-12-04 | Bearing pad oil retainer ring |
Country Status (1)
| Country | Link |
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| CN (1) | CN105134782B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106644795A (en) * | 2016-09-23 | 2017-05-10 | 上海交通大学 | Testing machine for abrasive wear test of bearing bush |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2177096Y (en) * | 1993-09-16 | 1994-09-14 | 哈尔滨电站改造高新技术应用公司 | Floating oil scraper ring for steam turbine |
| AU763748B2 (en) * | 1998-08-11 | 2003-07-31 | David Hercules Slabbert | Bearing maintenance accessory |
| CN201416639Y (en) * | 2009-06-24 | 2010-03-03 | 于翔 | Oil deflector ring for bearing box of rotary machine |
| CN202203282U (en) * | 2011-07-16 | 2012-04-25 | 黄浩杨 | Oil ring structure |
| CN102269224A (en) * | 2011-08-01 | 2011-12-07 | 扬州尼尔工程塑料有限公司 | Bearing cover |
| DE102012209121A1 (en) * | 2012-05-30 | 2013-12-05 | Aktiebolaget Skf | Sealing unit for sealing bearing against e.g. dirt, has sealing element that is fixed to another sealing element |
| CN103850723A (en) * | 2012-11-29 | 2014-06-11 | 哈尔滨中盈电力设备有限公司 | Combination ring sealing device |
| CN203516735U (en) * | 2013-08-20 | 2014-04-02 | 上海新建重型机械有限公司 | Oil deflector device of sliding shoe mill |
| CN204312546U (en) * | 2014-12-04 | 2015-05-06 | 哈尔滨三源汽轮机设备制造有限责任公司 | A kind of bearing shell flinger ring |
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2014
- 2014-12-04 CN CN201410724732.5A patent/CN105134782B/en active Active
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