CN211398270U - Power plant - Google Patents

Abstract

The present disclosure provides a power plant comprising a rotor and a shaft support assembly for supporting the rotor, the shaft support assembly comprising: a bearing support having a bearing mounting hole; the dynamic pressure gas bearing is arranged in the bearing mounting hole and comprises a bearing shell and a foil assembly arranged in the bearing shell, the foil assembly forms a shaft hole of the dynamic pressure gas bearing, and the rotor is rotatably arranged in the shaft hole; a bearing wear detection apparatus comprising a pressure sensor configured to detect a gas film pressure of a bearing gap between the rotor and the foil assembly to judge a wear state of the hydrodynamic gas bearing from the gas film pressure. The technical scheme disclosed facilitates convenient and low-cost real-time monitoring of the system stability of the power equipment.

Description

Power plant

Technical Field

The disclosure relates to the technical field of bearings, in particular to power equipment.

Background

By virtue of the advantages of no oiliness, high rotating speed, high temperature resistance and the like, the gas bearing is rapidly developed from the 60 th century in 20 th, and has very wide application prospect in power equipment such as high-speed turbines, compressors and the like.

Gas bearings are classified into static pressure gas bearings and dynamic pressure gas bearings according to the mechanism of generation of a lubricating gas film.

The static pressure gas bearing uses an external gas source to supply gas to the bearing to generate pressure bearing load, and the dynamic pressure gas bearing uses a pressure gas film generated by the gas in a wedge-shaped gap between a rotor and the inner surface of the dynamic pressure gas bearing to support the load.

The working principle of the dynamic pressure gas bearing is shown in fig. 1 and 2. Fig. 1 is a partial structural view of a hydrodynamic gas bearing in cooperation with a rotor according to the related art. Fig. 2 is a schematic view showing a principle of generating a dynamic pressure film when the dynamic pressure gas bearing shown in fig. 1 is engaged with a rotor. When the rotor 1 'is operated at a high speed, the center of the rotor 1' is eccentric to the center of the dynamic pressure gas bearing 2 'due to a force, such as gravity, applied to the rotor 1', and a wedge-shaped bearing gap is formed between the inner surface of the dynamic pressure gas bearing 2 'and the rotor 1'. When the rotor 1 'rotates at a high speed, gas with certain viscosity is continuously brought into the wedge-shaped gap due to gas viscosity, the gas continuously enters to enable the gas film to generate certain pressure, and when the gas film pressure is enough to balance the load of the rotor 1', the rotor 1 'is completely separated from the dynamic pressure gas bearing 2', and a dynamic pressure gas film 3 'is formed to support the rotor 1' to rotate.

From the above principle, the hydrodynamic gas bearing is actually one of the sliding bearings, and the key point of the operation is to form a hydrodynamic gas film with sufficient supporting force. In other words, when the rotating speed is low, such as in the starting and stopping processes, a dynamic pressure air film cannot be formed, dry friction occurs between the rotating shaft and the bearing at the moment, the bearing is abraded, the service life of the bearing is influenced by frequent starting and stopping, and the bearing is in failure in severe cases. In addition, other factors can also cause the possibility of bearing failure, such as rotor resonance, excessive unbalance, shaft deformation and the like, and once the bearing fails, the machine cannot work, and even accidents happen in severe cases. Therefore, the running reliability of the bearing is tested in real time, and the method has important significance for ensuring the stable running of the rotor and preventing failure accidents in advance.

The most direct way for testing the operational reliability of the bearing is to adopt a displacement sensor to monitor the amplitude of the rotor in real time, and judge whether the rotor normally operates according to the amplitude of the rotor, but the displacement sensor of the scheme has high price and needs to be provided with a more expensive collector, a display and the like. Therefore, the method is a convenient and low-cost dynamic pressure gas bearing abrasion detection technology and has important significance for improving the reliability of products.

SUMMERY OF THE UTILITY MODEL

The present disclosure provides a power plant including a rotor and a shaft support assembly for supporting the rotor, the shaft support assembly comprising:

a bearing support having a bearing mounting hole;

the dynamic pressure gas bearing is arranged in the bearing mounting hole and comprises a bearing shell and a foil assembly arranged in the bearing shell, the foil assembly forms a shaft hole of the dynamic pressure gas bearing, and the rotor is rotatably arranged in the shaft hole; and

a bearing wear detection apparatus comprising a pressure sensor configured to detect a gas film pressure of a bearing gap between the rotor and the foil assembly to judge a wear state of the hydrodynamic gas bearing from the gas film pressure.

In some embodiments, the bearing housing has a pressure measuring hole communicating a radially inner peripheral surface and a radially outer peripheral surface thereof, and the sensor inlet port of the pressure sensor communicates with the bearing gap through the pressure measuring hole.

In some embodiments, a gas storage cavity is arranged between the hole wall of the bearing mounting hole and the outer peripheral surface of the bearing shell of the dynamic pressure gas bearing, and the pressure measuring hole is communicated with the gas storage cavity;

the sensor air inlet is communicated with the air storage cavity.

In some embodiments, the bearing housing has a plurality of the pressure taps communicating with the same gas storage chamber.

In some embodiments, a plurality of gas storage cavities are axially arranged between the hole wall of the bearing mounting hole and the outer peripheral surface of the bearing shell of the dynamic pressure gas bearing, and each gas storage cavity is respectively communicated with a plurality of pressure measuring holes arranged along the axial direction of the dynamic pressure gas bearing;

the bearing wear detection device comprises a plurality of pressure sensors, and the pressure sensors are communicated with the gas storage cavities respectively.

In some embodiments, the bearing wear detection device includes a plurality of the pressure sensors arranged to detect the gas film pressure of the bearing gap at different positions in the axial direction of the dynamic pressure gas bearing.

In some embodiments, the bearing housing has a bearing air intake hole located at an axially middle portion of the bearing housing, and the plurality of pressure sensors are distributed on both axial sides of the bearing air intake hole.

In some embodiments, the bearing housing has a bearing air inlet hole located at an axial middle portion of the bearing housing, and the power equipment further includes a plurality of seal rings located between the bearing support and the bearing housing and respectively disposed at both sides of the bearing air inlet hole in an axial direction of the dynamic pressure gas bearing.

In some embodiments, the bearing housing has a bearing air inlet hole located in the middle of the bearing housing in the axial direction, the power equipment further includes two comb sealing members disposed at two ends of the bearing housing in the axial direction, each comb sealing member has a shaft sealing hole, a hole wall of the shaft sealing hole is provided with a sealing comb, an end surface of each comb sealing member close to the dynamic pressure gas bearing abuts against a corresponding end surface of the dynamic pressure gas bearing, the rotor is mounted in the shaft sealing hole, and an outer peripheral surface of the rotor is engaged with the sealing comb.

In some embodiments, the portion of the rotor that engages with the comb seal member includes a stepped surface, and the seal comb includes a first-order tooth that engages with an end surface of the stepped surface that is closer to the hydrodynamic gas bearing and a second-order tooth that is located on a side of the first-order tooth that is farther from the hydrodynamic gas bearing.

In some embodiments, a plurality of the shaft support assemblies arranged in an axial direction of the rotor is included.

In some embodiments, the power plant includes a compressor.

Based on this power equipment that the disclosure provided, set up bearing wear detection device, the rotational speed that utilizes the rotor is positive correlation's relation with gas film pressure, and the gas film pressure in the bearing clearance between through pressure sensor detection rotor and the foil subassembly is in order to judge dynamic pressure gas bearing's wearing and tearing state according to gas film pressure, does benefit to the system stability of convenient, with low costs real time monitoring power equipment.

Other features of the present disclosure and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which proceeds with reference to the accompanying drawings.

Drawings

The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the disclosure and together with the description serve to explain the disclosure and not to limit the disclosure. In the drawings:

fig. 1 is a partial structural view of a hydrodynamic gas bearing in cooperation with a rotor according to the related art.

Fig. 2 is a schematic view showing a principle of generating a dynamic pressure film when the dynamic pressure gas bearing shown in fig. 1 is engaged with a rotor.

Fig. 3 is a partially sectional structural schematic view of a power plant of an embodiment of the present disclosure.

Fig. 4 is an enlarged schematic view of a portion I of fig. 3.

Fig. 5 is a schematic perspective view of a bearing housing of the dynamic pressure gas bearing in the power unit shown in fig. 3.

Fig. 6 is a sectional structural view of the bearing housing shown in fig. 5.

Detailed Description

The technical solutions in the embodiments of the present disclosure will be clearly and completely described below with reference to the drawings in the embodiments of the present disclosure, and it is obvious that the described embodiments are only a part of the embodiments of the present disclosure, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the disclosure, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments disclosed herein without making any creative effort, shall fall within the protection scope of the present disclosure.

The relative arrangement of the components and steps, the numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present disclosure unless specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate. In all examples shown and discussed herein, any particular value should be construed as merely illustrative, and not limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.

In the description of the present disclosure, it should be understood that the terms "first", "second", etc. are used to define the components, and are used only for convenience of distinguishing the corresponding components, and if not otherwise stated, the terms have no special meaning, and thus, should not be construed as limiting the scope of the present disclosure.

In the description of the present disclosure, it is to be understood that the directional terms are merely used for convenience in describing the present disclosure and for simplicity in description, and in the absence of any indication to the contrary, these directional terms are not intended to indicate and imply that the referenced device or element must have a particular orientation or be constructed and operated in a particular orientation, and therefore should not be taken as limiting the scope of the present disclosure; the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.

As shown in fig. 3-6, embodiments of the present disclosure provide a power plant. The power plant comprises a rotor 2 and a shaft support assembly for supporting the rotor 2. The power plant is for example a compressor.

As shown in fig. 3 to 6, the shaft support assembly includes a bearing holder 5, a dynamic pressure gas bearing 7, and a bearing wear detection device. The bearing support 5 has a bearing mounting hole. The dynamic pressure gas bearing 7 is mounted in a bearing mounting hole of the bearing holder 5. The hydrodynamic gas bearing 7 includes a bearing housing 71 and a foil assembly 72 disposed within the bearing housing 71. The foil assembly 72 forms the shaft hole of the dynamic pressure gas bearing 7. The rotor 2 is rotatably mounted in a shaft hole of a dynamic pressure gas bearing 7. The bearing wear detection means comprises a pressure sensor 6. The pressure sensor 6 is configured to detect a film pressure in the bearing gap between the rotor 2 and the foil assembly 72 to judge the wear state of the dynamic pressure gas bearing 7 from the film pressure.

As is clear from the characteristics of the dynamic pressure gas bearing, the faster the rotational speed of the rotor, the greater the gas film pressure between the rotor and the dynamic pressure gas bearing, and the greater the supporting force that can be provided, so the rotational speed of the rotor and the gas film pressure of the dynamic pressure gas film have a positive correlation. For a dynamic pressure gas bearing and a rotor with determined structural parameters, the rotating speed of the rotor has a determined relation with the pressure of a gas film, and when the dynamic pressure gas bearing is worn, the pressure of the formed gas film deviates from an original value. In the power equipment of the embodiment of the present disclosure, a bearing wear detection device is provided, the rotation speed of the rotor 2 and the gas film pressure are in positive correlation, and the gas film pressure in the bearing gap between the rotor 2 and the foil assembly 72 is detected by the pressure sensor 6 to judge the wear state of the dynamic pressure gas bearing 7 according to the gas film pressure, so that the system stability of the power equipment can be conveniently monitored in real time with low cost.

As shown in fig. 3 to 6, in the power plant of some embodiments, the bearing housing 71 has a pressure measuring hole 711 communicating the radially inner peripheral surface and the radially outer peripheral surface thereof, and the sensor inlet port of the pressure sensor 6 communicates with the bearing gap through the pressure measuring hole 711.

As shown in fig. 3 to 6, in the power equipment of some embodiments, an air reservoir 51 is provided between the hole wall of the bearing mounting hole and the outer circumferential surface of the bearing housing 71 of the dynamic pressure gas bearing 7. The pressure measuring hole 711 is communicated with the gas storage cavity 51; the sensor inlet of the pressure sensor 6 communicates with the air reservoir 51.

The air inlet of the pressure sensor 6 is communicated with the pressure measuring hole 711 through the air storage cavity 51, so that the stability of the air film pressure measured by the pressure sensor 6 is kept, and the fluctuation of the measured air film pressure is reduced.

As shown in fig. 3 to 6, in the power device of some embodiments, the bearing housing 71 has a plurality of pressure taps 711 communicating with the same air storage chamber 51. One gas storage chamber 51 is communicated with a plurality of pressure measuring holes 711, so that the pressure of each pressure measuring hole 711 can be integrated, and the gas film pressure at the corresponding position can be measured more accurately.

In the power equipment of some embodiments, the bearing wear detection means includes a plurality of pressure sensors 6, and the plurality of pressure sensors 6 detect the gas film pressures of the aforementioned bearing gaps at different positions in the axial direction of the dynamic pressure gas bearing 7.

As shown in fig. 3 to 6, in the power equipment of some embodiments, a plurality of air reserving cavities 51 are provided in the axial direction between the hole wall of the bearing mounting hole and the outer circumferential surface of the bearing housing 71 of the dynamic pressure gas bearing 7. Each gas reserving chamber 51 is communicated with a plurality of pressure measuring holes 711 provided in the axial direction of the dynamic pressure gas bearing 7. The bearing wear detection device includes a plurality of pressure sensors 6, and the plurality of pressure sensors 6 communicate with the plurality of air reservoir chambers 51, respectively.

The adoption of a plurality of pressure sensors can realize the multi-section detection of the air film pressure of the dynamic pressure gas bearing 7 along the axial direction, and is beneficial to more effectively monitoring the stability of power equipment in real time.

As shown in fig. 3 to 6, in the power plant of some embodiments, the bearing housing 71 has a bearing air intake hole 712 located at an axially middle portion of the bearing housing 71, and the plurality of pressure sensors 6 are distributed on both axial sides of the bearing air intake hole 712. Whether the dynamic pressure gas bearing 7 is abraded or not is detected by adopting the multiple pressure sensors 6, so that the integration of multiple pressure data is facilitated, and the condition that the single pressure sensor 6 is interfered to display abnormity is avoided.

As shown in fig. 3 to 6, in the power equipment of some embodiments, the bearing housing 71 has a bearing air intake hole 712 located at an axially middle portion of the bearing housing 71, and the power equipment further includes a sealing device including a plurality of sealing rings 8, and the plurality of sealing rings 8 are located between the bearing holder 5 and the bearing housing 71 of the dynamic pressure gas bearing 7 and are respectively disposed at both sides of the bearing air intake hole 712 in an axial direction of the dynamic pressure gas bearing 7.

The sealing ring 8 is used for sealing the fit clearance between the bearing support 5 and the bearing shell 71 of the dynamic pressure gas bearing 7, so that the leakage of gas in the bearing clearance is avoided, the pressure stability of a gas film is improved, and the sealing ring 8 can provide extra damping for the dynamic pressure gas bearing 7.

As shown in fig. 3 to 6, in the power device of some embodiments, the bearing housing 71 has a bearing intake hole 712 located at an axially middle portion of the bearing housing 71. The power plant also includes two comb seal members provided at both axial ends of the bearing housing 71. The comb tooth sealing part is provided with a shaft sealing hole, and the hole wall of the shaft sealing hole is provided with sealing comb teeth. The end face of the comb tooth sealing component close to the dynamic pressure gas bearing 7 is abutted against the corresponding end face of the dynamic pressure gas bearing 7, the rotor 2 is arranged in the shaft seal hole, and the peripheral face of the rotor 2 is matched with the sealing comb teeth.

The two axial ends of the bearing housing 71 are respectively provided with a comb sealing component, which is beneficial to reducing the sudden change of the airflow pressure of the gas outlet of the dynamic pressure gas bearing 7, and further improves the stability of the gas film distribution and the pressure detection of the dynamic pressure gas bearing 7.

As shown in fig. 3 to 6, in the power plant of some embodiments, the portion of the rotor 2 that engages with the comb sealing part includes a stepped surface, and the sealing comb of the comb sealing part includes first-order teeth that engage with an end surface of the stepped surface that is close to the dynamic pressure gas bearing 7 and second-order teeth that are located on a side of the first-order teeth that is away from the dynamic pressure gas bearing 7.

Rotor 2 sets up the step face with broach seal part complex position, broach seal part corresponds and sets up first order tooth and second order tooth, does benefit to and reduces outlet airflow pressure sudden change, and then more is favorable to improving dynamic pressure gas bearing 7 gas films and distributes and pressure measurement's stability.

In the power plant of some embodiments, a plurality of shaft support assemblies arranged in the axial direction of the rotor 2 are included. As shown in fig. 3, in the embodiment of the present disclosure, one shaft support assembly is disposed at each of both axial ends of the rotor 2. This setting does benefit to and makes the even atress of both sides dynamic pressure gas bearing 7, the pressure measurement of being convenient for.

An embodiment of the present disclosure is further described below with reference to fig. 3 to 6.

As shown in fig. 3 to 6, the power plant of the embodiment of the present disclosure includes a power plant case 1, a rotor 2, a motor stator 3, and two shaft support assemblies. The two shaft support assemblies are respectively supported between the power equipment housing 1 and the rotor 2 and respectively located at the left and right ends of the rotor 2 to support the rotor 2 on the power equipment housing 1.

The power equipment shell 1 is an irregular cavity part, is generally cast, and plays a role in supporting and protecting core components of power equipment.

The motor stator 3 is fixedly arranged inside the power equipment shell 1, and the motor stator 3 is provided with a rotor mounting hole. The rotor 2 is rotatably mounted in a rotor mounting hole of the motor stator 3. The rotor 2 is a shaft and a solid part and forms a motor with the motor stator 3. When the electromagnetic field-driven high-speed rotating rotor works, the rotor 2 rotates at a high speed under the action of the electromagnetic field.

For the purpose of describing the shaft support assembly of the embodiment of the present disclosure in detail, the embodiment is described below by taking only the shaft support assembly located at the left end of the rotor 2 as an example, and the composition of the shaft support assembly located at the right end of the rotor 2, the structure, function, and the like of each component part may refer to the corresponding contents for describing the shaft support assembly located at the left end of the rotor 2.

As shown in fig. 3 to 6, the shaft support assembly includes a first comb seal 4, a bearing support 5, a pressure sensor 6, a dynamic pressure gas bearing 7, a seal ring 8, and a second comb seal 9.

The dynamic pressure gas bearing 7 is mounted in a bearing mounting hole of the bearing holder 5. The hydrodynamic gas bearing 7 includes a bearing housing 71 and a foil assembly 72. The bearing support 5 and the bearing housing 71 are both rotary and hollow parts. As shown in fig. 4, in the present embodiment, the foil assembly 72 includes a support foil 721 located radially inward of the bearing housing 71 and a top foil 722 located radially inward of the support foil 721. The inner wall of the top foil 722 forms the axial bore of the hydrodynamic gas bearing 7. The rotor 2 is mounted in the shaft hole. A bearing gap is formed between the bore wall of the shaft bore and the rotor 2.

The form of the foil assembly 72 is not limited thereto, and for example, in some embodiments not shown, two layers of support foil 721 may be included.

The bearing support 5 is connected with the power equipment shell 1 and the bearing shell 71, a plurality of support air inlet holes 52 are uniformly distributed on the bearing support 5 along the circumferential direction, and the support air inlet holes 52 are channels for allowing outside air of the dynamic pressure gas bearing 7 to enter the dynamic pressure gas bearing 7.

In order to avoid the impact of the air flow on the pressure sensor 6 through the support air inlet hole 52, an annular groove is designed on the inner wall of the bearing mounting hole of the bearing support 5, the annular groove is matched with the outer peripheral surface of the bearing shell 71 to form an air storage cavity 51, the air storage cavity 51 is communicated with a pressure measuring hole 711 on the bearing shell 71, and a sensor air inlet of the pressure sensor 6 is communicated with the air storage cavity 51. The gas reservoir 51 is used to buffer the gas entering the sensor inlet.

The structure of the bearing housing 71 is shown in fig. 5 and 6. A plurality of pressure measuring holes 711 are uniformly distributed on the bearing shell 71 along the circumferential direction, and the pressure measuring holes 711 communicate the bearing gap with the air storage cavity 51, so that the pressure sensor 6 can accurately test the pressure of the air film of the dynamic pressure gas bearing. As described above, the rotation speed of the rotor 2 has a positive correlation with the film pressure in the bearing gap, that is, the film pressure increases as the rotation speed increases, and the rotation speed of the rotor has a definite correlation with the film pressure in the power plant including the dynamic pressure gas bearing 7 and the rotor 2 whose structural parameters are fixed. When the dynamic pressure gas bearing is worn, the value detected by the pressure sensor 6 deviates from the original value. It is therefore possible to determine whether the hydrodynamic gas bearing is worn or not based on the gas film pressure detected by the pressure sensor 6.

As shown in fig. 3 to 6, the bearing housing 71 has a plurality of bearing air inlet holes 712 uniformly distributed along the circumferential direction at the middle portion thereof, and the plurality of bearing air inlet holes 712 are correspondingly communicated with the plurality of support air inlet holes 52 on the bearing support 5.

In this embodiment, in order to achieve a more accurate test result, the structural characteristic that the bearing housing 71 is divided into the left and right portions by the bearing air inlet hole 712 is met, and the two pressure sensors 6 are symmetrically distributed about the bearing air inlet hole 712 to respectively test the pressure conditions of the dynamic pressure air films on the two axial sides of the bearing housing 71. In the disclosed embodiment, each shaft support assembly comprises two pressure sensors 6.

Each shaft support component adopts a plurality of pressure sensors 6 to detect whether the dynamic pressure gas bearing 7 is abraded or not, so that the comprehensive data of a plurality of pressures are facilitated, and the condition that a single pressure sensor 6 is interfered, such as the interference of low-frequency filtering of a frequency converter, and the abnormal display is avoided.

As shown in fig. 3 and 4, in order to avoid the leakage of the pressure of the bearing air film, a matching structure of clearance fit and packing of the sealing ring 8 is adopted between the bearing support 5 and the bearing housing 71, and the deformation sealing effect of the sealing ring 8 is favorable for avoiding the leakage of the air flow inside the dynamic pressure gas bearing 7 from the clearance between the bearing support 5 and the bearing housing 71, and is favorable for improving the pressure stability of the air film and the accuracy of the test of the pressure sensor 6. Furthermore, the deformation of the sealing ring 8 also provides additional damping for the hydrodynamic gas bearing 7.

In the embodiment of the present disclosure, four seal grooves 713 are circumferentially provided on the outer circumferential surface of the bearing housing 7, and four seal rings 8 are respectively installed in the four seal grooves 713. Two seal rings 8 are disposed on the left and right sides of the bearing intake hole 712.

In the embodiment of the present disclosure, the first comb seal 4 and the second comb seal 9 are provided as two comb seal members at the left and right ends of the dynamic pressure gas bearing 7, respectively. The first comb tooth seal 4 and the second comb tooth seal 9 are both rotary parts and are in clearance fit with the rotor 2, and the fit clearance with the rotor is an airflow outlet of the dynamic pressure gas bearing 7.

In order to reduce the pressure sudden change of the outlet airflow of the dynamic pressure gas bearing and improve the stability of the distribution of the gas film of the dynamic pressure gas bearing 7 and the accuracy of pressure detection, the airflow outlet of the dynamic pressure gas bearing 7 of the embodiment of the present disclosure adopts a multi-comb-tooth and step-type structural form.

As shown in fig. 3 and 4, the portions of the rotor 2 that engage with the first comb seal 4 and the second comb seal 9 each include a stepped surface. The seal comb teeth of the first comb seal 4 include first-order teeth 41 and second-order teeth 42, and the seal comb teeth of the second comb seal 9 include first-order teeth 91 and second-order teeth 92, corresponding to the step surfaces. That is, the first and second stepped teeth of the first and second comb seals 4 and 9 are engaged with the corresponding stepped surfaces of the rotor 2 to form a plurality of gaps. When the rotor 2 rotates and the airflow in the dynamic pressure gas bearing 7 flows to the airflow outlet, the airflow flows through each gap and is approximately in an ideal throttling process, the pressure and the temperature of the airflow are reduced, and the speed is increased; when the air enters the cavity of the sealed comb teeth, the flow area is suddenly increased, the air flow forms strong vortex, the pressure is unchanged, but the speed almost completely disappears, the more gaps the air flow passes through, and the better the air film pressure is maintained. The sealing comb teeth distributed in a stepped manner are adopted, so that the throttling effect is better, the pressure mutation of outlet airflow is further reduced, and the stability of the air film pressure of the dynamic pressure gas bearing 7 is facilitated.

Finally, it should be noted that: the above examples are intended only to illustrate the technical solutions of the present disclosure and not to limit them; although the present disclosure has been described in detail with reference to preferred embodiments, those of ordinary skill in the art will understand that: modifications to the embodiments of the disclosure or equivalent replacements of parts of the technical features may be made, which are all covered by the technical solution claimed by the disclosure.

Claims (12)

1. A power plant, characterized by comprising a rotor (2) and a shaft support assembly for supporting the rotor (2), the shaft support assembly comprising:

a bearing support (5) having a bearing mounting hole;

the dynamic pressure gas bearing (7) is mounted in the bearing mounting hole, and comprises a bearing housing (71) and a foil assembly (72) arranged in the bearing housing (71), wherein the foil assembly (72) forms a shaft hole of the dynamic pressure gas bearing (7), and the rotor (2) is rotatably mounted in the shaft hole; and

bearing wear detection apparatus comprising a pressure sensor (6), said pressure sensor (6) being configured to detect a gas film pressure of a bearing gap between said rotor (2) and said foil assembly (72) to determine a wear state of said hydrodynamic gas bearing (7) from said gas film pressure.

2. A power plant according to claim 1, characterized in that the bearing housing (71) has a pressure measuring hole (711) communicating the radially inner and outer peripheral surfaces thereof, and the sensor inlet port of the pressure sensor (6) communicates with the bearing gap through the pressure measuring hole (711).

3. The power plant of claim 2,

an air storage cavity (51) is formed between the hole wall of the bearing mounting hole and the outer peripheral surface of a bearing shell (71) of the dynamic pressure gas bearing (7), and the pressure measuring hole (711) is communicated with the air storage cavity (51);

the sensor air inlet is communicated with the air storage cavity (51).

4. A power plant according to claim 3, characterized in that the bearing housing (71) has a plurality of said pressure taps (711) communicating with the same air reservoir (51).

5. The power plant of claim 3,

a plurality of gas storage cavities (51) are axially arranged between the hole wall of the bearing mounting hole and the outer peripheral surface of a bearing shell (71) of the dynamic pressure gas bearing (7), and each gas storage cavity (51) is respectively communicated with a plurality of pressure measuring holes (711) axially arranged along the dynamic pressure gas bearing (7);

the bearing wear detection device comprises a plurality of pressure sensors (6), and the pressure sensors (6) are respectively communicated with the air storage cavities (51).

6. A power plant according to claim 1, characterized in that the bearing wear detection means comprises a plurality of said pressure sensors (6), the plurality of said pressure sensors (6) being arranged to detect the gas film pressure of the bearing gap at different positions in the axial direction of the hydrodynamic gas bearing (7).

7. The power plant as claimed in claim 6, wherein the bearing housing (71) has a bearing intake hole (712) located at an axially middle portion of the bearing housing (71), and a plurality of the pressure sensors (6) are distributed on both axial sides of the bearing intake hole (712).

8. The power equipment according to any one of claims 1 to 7, wherein the bearing housing (71) has a bearing intake hole (712) located at an axially middle portion of the bearing housing (71), the power equipment further comprising a plurality of seal rings (8), the plurality of seal rings (8) being located between the bearing holder (5) and the bearing housing (71) and being respectively disposed at both sides of the bearing intake hole (712) in an axial direction of the dynamic pressure gas bearing (7).

9. The power equipment according to any one of claims 1 to 7, wherein the bearing housing (71) has a bearing air inlet hole (712) located at an axially middle portion of the bearing housing (71), the power equipment further comprises two comb seal members provided at both axial ends of the bearing housing (71), the comb seal members having shaft seal holes, the hole walls of the shaft seal holes being provided with sealing comb teeth, end faces of the comb seal members near the dynamic pressure gas bearing (7) abutting against corresponding end faces of the dynamic pressure gas bearing (7), the rotor (2) being mounted in the shaft seal holes, and an outer peripheral surface of the rotor (2) being engaged with the sealing comb teeth.

10. A power plant according to claim 9, characterized in that the portion of the rotor (2) which engages with the comb sealing part comprises a stepped surface, and the sealing comb comprises a first-order tooth which engages with an end surface of the stepped surface which is close to the dynamic pressure gas bearing (7), and a second-order tooth which is located on a side of the first-order tooth which is remote from the dynamic pressure gas bearing (7).

11. A power plant according to any of claims 1-7, characterized by comprising a plurality of said shaft support assemblies arranged in the axial direction of the rotor (2).

12. A power plant according to any of claims 1 to 7, characterized in that the power plant comprises a compressor.

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