CN109869411B - High-speed rotor system with elliptical bearing and four-oil-blade bearing coaxially and four-support - Google Patents
High-speed rotor system with elliptical bearing and four-oil-blade bearing coaxially and four-support Download PDFInfo
- Publication number
- CN109869411B CN109869411B CN201910283846.3A CN201910283846A CN109869411B CN 109869411 B CN109869411 B CN 109869411B CN 201910283846 A CN201910283846 A CN 201910283846A CN 109869411 B CN109869411 B CN 109869411B
- Authority
- CN
- China
- Prior art keywords
- bearing
- rotor
- speed
- oil
- elliptical
- 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
Links
- 238000009434 installation Methods 0.000 claims description 31
- 238000000034 method Methods 0.000 claims description 7
- 238000006073 displacement reaction Methods 0.000 description 6
- 230000005484 gravity Effects 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 238000013016 damping Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
The invention discloses a high-speed rotor system with an elliptic bearing and four oil-blade bearings coaxially supported by four, and relates to a variable-speed clutch. The high-speed rotor system comprises a high-speed rotor body, wherein the high-speed rotor body is formed by connecting an input assembly rotor body and an output assembly rotor body, the high-speed rotor system further comprises two elliptical bearings and two four-oil-blade bearings, the input assembly rotor body is supported by the two elliptical bearings, and the output assembly rotor body is supported by the two four-oil-blade bearings. The invention relates to the technical field of rotor system structures.
Description
Technical Field
The invention relates to a rotor system, in particular to a high-speed rotor system with an elliptical bearing and four oil vane bearings coaxially and four-supported.
Background
When mechanical equipment uses dynamic pressure sliding bearings, the phenomenon that shafting and equipment body vibrate exists in actual operation due to small oil film rigidity or large calculation error, and increasingly-promoted application requirements of various industries also put more and more strict requirements on vibration indexes of the mechanical equipment. For a high-speed rotor system of a speed-increasing type speed-changing clutch, the linear speed of a sliding bearing for supporting a rotor is generally more than 60m/s, the maximum linear speed can be close to 80m/s, the avoidance rate of a rated rotating speed relative to the critical rotating speed of the rotor is designed to have certain requirements, and the radial vibration displacement data of a shaft and the vibration displacement data of a speed-changing clutch box body, which are operated in an engaged or disengaged state of the high-speed rotor system, have strict index requirements.
Because the high-speed rotor can be divided into an input assembly rotor and an output assembly rotor in a disengaged state, four fulcrums are required to be arranged on the two rotors which are integrally connected. In order to meet the requirements of safe and stable operation of the input assembly and the output assembly in the speed change clutch in the state of disengaging and engaging the high-speed rotor, the sliding bearing for supporting the rotor needs to meet the static index (such as the highest temperature of a bearing oil film and the minimum oil film thickness) and the dynamic performance index (such as the rigidity of the bearing oil film and the damping of the bearing oil film). However, for a high-speed rotor system of a speed-changing clutch, the input assembly rotor does not transmit power to be in an idle state in the process of increasing the speed before the clutch is engaged, and the sliding support bearing is only acted by the gravity of the rotor, so that the bearing is in a high-speed light-load state; after the clutch is engaged, the whole elliptical bearing of the high-speed rotor is in a high-speed heavy-load working state, and the four-oil-blade bearing is in a high-speed light-load working state.
Therefore, the bearing type selection, design and installation modes of four fulcrums of the high-speed rotor system of the speed change clutch are key for ensuring safe and stable operation of the high-speed rotor system of the speed change clutch. The existing four fulcrums are supported by adopting a round bearing, the rigidity and damping of the round bearing are relatively small, the avoidance rate of the critical rotation speed of the rotor is too small, the radial vibration displacement of a shaft running in the joint or the disconnection state of a high-speed rotor system is too large, and the problems of unit resonance and the like occur.
Disclosure of Invention
The invention aims to solve the problems that the avoidance rate of the rotating speed of a high-speed rotor system of a speed change clutch relative to the critical rotating speed of a rotor is too small, the radial vibration displacement of a shaft operated in an engaged or disengaged state of the high-speed rotor system is too large, and unit resonance occurs, and further provides a high-speed rotor system with an elliptic bearing and four oil vane bearings which are coaxial and four-support.
The technical scheme adopted by the invention for solving the problems is as follows:
the high-speed rotor system comprises a high-speed rotor body, wherein the high-speed rotor body is formed by connecting an input assembly rotor body and an output assembly rotor body, the high-speed rotor system further comprises two elliptical bearings and two four-oil-blade bearings, the input assembly rotor body is supported by the two elliptical bearings, and the output assembly rotor body is supported by the two four-oil-blade bearings.
The beneficial effects of the invention are as follows:
the pinion shaft and the input assembly are connected into an input assembly rotor integral structure, and an elliptical bearing is adopted for supporting; the output shaft and the output assembly are connected into an output assembly rotor integral structure, and are supported by four oil leaf bearings. The input assembly rotor body and the output assembly rotor body are integrated into a high-speed rotor body structure in a clutch engagement state.
In the clutch release state, the integral four-oil-blade bearing of the rotor of the output assembly is in a high-speed light-load working state; in the clutch engagement process, the elliptical bearing of the whole input rotor assembly is in a high-speed light-load working state; after the clutch is engaged, the whole elliptical bearing of the high-speed rotor is in a high-speed heavy-load working state, and the four-oil-blade bearing is in a high-speed light-load working state. Therefore, the invention solves the technical problems of the prior art that the avoidance rate of the designed rated rotating speed of the high-speed rotor system of the speed change clutch relative to the critical rotating speed of the rotor is too small, and the radial vibration displacement of the shaft running in the engaged or disengaged state of the high-speed rotor system is too large.
Drawings
FIG. 1 is a schematic diagram of a transmission system of the present invention;
FIG. 2 is a schematic diagram of the structure of the present invention;
FIG. 3 is a schematic view of the installation of a four-lobe bearing without an installation angle of the elliptical bearing;
FIG. 4 is a schematic view of the elliptical bearing installed without an installation angle;
FIG. 5 is a schematic view of a four-lobe bearing installation with an elliptical bearing having an installation angle;
fig. 6 is a schematic view of the elliptical bearing installed with the elliptical bearing installed at an angle.
Detailed Description
The first embodiment is as follows: referring to fig. 1 and 2, a high-speed rotor system with four coaxial supports of an elliptic bearing and a four-lobe bearing according to the present embodiment is described, including a high-speed rotor body 11, where the high-speed rotor body 11 is formed by connecting an input component rotor body 8 and an output component rotor body 9, and is characterized in that: the high-speed rotor system further comprises two elliptical bearings 6 and two four-lobe bearings 7, the input assembly rotor body 8 is supported by the two elliptical bearings 6, and the output assembly rotor body 9 is supported by the two four-lobe bearings 7.
Pinion shaft 1 and input assembly 2 are coupled as an input assembly rotor monolith 8, and output assembly 3 and output shaft 4 are coupled as an output assembly rotor monolith 9; the input assembly 2 and the output assembly 3 belong to a clutch integral 10, and the working state of the clutch integral 10 is divided into an engagement state and a disengagement state. In the engaged state of the clutch body 10, the input assembly rotor body 8 and the output assembly rotor body 9 are integrated into a high-speed rotor body 11 to operate in combination; the clutch pack 10 is in the disengaged state and the output assembly rotor 9 is operated alone. The elliptical bearing 6 can adapt to two working states of high-speed heavy load and high-speed light load. The four-oil-blade bearing 7 can adapt to the working state of high-speed light load.
In the process of disengaging the whole clutch 10, the rotation speed of the large gear shaft 5 starts to be increased, the small gear shaft 1 is driven by meshing and simultaneously increased, and before the whole clutch is not combined, the power transmitted to the large gear shaft 5 by external equipment is negligible, so that the meshing force is not transmitted to the support bearing of the whole input assembly rotor 8, the oval bearing 6 is only influenced by the gravity of the whole input assembly rotor 8, and the clutch needs to be continuously operated for a period of time in the process of increasing the speed, and the clutch is in a high-speed light-load working state; after the clutch body 10 is engaged, the large gear shaft 5 transmits power to the small gear shaft 1, and then to the clutch body 10 and the output shaft 4 for output to external equipment, at the moment, meshing force action is generated between the large gear 5 and the small gear 1, and the meshing force is transmitted to the elliptical bearing 6 supporting the input rotor body 8 and runs at the rated rotation speed, so that the clutch body is in a high-speed heavy-load working state; the clutch assembly 10 is in a high-speed light-load state in which the output shaft 4 only transmits torque, has only rotor gravity influence on the four-lobe bearing 7 and continuously works at a rated rotation speed in a disengaging and engaging state. The dynamic performance index of the bearing of the elliptic bearing 6 in the two working states of high-speed light load and high-speed heavy load can meet the requirements of various vibration indexes of the system, the dynamic performance index of the bearing of the four-oil-blade bearing 7 in the working state of high-speed light load can meet the requirements of various vibration indexes of the system, and the lubrication heat power consumption and the overall temperature of the four-oil-blade bearing 7 used at the moment are lower than those of other bearing types. The designed rated rotating speed of the high-speed rotor system is larger than the avoidance rate of the critical rotating speed of the rotor, the radial vibration displacement of the shaft operated in the engaged or disengaged state of the high-speed rotor system is smaller, and the operation state is safe and stable.
The internal molded line of the elliptical bearing 6 is elliptical, namely when the center of the rotor is coincident with the theoretical installation center of the elliptical bearing 6, the gap of the bearing close to the oil inlet is larger, and the gap far from the oil inlet is smaller; the inner molded line of the four-oil-leaf bearing 7 is also not circular, and when the rotor is coincident with the theoretical installation center of the four-oil-leaf bearing 7, the bearing clearance near the oil inlet is larger, and the clearance far from the oil inlet is smaller. In order to ensure that the whole input assembly rotor 8 and the whole output assembly rotor 9 can be located at the bottoms of the sliding support bearings in a stop state, and the sliding support bearings run safely and stably in and after the joint process, the theoretical clearance values of the front sliding support bearing and the rear sliding support bearing should be kept consistent.
The second embodiment is as follows: the present embodiment is described with reference to fig. 1 and 2, in which the input assembly rotor body 8 includes an input assembly 2 and a pinion shaft 1, the pinion shaft 1 and the input assembly 2 are coupled, and two elliptical bearings 6 are mounted at both ends of the pinion shaft 1. Other components and connection relationships are the same as those of the first embodiment.
And a third specific embodiment: the present embodiment is described with reference to fig. 3 and 4, in which the output assembly rotor assembly 9 includes an output assembly 3 and an output shaft 4, the output shaft 4 is coupled to the output assembly 3, and two four-lobe bearings 7 are installed at both ends of the output shaft 4. Other components and connection relationships are the same as those of the first embodiment.
The specific embodiment IV is as follows: the present embodiment will be described with reference to fig. 5 and 6, in which the input assembly 2 and the output assembly 3 can be engaged or disengaged to form the clutch pack 10. The clutch body 10 is operated in both an engaged and a disengaged state. Other compositions and connection relationships are the same as those of the second or third embodiment.
Fifth embodiment: in the present embodiment, when the elliptical bearing 6 has no installation angle, the total value a1 of the vertical installation clearance between the elliptical bearing 6 and the whole input assembly rotor is equal to the total value a2 of the vertical installation clearance between the four-oil-blade bearing 7 and the whole output assembly rotor, as described with reference to fig. 3 to 4.
When the elliptical bearing 6 has no installation angle, the total value a1 of the vertical installation clearance between the elliptical bearing 6 and the input assembly rotor whole 8 and the total value a2 of the vertical installation clearance between the four-oil-blade bearing 7 and the output rotor whole 9 are required to be ensured to be equal; the diameter sizes of the input rotor assembly whole 8 and the output rotor assembly whole 9 at the four sliding support bearings are equal; at the same time, the theoretical installation center O1 of the two elliptic bearings 6 in the speed change clutch box body and the theoretical installation center O2 of the two four-oil-leaf bearings 7 in the speed change clutch box body are ensured to be on the same straight line through processing.
Other components and connection relationships are the same as those of the first embodiment.
Specific embodiment six: in the present embodiment, when the elliptical bearing 6 has an installation angle, the total value a1 of the vertical installation gap between the elliptical bearing 6 and the input assembly rotor body 8 is equal to the total value a2 of the vertical installation gap between the four-oil-blade bearing 7 and the output assembly rotor body, as described with reference to fig. 5 to 6.
When the elliptical bearing 6 has an installation angle, a total value a1 of a vertical installation gap between the elliptical bearing 6 and the input assembly rotor body 8 is required to be calculated according to a molded line formula of the elliptical bearing 6 at an installation angle beta, and the total value a2 of the vertical installation gap between the four-oil-blade bearing 7 and the output rotor body 9 is equal to the total value a1 of the vertical installation gap; the diameter sizes of the input rotor assembly whole 8 and the output rotor assembly whole 9 at the four sliding support bearings are equal; at the same time, the theoretical installation center O1 of the two elliptic bearings 6 in the speed change clutch box body and the theoretical installation center O2 of the two four-oil-leaf bearings 7 in the speed change clutch box body are ensured to be on the same straight line through processing. Other components and connection relationships are the same as those of the first embodiment.
Seventh embodiment: the present embodiment will be described with reference to fig. 3 to 6, in which the installation centers O1 of the two elliptical bearings 6 and the installation centers O2 of the two four-lobe bearings 7 are aligned. The theoretical values of the diameters of the rotors supported by the four sliding support bearings are equal, and meanwhile, the theoretical clearance values of the four sliding support bearings are equal, namely, the theoretical height positions of the input assembly rotor body 8 and the output assembly rotor body 9, where the clutch is disengaged in a stop state, are on the same straight line, are not influenced by the installation angle of the elliptical bearing 6, so that the coaxiality of the high-speed rotor body in the operation process is ensured, and the operation safety and stability of a high-speed rotor system are further ensured.
Other compositions and connection relationships are the same as those of the fifth or sixth embodiment.
Eighth embodiment: referring to fig. 3 to 6, the present embodiment is described in which the axial diameter dimension of the input assembly rotor body 8 at the support of the elliptical bearing 6 is equal to the axial diameter dimension of the output assembly rotor body 9 at the support of the four-lobe bearing 7.
The arrangement is such that the input assembly rotor body 8 and the output assembly rotor body 9 can sit at the bottoms of the elliptical bearing 6 and the four-oil-blade bearing 7 in a stop state, and the operation is safe and stable during and after the engagement.
Other compositions and connection relationships are the same as those of the fifth or sixth embodiment.
The present invention is not limited to the preferred embodiments, but is capable of modification and variation in detail, and other embodiments, such as those described above, of making various modifications and equivalents will fall within the spirit and scope of the present invention.
Claims (1)
1. The utility model provides an oval bearing and coaxial four high-speed rotor system who supports of four oil leaf bearings, it includes high-speed rotor whole (11), high-speed rotor whole (11) are connected by input subassembly rotor whole (8) and output subassembly rotor whole (9) and are constituteed, its characterized in that: the high-speed rotor system further comprises two elliptical bearings (6) and two four-oil-blade bearings (7), the input assembly rotor whole (8) is supported by the two elliptical bearings (6), and the output assembly rotor whole (9) is supported by the two four-oil-blade bearings (7);
the input assembly rotor whole (8) comprises an input assembly (2) and a pinion shaft (1), the pinion shaft (1) is connected with the input assembly (2), and two elliptical bearings (6) are arranged at two ends of the pinion shaft (1);
the output assembly rotor whole (9) comprises an output assembly (3) and an output shaft (4), the output shaft (4) is connected with the output assembly (3), and two four-oil-leaf bearings (7) are arranged at two ends of the output shaft (4);
the shaft diameter of the input assembly rotor whole (8) at the supporting position of the elliptical bearing (6) is equal to that of the output assembly rotor whole (9) at the supporting position of the four-oil-vane bearing (7);
the input assembly (2) and the output assembly (3) form a clutch whole (10);
when the elliptical bearing (6) has no installation angle, the total value (a 1) of the vertical installation clearance between the elliptical bearing (6) and the input assembly rotor body (8) is equal to the total value (a 2) of the vertical installation clearance between the four-oil-blade bearing (7) and the output assembly rotor body (9);
when the elliptical bearing (6) has an installation angle, a vertical installation clearance total value (a 1) of the elliptical bearing (6) and the input assembly rotor whole (8) is calculated according to a molded line formula of the elliptical bearing (6), and the value is equal to a vertical installation clearance total value (a 2) of the four-oil-leaf bearing (7) and the output assembly rotor whole (9);
the installation centers (O1) of the two elliptic bearings (6) and the installation centers (O2) of the two four-oil-leaf bearings (7) are positioned on the same straight line;
in the state that the clutch is in a disengaged state, the four-oil-blade bearing (7) of the output assembly rotor body (9) is in a high-speed light-load working state;
in the process of the engagement of the clutch whole (10), an elliptical bearing (6) of the input assembly rotor whole (8) is in a high-speed light-load working state;
after the clutch whole (10) is connected, the elliptical bearing (6) of the high-speed rotor whole (11) is in a high-speed heavy-load working state, and the four-oil-blade bearing (7) is in a high-speed light-load working state.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910283846.3A CN109869411B (en) | 2019-04-09 | 2019-04-09 | High-speed rotor system with elliptical bearing and four-oil-blade bearing coaxially and four-support |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910283846.3A CN109869411B (en) | 2019-04-09 | 2019-04-09 | High-speed rotor system with elliptical bearing and four-oil-blade bearing coaxially and four-support |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109869411A CN109869411A (en) | 2019-06-11 |
| CN109869411B true CN109869411B (en) | 2024-03-26 |
Family
ID=66922389
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910283846.3A Active CN109869411B (en) | 2019-04-09 | 2019-04-09 | High-speed rotor system with elliptical bearing and four-oil-blade bearing coaxially and four-support |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109869411B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DK3834922T3 (en) * | 2019-12-11 | 2022-08-22 | Alfa Laval Corp Ab | SHAFT BRACKET TO SUPPORT AN AGITATOR SHAFT AND AN AGITATOR |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102207426A (en) * | 2011-03-17 | 2011-10-05 | 北京必可测科技有限公司 | Shafting state monitoring method for rotary machine |
| CN102808666A (en) * | 2012-08-03 | 2012-12-05 | 上海电气电站设备有限公司 | Shafting support structure of online-disconnected double-cylinder steam turbine |
| CN204213188U (en) * | 2014-10-11 | 2015-03-18 | 沈阳鼓风机集团齿轮压缩机有限公司 | Four oily rachises are held |
| WO2016076750A1 (en) * | 2014-11-11 | 2016-05-19 | Фонд Поддержки Научной, Научно-Технической И Инновационной Деятельности "Энергия Без Границ", (Фонд "Энергия Без Границ") | Turbine-generator shaft train and support bearing or thrust and support bearing for same |
| CN206972762U (en) * | 2017-08-03 | 2018-02-06 | 中冶赛迪工程技术股份有限公司 | The oval filmatic bearing structure of Laying head |
| CN209743379U (en) * | 2019-04-09 | 2019-12-06 | 哈尔滨广瀚动力传动有限公司 | Elliptical bearing and four-oil-vane bearing coaxial four-support high-speed rotor system |
-
2019
- 2019-04-09 CN CN201910283846.3A patent/CN109869411B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102207426A (en) * | 2011-03-17 | 2011-10-05 | 北京必可测科技有限公司 | Shafting state monitoring method for rotary machine |
| CN102808666A (en) * | 2012-08-03 | 2012-12-05 | 上海电气电站设备有限公司 | Shafting support structure of online-disconnected double-cylinder steam turbine |
| CN204213188U (en) * | 2014-10-11 | 2015-03-18 | 沈阳鼓风机集团齿轮压缩机有限公司 | Four oily rachises are held |
| WO2016076750A1 (en) * | 2014-11-11 | 2016-05-19 | Фонд Поддержки Научной, Научно-Технической И Инновационной Деятельности "Энергия Без Границ", (Фонд "Энергия Без Границ") | Turbine-generator shaft train and support bearing or thrust and support bearing for same |
| CN206972762U (en) * | 2017-08-03 | 2018-02-06 | 中冶赛迪工程技术股份有限公司 | The oval filmatic bearing structure of Laying head |
| CN209743379U (en) * | 2019-04-09 | 2019-12-06 | 哈尔滨广瀚动力传动有限公司 | Elliptical bearing and four-oil-vane bearing coaxial four-support high-speed rotor system |
Non-Patent Citations (1)
| Title |
|---|
| 轴系稳定性与支承轴承的关系;徐龙祥 等;南京航空航天大学学报;第25卷(第02期);168-175 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109869411A (en) | 2019-06-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN202048122U (en) | Liquid viscosity speed regulation clutch | |
| CN109869411B (en) | High-speed rotor system with elliptical bearing and four-oil-blade bearing coaxially and four-support | |
| CN203027079U (en) | Flexible start motor | |
| CN209743379U (en) | Elliptical bearing and four-oil-vane bearing coaxial four-support high-speed rotor system | |
| CN205101520U (en) | High -speed gear box of wet friction clutch | |
| CN102401106B (en) | Megawatt-level closed planet differential motion wind power speed increasing box | |
| CN201858326U (en) | Double-turbine hydrodynamic torque converter | |
| CN108006197A (en) | A kind of gear axis mechanism for high speed driving unit | |
| CN106481736A (en) | Double motive power driving gear-boxes and freewheel clutch integrated | |
| CN201715220U (en) | Cycloid rotor lubricant pump | |
| CN206280440U (en) | Double motive power driving gear-boxes and freewheel clutch are integrated | |
| CN102410312A (en) | Gear and thin-wall disc combined type coupling | |
| CN212803677U (en) | Fan unit | |
| CN213478965U (en) | Flexible ripple coupling | |
| CN201335111Y (en) | Limit-torque clutch with bearing | |
| CN208203847U (en) | flexible speed change clutch soft start transmission device | |
| CN202612398U (en) | Outer ring of integrated special-shaped crossed roller bearing for miniature reducer | |
| CN203926630U (en) | Gearbox | |
| CN221054251U (en) | Shafting assembly for high-speed heavy-load gearbox and high-speed heavy-load gearbox | |
| CN207485989U (en) | A kind of guide wheel locking torque converter | |
| CN202402471U (en) | Integrated irregular crossed roller bearing for mini-type reduction gear | |
| CN202402473U (en) | Device for connecting inner rings and outer rings of integrated abnormally-shaped intercrossed roller bearing for micro speed reducer | |
| CN105587846A (en) | Speed reducing device and fracturing equipment | |
| CN202301495U (en) | Rear power takeoff transmission component of diesel engine | |
| CN115126553A (en) | Aviation air turbine starter transmission system easy to lubricate |
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 |