PARALLEL BEARING AND ROTOR SYSTEM

Abstract

A parallel bearing includes a rotary shaft bearing and a stator bearing, wherein the rotary shaft bearing is a contact bearing, and the rotary shaft bearing is sleeved on a rotary shaft; and the stator bearing is a non-contact bearing, the stator bearing is sleeved on the rotary shaft bearing, and a clearance is provided between the stator bearing and the rotary shaft bearing. The parallel bearing is cost-effective, reduces the relative rotational speed of each stage of bearing, breaks through the limitation of the theoretical DN factor and has the low dependency on the lubricating oil. In the rotor system having the parallel bearing, rotational speeds of multiple parallel bearings on the same rotary shaft can be adaptively adjusted to achieve the synchronous rotation, and thus the rotor system has the desired stability in high-speed operation.

Claims

1. A parallel bearing, comprising a rotary shaft bearing and a stator bearing, wherein the rotary shaft bearing is a contact bearing, and the rotary shaft bearing is sleeved on a rotary shaft; and the stator bearing is a non-contact bearing, the stator bearing is sleeved on the rotary shaft bearing, a clearance is provided between an inner wall of the stator bearing and an outer wall of the rotary shaft bearing, and the stator bearing is fixed on a stator.

2. The parallel bearing according to claim 1, wherein the parallel bearing further comprises a bearing shell, the bearing shell covers a first end surface and a periphery of the stator bearing, a bearing end cover is provided on a second end surface of the stator bearing and fixed to the bearing shell, the bearing shell and/or the bearing end cover is fixed on the stator, and the stator bearing is peripherally fixed to the bearing shell or the bearing end cover.

3. The parallel bearing according to claim 1, wherein the rotary shaft bearing is a ball bearing, a ceramic bearing or a polytetrafluoroethylene (PTFE) bearing.

4. The parallel bearing according to claim 1, wherein the rotary shaft bearing is a single-row, double-row or multi-row ball bearing.

5. The parallel bearing according to claim 1, wherein the rotary shaft bearing is two angular contact ball bearing opposite to each other, and a preloaded spring is provided between outer rings of the two angular contact ball bearings.

6. The parallel bearing according to claim 1, wherein the stator bearing is an air bearing, an oil film floating ring bearing (FRB) or a tilting pad bearing.

7. The parallel bearing according to claim 6, wherein the stator bearing is the air bearing, an air chamber is provided on a peripheral surface of the stator bearing, an air hole is formed in a bottom of the air chamber, the air hole comprises a first end communicating with the air chamber and a second end connected to the clearance between the inner wall of the stator bearing and the outer wall of the rotary shaft bearing, and a rubber ring is further provided between the stator bearing and the bearing shell.

8. The parallel bearing according to claim 1, wherein the rotary shaft bearing is a ball bearing, and the stator bearing is an air bearing.

9. The parallel bearing according to claim 1, wherein the parallel bearing further comprises at least one intermediate bearing, the at least one intermediate bearing is a contact bearing, the at least one intermediate bearing is sleeved between the rotary shaft bearing and the stator bearing, and a clearance is provided between the stator bearing and the at least one intermediate bearing.

10. The parallel bearing according to claim 9, wherein the at least one intermediate bearing is a ball bearing.

11. A rotor system, wherein the rotor system comprises two parallel bearings according to claim 1, wherein the two parallel bearings are a first parallel bearing and a second parallel bearing, and the first parallel bearing and the second parallel bearing are pairwise sleeved on a rotary shaft.

12. The rotor system according to claim 11, wherein the rotor system further comprises a turbine, a compressor, a motor and a thrust bearing; and the rotary shaft passes through the thrust bearing, the first parallel bearing, the motor, the second parallel bearing, the compressor and the turbine, wherein the thrust bearing, the first parallel bearing, the motor, the second parallel bearing, the compressor and the turbine are arranged sequentially, the rotary shaft rotates in a stator of the thrust bearing, the first parallel bearing, a stator of the motor and the second parallel bearing, and the rotary shaft is fixedly connected to a thrust collar of the thrust bearing, a worm gear of the turbine, and a compression wheel of the compressor.

13. The rotor system according to claim 11, wherein the parallel bearing further comprises at least one intermediate bearing, the at least one intermediate bearing is a contact bearing, the at least one intermediate bearing is sleeved between the rotary shaft bearing and the stator bearing, and a clearance is provided between the stator bearing and the at least one intermediate bearing.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0026] FIG. 1 is a schematic structural view of a parallel bearing according to Embodiment 1 of the present disclosure.

[0027] FIG. 2 is a structural side view of a parallel bearing according to Embodiment 1 of the present disclosure.

[0028] FIG. 3 is a schematic structural view of a parallel bearing according to Embodiment 2 of the present disclosure.

[0029] FIG. 4 is a schematic structural view of a rotor system having a parallel bearing.

[0030] FIG. 5 is a schematic structural view illustrating that a parallel bearing is provided on two ends of a shaft according to the present disclosure.

[0031] FIG. 6 is a schematic view of a positional relationship of a bearing when a rotary shaft is started according to the present disclosure.

[0032] FIG. 7 is a schematic view of a positional relationship of a bearing when a rotary shaft is stable according to the present disclosure.

[0033] FIG. 8 is a schematic structural view illustrating that a rotary shaft bearing uses an angular contact ball bearing according to Embodiment 3 of the present disclosure.

[0034] FIG. 9 is a schematic structural view illustrating that a rotary shaft bearing uses an integral multi-layer bearing according to the present disclosure.

DETAILED DESCRIPTION OF THE EMBODIMENTS

[0035] The following clearly and completely describes the technical solutions of the present disclosure with reference to accompanying drawings. Apparently, the described embodiments are merely some rather than all of the embodiments of the present disclosure.

[0036] The present disclosure provides a parallel bearing, provided on a rotary shaft 100 and configured to radially support the rotary shaft 100.

Embodiment 1

[0037] Referring to FIG. 1 and FIG. 2, the parallel bearing in the embodiment includes a rotary shaft bearing 1 and a stator bearing 2. The rotary shaft bearing 1 is sleeved on the rotary shaft 100; and the stator bearing 2 is sleeved on the rotary shaft bearing 1, with a certain clearance from an outer wall of the rotary shaft bearing 1.

[0038] A bearing shell 4 covers one end surface and a periphery of the stator bearing 2, a bearing end cover 5 is provided on the other end surface of the stator bearing 2 and abutted against and fixed to the bearing shell 4, the bearing shell 4 and the bearing end cover 5 are fixed on a motor stator, and the stator bearing 2 is peripherally fixed to the bearing shell 4 or the bearing end cover 5.

[0039] An air chamber 22 is provided on a peripheral surface of the stator bearing 2, an air hole 23 is formed in a bottom of the air chamber 22, the air hole 23 includes one end communicating with the air chamber 22 and the other end connected to the clearance between the stator bearing 2 and the rotary shaft bearing 1, and a rubber ring 21 is further provided between the stator bearing 2 and the bearing shell 4.

[0040] The stator bearing 2 is peripherally fixed to the bearing shell 4 or the bearing end cover 5 through a pin connection, a dowel connection or a key connection.

[0041] The pin may be fixed on the end surface of the stator bearing 2, and a corresponding accommodation hole is formed in the bearing shell 4.

[0042] The pin may be fixed on an end surface of the bearing shell 4 toward the stator bearing 2, and a corresponding accommodation hole is formed in the stator bearing 2.

[0043] The pin or the dowel may be radially provided along the bearing shell 4 from the periphery of the bearing shell 4, the pin includes one end fixed in the bearing shell 4 and the other end inserted into the periphery of the stator bearing 2, and a corresponding accommodation hole is formed in the periphery of the stator bearing 2.

[0044] The key may be fixed on the end surface of the stator bearing 2 or integrally formed with one end surface of the stator bearing 2, and a corresponding key slot is formed in the bearing shell 4.

[0045] The key may be fixed on the inner radial surface of the bearing shell 4, or integrally formed with the inner radial surface of the bearing shell 4, and a corresponding key slot is formed in the stator bearing 2.

[0046] Referring to FIG. 6, when the rotary shaft 100 is started, the rotary shaft bearing 1 sleeved on the rotary shaft 100 contacts the bottom of the stator bearing 2; and along with rotation of the rotary shaft 100, the inner ring of the rotary shaft bearing 1 is driven to rotate. At the same time, the stator bearing 2 is gradually separated from the outer ring of the rotary shaft bearing 1 due to an air film or an oil film, and the rotary shaft bearing 1 rotates eccentrically in the stator bearing 2. When the rotary shaft 100 rotates stably at a high speed, the rotary shaft 100 and the rotary shaft bearing 1 are coaxial, and rotate eccentrically around a circumference in the stator bearing 2, as shown in FIG. 7. Meanwhile, the outer ring of the rotary shaft bearing 1 rotates automatically.

[0047] Further, referring to FIG. 1, the present disclosure uses a ball bearing as the rotary shaft bearing 1, and an air bearing as the stator bearing 2.

[0048] When the rotary shaft 100 rotates, the inner ring of the ball bearing is driven to rotate, and an air film is formed between the outer ring of the rolling bearing and the air bearing. Fixed on the stator, the air bearing has a relative rotational speed with the outer ring of the rolling bearing.

[0049] For the original ball bearing, while the shaft diameter is fixed, the rotary shaft bearing originally provided on the shaft is implemented as follows: Supposing that the ball bearing has a rotational speed of V2 on the inner ring and a rotational speed of V0 on the outer ring during rotation of the rotary shaft, as the outer ring is fixed on the stator, the V0 is approximate to 0, and thus the relative rotational speed of the outer ring of the ball bearing is n=V2−V0.

[0050] After the parallel bearing of the present disclosure is used, supposing that the ball bearing has a rotational speed of V2 on the inner ring and a rotational speed of V1 on the outer ring and the air bearing has a rotational speed of V0 during rotation of the rotary shaft 100, as the air bearing is fixed on the stator, the V0 is approximate to 0, and thus the speed difference of the outer ring of the ball bearing relative to the inner ring is a=V2−V1, and the speed difference relative to the air bearing is b=V1−V0, a and b being less than n. Therefore, the relative rotational speed between the inner and outer rings of the rolling bearing is reduced, namely, under the same condition, the actual DN factor is reduced and the common lubricating grease can meet the requirements.

[0051] By the same reasoning, no matter how many rolling bearings are sequentially sleeved in parallel on the rotary shaft bearing 1, the actual DN factor is not too large, and thus the shaft diameter D and the rotational speed N of the bearing are decoupled. Therefore, the parallel bearing provided by the present disclosure is applied to working conditions with the large shaft diameter and the high rotational speed. Moreover, the damping and rigidity of the parallel bearing provided by the present disclosure are not lower than those of the single bearing, specifically, the damping of the parallel bearing=the damping of the air bearing+the damping of each rubber ring on the bearing, and the rigidity of the parallel bearing=the rigidity of the air bearing.

Embodiment 2

[0052] Referring to FIG. 3, the parallel bearing in the embodiment includes a rotary shaft bearing 1, a stator bearing 2 and an intermediate bearing 6.

[0053] On the basis of Embodiment 1, the intermediate bearing 6 is sleeved on the rotary shaft bearing 1 (or multiple intermediate bearings 6 are sequentially sleeved and the intermediate bearings 6 are coaxial); and the stator bearing 2 is sleeved on an outermost intermediate bearing 6, with a certain clearance from an outer wall of the outermost intermediate bearing 6.

[0054] Specifically, the intermediate bearing 6 is a ball bearing. Referring to FIG. 8, when the rotary shaft 100 is started, the outer ring of the intermediate bearing 6 contacts the bottom of the stator bearing 2; and along with rotation of the rotary shaft 100, the inner ring of the rotary shaft bearing 1 is driven to rotate. At the same time, the outer ring of the intermediate bearing 6 is gradually separated from the outer ring of the rotary shaft bearing 1 due to an air film or an oil film, and the rotary shaft 100 drives the rotary shaft bearing 1 and the intermediate bearing 6 to rotate eccentrically in the stator bearing 2. When the rotary shaft 100 rotates stably at a high speed, the rotary shaft 100, the rotary shaft bearing 1 and the intermediate bearing 6 are coaxial, and rotate eccentrically around a circumference in the stator bearing 2. Meanwhile, the outer ring of the rotary shaft bearing 1, and the inner ring and outer ring of the intermediate bearing 6 rotate automatically.

[0055] Further, the ball bearing or the roller bearing for the rotary shaft bearing 1 in Embodiment 1 and Embodiment 2 of the present disclosure is the integral multi-layer bearing, and there are multiple ball layers or roller layers, as shown in FIG. 9.

Embodiment 3

[0056] Referring to FIG. 8, when the rotary shaft bearing 1 in the present disclosure uses the angular contact ball bearing, as the inner ring of the bearing is fixed on the rotary shaft 100, the outer ring, the holder and the ball will move relatively, specifically, proper measures need to be taken as the ball in the bearing is excessively loose.

[0057] The solutions provided by the present disclosure are as follows: A pair of angular contact ball bearings that are opposite to each other are selected, and a preloaded spring is provided between outer rings of the two angular contact ball bearings.

[0058] By adjusting a preload of the spring, the ball is close to or away from the holder, such that the frictional force in the bearing increases or decreases to meet the working condition.

[0059] During specific applications, the parallel bearing provided by the present disclosure may be pairwise provided on the rotary shaft 100. Referring to FIG. 5, when the rotary shaft 100 rotates, the inner ring of the rotary shaft bearing 1 is driven to rotate, and the outer ring of the rotary shaft bearing 1 or the outer ring of the outermost intermediate bearing 6 rotates under the action of the air bearing or the oil film FRB. Rotational speeds of multiple parallel bearings on the same rotary shaft are adaptively adjusted according to the stress to achieve the synchronous rotation.

[0060] The parallel bearing provided by the present disclosure may be applied to working conditions requiring the high-speed rotary shaft, such as the rotor system and the microturbine system.

[0061] As shown in FIG. 4, the present disclosure further provides a rotor system including the above parallel bearing, including: a rotary shaft 100, a turbine 700, a compressor 600, a motor 400, a first parallel bearing 300, a second parallel bearing 500 and a thrust bearing 200; the rotary shaft 100 passes through the thrust bearing 200, the first parallel bearing 300, the motor 400, the second parallel bearing 500, the compressor 600 and the turbine 700 that are arranged sequentially; the rotary shaft 100 rotates in the thrust bearing 200, the first parallel bearing 300, a stator of the motor 400 and the second parallel bearing 500, and the rotary shaft 100 is fixedly connected to a thrust collar 210 of the thrust bearing 200, a worm gear of the turbomachine 700, and a compression wheel of the compressor 600.

[0062] In the above rotor system, the first parallel bearing 300 and the second parallel bearing 500 each are the parallel bearing of the present disclosure; and the rotational speeds of the outer rings of the rotary shaft bearings 1 on the first parallel bearing 300 and the second parallel bearing 500 are adaptive completely depending on the rotation condition, to ensure the reliable rotation of the rotary shaft 100.

[0063] Further, the thrust bearing 200 is a non-contact bearing.

[0064] Further, the thrust bearing 200 is an air bearing, and may specifically be any of a dynamic pressure bearing, a static pressure bearing or a dynamic and static pressure parallel bearing.

[0065] Further, in order to reduce influences on the efficiency of the compressor 600 from heat conduction at the hot end of the worm gear, the worm gear of the turbine 700 may be made of a ceramic material having a lower thermal conductivity coefficient or other materials.

[0066] Preferably, a reinforcing ring is provided between the compressor 600 and the turbine 700.

[0067] In view of dynamic performance of the rotor, the rotary shaft 100 should be as light as possible; and the smaller the diameter of the rotary shaft 100, the lighter the weight. However, such a case imposes higher requirements on strength of the rotary shaft 100 during the high-speed rotation of the rotor system. With the consideration of the dynamic characteristics of the rotor and the strength of the rotary shaft 100, the shaft diameter between the compressor 600 and the turbine 700 is set to be small and the reinforcing ring is provided between the compressor 600 and the turbine 700, to meet requirements on the rigidity of the rotor.

[0068] The rotor system of the present disclosure includes but is not limited to the above arrangements.

[0069] The present disclosure is applied to the microturbines. All bearings are provided in a motor casing, providing that the machining accuracy of the part for providing the stator bearing in the casing is ensured. During assembly, the part for connecting the stator bearing in the casing is clamped once for all. Therefore, the present disclosure reduces the machining accuracy and assembly accuracy of the microturbines, reduces the cost and is applicable to industrial mass production. Meanwhile, the present disclosure implements the compact layout of the microturbines, the short axial length of the rotary shaft, and the desired stability of the rotor system in high-speed operation.

[0070] The above describes the specific implementations of the present disclosure, but is not intended to limit the protection scope of the present disclosure. Those skilled in the art should understand that any modifications or variations made by those skilled in the art without creative efforts still fall within the protection scope of the present disclosure based on the technical solutions of the present disclosure.