WO2022111294A1 - Gas bearing and centrifugal compressor having same - Google Patents

Gas bearing and centrifugal compressor having same Download PDF

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Publication number
WO2022111294A1
WO2022111294A1 PCT/CN2021/130110 CN2021130110W WO2022111294A1 WO 2022111294 A1 WO2022111294 A1 WO 2022111294A1 CN 2021130110 W CN2021130110 W CN 2021130110W WO 2022111294 A1 WO2022111294 A1 WO 2022111294A1
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Prior art keywords
foil
bearing
gas bearing
top foil
gas
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PCT/CN2021/130110
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French (fr)
Chinese (zh)
Inventor
尹泳
俞国新
朱万朋
韩聪
常云雪
殷纪强
李思茹
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青岛海尔智能技术研发有限公司
海尔智家股份有限公司
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Publication of WO2022111294A1 publication Critical patent/WO2022111294A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings

Definitions

  • the present invention relates to the technical field of compressors, in particular to a gas bearing and a centrifugal compressor having the same.
  • the gas bearing in the prior art also has certain defects in practical use.
  • an aluminum foil is generally arranged between the bearing bush and the casing to play a supporting role.
  • the supporting surface is too small, the overall strength of the gas bearing may be unqualified, resulting in abnormal operation in actual operation. Vibration reduces the service life of the gas bearing, making it difficult to adapt to high-speed operating conditions.
  • An object of the present invention is to overcome at least one defect in the prior art and provide a gas bearing with improved support force and stability.
  • a further object of the present invention is to improve the stiffness and pressure resistance of the top foil when the gas bearing is used as a radial or circumferential bearing.
  • the present invention provides a gas bearing comprising:
  • the corrugated foil includes a plurality of arched portions arranged at intervals, and each of the arched portions has an adhering surface facing the top foil, and the adhering surface is adhered to the surface of the top foil in a surface-contact manner.
  • gas bearing is a radial bearing
  • corrugated foil is cylindrical as a whole
  • each arch portion is a circular arc surface matching the shape of the outer circular surface of the top foil.
  • the corrugated foil extends in a trapezoidal wave shape in the circumferential direction of the gas bearing, and the trapezoidal top surface of the corrugated foil facing the top foil constitutes a bonding surface.
  • top foil to bearing base diameter ratio is between 0.8 and 1.2.
  • the gas bearing is an axial bearing
  • the top foil is in the shape of a flat plate as a whole
  • the abutting surface of each arch is a flat surface.
  • bearing base is in the shape of an annular flat plate
  • the corrugated foil extends in a trapezoidal wave shape in the radial direction of the bearing base, and the trapezoidal top surface of the corrugated foil facing the top foil constitutes a bonding surface.
  • the number of the top foils is multiple and uniformly arranged along the circumferential interval of the bearing base.
  • the ratio of the outer diameter to the inner diameter of the bearing base is between 2 and 2.4.
  • the corrugated foil is provided with at least one flow hole for connecting the regions on both sides of the corrugated foil.
  • the present invention also provides a centrifugal compressor comprising the gas bearing of any one of the above.
  • the corrugated foil since the corrugated foil is arranged between the bearing base and the top foil, the corrugated foil has a plurality of arched portions protruding toward the top foil, and the adhering surfaces of the arched portions are in surface contact. On the surface of the top foil, the friction area between the corrugated foil and the top foil is increased, thereby increasing the damping coefficient between the corrugated foil and the top foil, improving the supporting force and stability of the gas bearing, and prolonging its service life.
  • the entire corrugated foil when the gas bearing is used as a radial bearing, can also be arranged in a cylindrical shape, and is arranged between the bearing base and the top foil, and the corrugated foil is uniform along its circumferential direction.
  • a plurality of arched parts are formed protruding toward the top foil, and the bonding surface of each arched part can be configured as a circular arc surface, which can realize the surface contact between the bonding surface and the top foil, and increase the number of arched parts.
  • the contact area with the top foil improves the rigidity and compression resistance of the top foil; when the gas bearing is used as an axial bearing, the shape of the top foil is a flat plate, and the fitting surface of the arched part can also be appropriately set By forming a plane, the bonding surface and the top foil can be bonded in a surface-contact manner, which increases the contact area between the arch and the top foil, and improves the rigidity and compression resistance of the top foil.
  • FIG. 1 is a schematic diagram of a complete machine structure of a centrifugal compressor according to an embodiment of the present invention
  • Fig. 2 is a schematic cross-sectional view obtained by cutting the centrifugal compressor shown in Fig. 1 along the axial direction of the centrifugal impeller;
  • Fig. 3 is the enlarged view of A place of Fig. 2;
  • FIG. 4 is a schematic diagram of a radial bearing in a centrifugal compressor according to an embodiment of the present invention
  • Fig. 5 is the enlarged view at B of Fig. 4;
  • FIG. 6 is a perspective view of an axial bearing in a centrifugal compressor according to an embodiment of the present invention.
  • FIG. 7 is a side view of an axial bearing in a centrifugal compressor according to an embodiment of the present invention.
  • Fig. 8 is an enlarged view at C of Fig. 7;
  • FIG. 9 is a schematic diagram of a corrugated foil in a radial bearing according to one embodiment of the present invention.
  • FIG. 1 is a schematic diagram of the whole machine structure of a centrifugal compressor according to an embodiment of the present invention
  • FIG. 2 is a schematic diagram obtained by cutting the centrifugal compressor shown in FIG. 1 along the axial direction of the centrifugal impeller
  • Fig. 3 is an enlarged view of part A of Fig. 2; the present invention first proposes a centrifugal compressor 1.
  • the centrifugal compressor 1 may generally comprise a casing 10 , a motor 40 and at least one compression unit 20 , 30 .
  • the casing 10 defines an accommodating space, and the motor 40 is installed in the casing 10 .
  • the motor 40 includes a stator 41 and a rotor 42 , the stator 41 is fixed to the casing 10 , and the rotor 42 is rotatable relative to the stator 41 .
  • the number of compression units 20, 30 may be one or more.
  • the centrifugal compressor 1 may be a single-stage compression type, and only one compression unit may be provided.
  • the centrifugal compressor 1 may also be of a multi-stage compression type in which a plurality of compression units 20, 30 are provided.
  • Each compression unit 20 , 30 includes a volute 100 mounted to the casing 10 and a closed impeller 200 disposed within the volute 100 .
  • the closed impeller 200 is configured to rotate under the driving of the motor 40 to compress the airflow entering the volute 100 and discharge it through the outlet of the volute 100 .
  • the centrifugal compressor 1 can be a two-stage compression type, and the number of compression units is two. It can be seen that one of the two compression units 20 and 30 must be a low pressure stage and the other is a high pressure stage. As shown in FIG. 1 and FIG. 2 , the compression unit 20 on the left side of the drawing is the low pressure stage, and the compression unit 30 on the right side is the low pressure stage. for the high pressure level.
  • the outlet of the volute 100 of the compression unit 20 of the low pressure stage communicates with the inlet of the volute 100 of the compression unit 30 of the high pressure stage through the connecting pipe 50 .
  • connection pipe 50 is provided with a flange 51 to connect with the flange 60 of the outlet of the volute 100 of the compression unit 20 of the low pressure stage, and the outlet end of the connection pipe 50 is provided with a flange 52 to be connected to the outlet of the compression unit 30 of the high pressure stage.
  • the volute 100 is connected.
  • the compression unit 20 of the low pressure stage and the compression unit 20 of the high pressure stage are located on both sides of the motor 40 in the axial direction, so that the closed impellers 200 of the two compression units 20 and 30 are directly connected to the motor 40, and it is convenient for the two The axial force of the closed impeller 200 is partially offset.
  • the volute 100 defines an inlet flow channel 101, a scroll-shaped flow channel 102 and an outlet flow channel 103 which are connected in sequence along the airflow direction, that is, the flow channel of the volute 100 is divided into three sections.
  • the inlet of the intake runner 101 constitutes the inlet of the volute 100 described herein, and the outlet of the outlet runner 103 constitutes the outlet of the volute 100 .
  • the intake flow passage 101 extends in the axial direction (x-axis direction) of the closed impeller 200 .
  • the centrifugal compressor may further include at least one radial bearing 70 and at least one axial bearing 80 .
  • the radial bearing 70 and the axial bearing 80 are arranged in the casing 10 to support the motor 40 .
  • the rotor 42 wherein the radial bearing 70 is used to limit the displacement of the rotor 42 in its radial direction, and the axial bearing 80 is used to limit the displacement of the rotor 42 in its axial direction.
  • radial bearing 70 and axial bearing 80 may also be gas bearings.
  • the gas bearing can utilize the working fluid of the centrifugal compressor 1 as a lubricant.
  • a gas film gap can be formed between the gas bearing and the rotor 42 , and the gas enters the gas film gap to form a dynamic pressure gas film, so that the rotor 42 is suspended.
  • gas bearings Compared with traditional sliding bearings, gas bearings have no mechanical contact, and the degree of wear is minimized, thereby ensuring that the accuracy is always stable; compared with magnetic bearings, gas bearings also have the advantages of simple structure and low manufacturing cost, especially when the centrifugal
  • the compressor 1 is used in the field of refrigeration equipment (such as refrigerators, etc.), the gas bearing can use the gas refrigerant as a lubricant, and no additional lubricant is needed, so that the structure of the centrifugal compressor 1 is simple and compact, and at the same time, the rotation can be reduced. Process wear and prolong the service life of gas bearings.
  • FIG. 4 is a schematic diagram of a radial bearing in a centrifugal compressor according to an embodiment of the present invention
  • FIG. 5 is an enlarged view of part B of FIG. 4
  • FIG. 7 is a side view of an axial bearing in a centrifugal compressor according to an embodiment of the present invention
  • FIG. 8 is an enlarged view of C in FIG. 7 .
  • the gas bearing may further include a bearing base 110, a corrugated foil 120 and a top foil 130, the corrugated foil 120 is disposed between the bearing base 110 and the top foil 130, and the corrugated foil 120 further includes a plurality of spaced apart
  • Each of the arched portions 122 has an adhering surface 122a facing the top foil 130 , and the adhering surface 122a is adhered to the surface of the top foil 130 in a surface-contact manner.
  • the corrugated foil 120 is disposed between the bearing base 110 and the top foil 130 , so that the corrugated foil 120 can provide the top foil 130 with a supporting force away from the bearing base 110 , so that the gas bearing meets the strength of the centrifugal compressor 1 need.
  • the corrugated foil 120 is fixed on the bearing base 110 , and the corrugated foil 120 protrudes toward the top foil 130 to form a plurality of arched portions 122 , and the arched portions 122 can push up the top foil 130 in a direction away from the bearing base 110 .
  • the bonding surface 122a of the arched portion 122 is bonded to the surface of the top foil 130 in a surface contact manner, which increases the friction area between the corrugated foil 120 and the top foil 130, thereby increasing the friction between the corrugated foil 120 and the top foil 130.
  • the damping coefficient improves the support force and stability of the gas bearing and prolongs its service life.
  • the gas bearing in the prior art has a too small supporting surface, which may lead to unqualified strength of the gas bearing as a whole, resulting in abnormal vibration in actual operation, reducing the service life of the gas bearing, and it is difficult to Adapt to high-speed operation conditions.
  • the gas bearing of this embodiment uses the corrugated foil 120 to be attached to the surface of the top foil 130 in a surface-contact manner, so as to increase the friction area between the corrugated foil 120 and the top foil 130, so that in the During operation, the structure between the corrugated foil 120 and the top foil 130 is more stable, which improves the rigidity and compression resistance of the top foil 130 .
  • the shape of the bearing base 110 and the top foil 130 may be configured as a cylinder, and the diameter of the bearing base 110 is larger than that of the top foil 130, the top foil 130 is arranged at intervals inside the bearing base 110, the interior of the top foil 130 defines a space that can be used for the rotor 42 to pass through, and the rotor 42 can rotate relative to the top foil 130, and the top foil 130 and the rotor 42 form a space.
  • the gas enters the air film gap to form a dynamic pressure air film, so that the rotor 42 is suspended in the space, which can not only limit the radial displacement of the rotor 42, but also reduce the wear.
  • the corrugated foil 120 can also be configured in a cylindrical shape as a whole, and is disposed between the bearing base 110 and the top foil 130.
  • the corrugated foil 120 is uniformly protruded toward the top foil 130 along its circumferential direction to form a plurality of arched portions 122, each of which is
  • the adhering surface 122a of the arched portion 122 may be configured as a circular arc surface.
  • the top foil 130 is cylindrical, and the attaching surface 122a is set to be the same arc surface as the outer circular surface of the top foil 130, so that the attaching surface 122a and the top foil 130 can be attached in a surface-contact manner.
  • the contact area between the arched portion 122 and the top foil 130 is increased, and the rigidity and compression resistance of the top foil 130 are improved.
  • the diameter of the abutting surface 122 a can also be configured to be smaller than or equal to the diameter of the top foil 130 , so as to ensure that the outer circumference of the abutting surface 122 a and the top foil 130 are There is no gap between the surfaces when they are attached.
  • the corrugated foil 120 when the gas bearing is used as the radial bearing 70, the corrugated foil 120 extends in a trapezoidal wave shape in the circumferential direction of the gas bearing, and the corrugated foil 120 faces the top foil
  • the trapezoidal top surface of 130 constitutes the contact surface 122a.
  • the arched portion 122 is formed on the corrugated foil 120, so that the entire corrugated foil 120 has a trapezoidal wave shape and extends along the circumferential direction of the gas bearing, and the corrugated foil 120 faces
  • the trapezoidal top surface of the top foil 130 constitutes the adhering surface 122a, and the two side surfaces of the arched portion 122 respectively extend from the two sides of the adhering surface 122a to the corrugated foil 120 to form a stable trapezoidal structure.
  • the diameter ratio of the top foil 130 to the bearing base 110 is between 0.8 and 1.2, eg, 0.8, 1, or 1.2, etc.
  • the shape of the top foil 130 can be configured as a flat plate, and the rotor 42 is formed with a thrust plate (not shown in the figure) along its radial direction. shown), the top foil 130 is opposite to one side of the thrust plate, a gas film gap is formed between the top foil 130 and the rotor 42, and the gas enters the gas film gap to form a dynamic pressure gas film, which can not only limit the radial displacement of the rotor 42, but also reduce the worn out.
  • the abutting surface 122a of the arched portion 122 can also be adapted to be flat, so that the abutting surface 122a and the top foil 130 are in surface contact with each other.
  • the contact area between the arched portion 122 and the top foil 130 is increased, and the rigidity and compression resistance of the top foil 130 are improved.
  • the bearing base 110 can also be configured as an annular flat plate, the inner ring of the bearing base 110 is used for the rotor 42 to pass through, and the top foil 130 is made to pass through. Opposite to the thrust plate of the rotor 42 .
  • top foils 130 are provided on both sides of a thrust disk to clamp the thrust disks of the rotor 42 , thereby limiting the axial displacement of the rotor 42 .
  • the corrugated foil 120 extends in a trapezoidal wave shape in the radial direction of the bearing base 110 , and the trapezoidal top surface of the corrugated foil 120 facing the top foil 130 forms a bonding surface 122 a. Since the arched portion 122 protrudes toward the top foil 130 , and the corrugated foil 120 extends in the radial direction of the bearing base 110 , the corrugated foil 120 has a trapezoidal wave shape in the radial direction of the bearing base 110 , and the arched portion 122 faces the top. The trapezoidal top surface of the foil 130 serves as the adhering surface 122a.
  • the number of the top foils 130 is multiple, and correspondingly, the number of the corrugated foils 120 can be multiple, and the top foil 130 is along the circumferential direction of the bearing base 110 .
  • the intervals are evenly arranged, and a gap is formed between two adjacent top foils 130 to facilitate the flow of lubricating gas.
  • the ratio of the outer diameter to the inner diameter of the bearing base 110 is between 2 and 2.4, such as 2, 2.2, or 2.4.
  • the relative area of the discs is within a reasonable range, which further ensures the rigidity and compression resistance of the top foil 130 .
  • FIG. 9 is a schematic diagram of a corrugated foil in a radial bearing according to an embodiment of the present invention.
  • the corrugated foil 120 is provided with at least one flow hole 124 for connecting regions on both sides of the corrugated foil 120 .
  • the bearing base 110 may also be provided with a plurality of air inlet holes (not shown in the figure) for guiding the lubricating gas from the air inlet holes to the gap between the bearing base 110 and the top foil 130, When the lubricating gas fills the gap, the lubricating gas can directly act on the corrugated foil 120 between the bearing base 110 and the top foil 130 , thereby further improving the stiffness of the corrugated foil 120 .
  • the corrugated foil 120 is also provided with a circulation hole 124. The circulation hole 124 communicates with the regions on both sides of the corrugated foil 120.
  • the lubricating gas on one side of the corrugated foil 120 can flow to the other side of the corrugated foil 120 through the circulation hole 124, so that the lubricating gas can flow to the other side of the corrugated foil 120.
  • the better flow in the gas bearing prevents the rotor 42 from contacting the gas bearing, avoids the wear of the gas bearing after contact, and ensures that the rotor 42 can run at high speed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Support Of The Bearing (AREA)

Abstract

A gas bearing and a centrifugal compressor (1) having same. The gas bearing comprises a bearing base body (110), a top foil (130) and a bump foil (120) arranged between the bearing base body (110) and the top foil (130), wherein the bump foil (120) comprises a plurality of bumps (122) arranged at intervals, each bump (122) is provided with a fitting face (122a) facing the top foil (130), and the fitting face (122a) is attached to the surface of the top foil (130) in a face contact manner.

Description

气体轴承和具有其的离心压缩机Gas bearing and centrifugal compressor having the same 技术领域technical field
本发明涉及压缩机技术领域，特别是涉及一种气体轴承和具有其的离心压缩机。The present invention relates to the technical field of compressors, in particular to a gas bearing and a centrifugal compressor having the same.
背景技术Background technique
随着离心压缩技术的不断发展，对于离心压缩机的轴承要求也不断提高。目前现有技术中出现了利用压缩机工作介质作为润滑剂的气体轴承，其凭借着效率高、能源损失小的特点被人们所关注。With the continuous development of centrifugal compression technology, the requirements for bearings of centrifugal compressors are also increasing. At present, in the prior art, a gas bearing using the compressor working medium as a lubricant has appeared, and it has attracted people's attention due to its features of high efficiency and small energy loss.
但是现有技术中的气体轴承在实际使用时也具有一定的缺陷。例如，现有技术的气体轴承一般采用在轴瓦与外壳之间设置铝箔来起到支撑作用，但是由于其支撑面过小，这可能导致气体轴承整体的强度不合格，导致在实际运行中产生异常振动，降低了气体轴承的使用寿命，难以适应高速运行的工况。However, the gas bearing in the prior art also has certain defects in practical use. For example, in the gas bearing of the prior art, an aluminum foil is generally arranged between the bearing bush and the casing to play a supporting role. However, because the supporting surface is too small, the overall strength of the gas bearing may be unqualified, resulting in abnormal operation in actual operation. Vibration reduces the service life of the gas bearing, making it difficult to adapt to high-speed operating conditions.
发明内容SUMMARY OF THE INVENTION
本发明的一个目的旨在克服现有技术中的至少一个缺陷，提供一种提高支撑力和稳定性的气体轴承。An object of the present invention is to overcome at least one defect in the prior art and provide a gas bearing with improved support force and stability.
本发明一个进一步的目的是当气体轴承作为径向轴承或周向轴承时，提高顶箔的刚度和抗压能力。A further object of the present invention is to improve the stiffness and pressure resistance of the top foil when the gas bearing is used as a radial or circumferential bearing.
特别地，本发明提供了一种气体轴承，包括：In particular, the present invention provides a gas bearing comprising:
轴承基体、顶箔和设置于轴承基体和顶箔之间的波箔；其中，A bearing base, a top foil, and a corrugated foil disposed between the bearing base and the top foil; wherein,
波箔包括多个间隔设置的拱起部，且每个拱起部具有朝向顶箔的贴合面，贴合面以面接触的方式贴合于顶箔表面。The corrugated foil includes a plurality of arched portions arranged at intervals, and each of the arched portions has an adhering surface facing the top foil, and the adhering surface is adhered to the surface of the top foil in a surface-contact manner.
进一步地，气体轴承为径向轴承，波箔整体为圆柱状；且Further, the gas bearing is a radial bearing, and the corrugated foil is cylindrical as a whole; and
每个拱起部的贴合面为与顶箔外圆面形状匹配的圆弧面。The abutting surface of each arch portion is a circular arc surface matching the shape of the outer circular surface of the top foil.
进一步地，波箔在气体轴承的周向方向上以梯形波浪状延伸，且波箔朝向顶箔的梯形顶面构成贴合面。Further, the corrugated foil extends in a trapezoidal wave shape in the circumferential direction of the gas bearing, and the trapezoidal top surface of the corrugated foil facing the top foil constitutes a bonding surface.
进一步地，顶箔与轴承基体直径比在0.8至1.2之间。Further, the top foil to bearing base diameter ratio is between 0.8 and 1.2.
进一步地，气体轴承为轴向轴承，顶箔整体为平板状；且Further, the gas bearing is an axial bearing, and the top foil is in the shape of a flat plate as a whole; and
每个拱起部的贴合面为平面。The abutting surface of each arch is a flat surface.
进一步地，轴承基体为环形平板状；Further, the bearing base is in the shape of an annular flat plate;
波箔在轴承基体的径向方向上呈梯形波浪状延伸，且其朝向顶箔的梯形顶面构成贴合面。The corrugated foil extends in a trapezoidal wave shape in the radial direction of the bearing base, and the trapezoidal top surface of the corrugated foil facing the top foil constitutes a bonding surface.
进一步地，顶箔的数量为多个且沿轴承基体的周向间隔均匀布置。Further, the number of the top foils is multiple and uniformly arranged along the circumferential interval of the bearing base.
进一步地，轴承基体的外径与内径的比值在2至2.4之间。Further, the ratio of the outer diameter to the inner diameter of the bearing base is between 2 and 2.4.
进一步地，波箔上开设有至少一个用于连通波箔两侧区域的流通孔。Further, the corrugated foil is provided with at least one flow hole for connecting the regions on both sides of the corrugated foil.
特别地，本发明还提供了一种离心压缩机，该离心压缩机包括上述中任一项的气体轴承。In particular, the present invention also provides a centrifugal compressor comprising the gas bearing of any one of the above.
本发明的气体轴承中，由于波箔设置于轴承基体和顶箔之间，波箔上具有向顶箔凸出的多个拱起部，拱起部的贴合面以面接触的方式贴合于顶箔表面，增加了波箔与顶箔之间的摩擦面积，进而增加了波箔与顶箔之间的阻尼系数，提高了气体轴承的支撑力和稳定性，延长了其使用寿命。In the gas bearing of the present invention, since the corrugated foil is arranged between the bearing base and the top foil, the corrugated foil has a plurality of arched portions protruding toward the top foil, and the adhering surfaces of the arched portions are in surface contact. On the surface of the top foil, the friction area between the corrugated foil and the top foil is increased, thereby increasing the damping coefficient between the corrugated foil and the top foil, improving the supporting force and stability of the gas bearing, and prolonging its service life.
进一步地，本发明的气体轴承中，当该气体轴承作为径向轴承时，波箔整体还可以被配置成圆柱状，并且设置于轴承基体与顶箔之间，波箔沿其周向均匀地朝向顶箔凸起形成多个拱起部，每个拱起部的贴合面可以配置成圆弧面，能够实现贴合面与顶箔以面接触的方式贴合，增大了拱起部与顶箔之间的接触面积，提高了顶箔的刚度和抗压能力；当气体轴承作为轴向轴承时，顶箔的形状为平板状，拱起部的贴合面也可以适配地设置成平面，实现该贴合面与顶箔以面接触的方式贴合，增大了拱起部与顶箔之间的接触面积，提高了顶箔的刚度和抗压能力。Further, in the gas bearing of the present invention, when the gas bearing is used as a radial bearing, the entire corrugated foil can also be arranged in a cylindrical shape, and is arranged between the bearing base and the top foil, and the corrugated foil is uniform along its circumferential direction. A plurality of arched parts are formed protruding toward the top foil, and the bonding surface of each arched part can be configured as a circular arc surface, which can realize the surface contact between the bonding surface and the top foil, and increase the number of arched parts. The contact area with the top foil improves the rigidity and compression resistance of the top foil; when the gas bearing is used as an axial bearing, the shape of the top foil is a flat plate, and the fitting surface of the arched part can also be appropriately set By forming a plane, the bonding surface and the top foil can be bonded in a surface-contact manner, which increases the contact area between the arch and the top foil, and improves the rigidity and compression resistance of the top foil.
根据下文结合附图对本发明具体实施例的详细描述，本领域技术人员将会更加明了本发明的上述以及其他目的、优点和特征。The above and other objects, advantages and features of the present invention will be more apparent to those skilled in the art from the following detailed description of the specific embodiments of the present invention in conjunction with the accompanying drawings.
附图说明Description of drawings
后文将参照附图以示例性而非限制性的方式详细描述本发明的一些具体实施例。附图中相同的附图标记标示了相同或类似的部件或部分。本领域技术人员应该理解，这些附图未必是按比例绘制的。附图中：Hereinafter, some specific embodiments of the present invention will be described in detail by way of example and not limitation with reference to the accompanying drawings. The same reference numbers in the figures designate the same or similar parts or parts. It will be understood by those skilled in the art that the drawings are not necessarily to scale. In the attached picture:
图1是根据本发明一个实施例的离心压缩机的整机结构示意图；1 is a schematic diagram of a complete machine structure of a centrifugal compressor according to an embodiment of the present invention;
图2是对图1所示离心压缩机沿离心叶轮的轴线方向剖切后得到的示意性剖视图；Fig. 2 is a schematic cross-sectional view obtained by cutting the centrifugal compressor shown in Fig. 1 along the axial direction of the centrifugal impeller;
图3是图2的A处放大图；Fig. 3 is the enlarged view of A place of Fig. 2;
图4是根据本发明一个实施例的离心压缩机中径向轴承的示意图；4 is a schematic diagram of a radial bearing in a centrifugal compressor according to an embodiment of the present invention;
图5是图4的B处放大图；Fig. 5 is the enlarged view at B of Fig. 4;
图6是根据本发明一个实施例的离心压缩机中轴向轴承的立体图；6 is a perspective view of an axial bearing in a centrifugal compressor according to an embodiment of the present invention;
图7是根据本发明一个实施例的离心压缩机中轴向轴承的侧视图；7 is a side view of an axial bearing in a centrifugal compressor according to an embodiment of the present invention;
图8是图7的C处放大图；Fig. 8 is an enlarged view at C of Fig. 7;
图9是根据本发明一个实施例的径向轴承中波箔的示意图。9 is a schematic diagram of a corrugated foil in a radial bearing according to one embodiment of the present invention.
具体实施方式Detailed ways
请参见图1至图3，图1是根据本发明一个实施例的离心压缩机的整机结构示意图，图2是对图1所示离心压缩机沿离心叶轮的轴线方向剖切后得到的示意性剖视图，图3是图2的A处放大图；本发明首先提出一种离心压缩机1。该离心压缩机1一般性地可以包括机壳10、电机40和至少一个压缩单元20,30。Please refer to FIG. 1 to FIG. 3 , FIG. 1 is a schematic diagram of the whole machine structure of a centrifugal compressor according to an embodiment of the present invention, and FIG. 2 is a schematic diagram obtained by cutting the centrifugal compressor shown in FIG. 1 along the axial direction of the centrifugal impeller Fig. 3 is an enlarged view of part A of Fig. 2; the present invention first proposes a centrifugal compressor 1. The centrifugal compressor 1 may generally comprise a casing 10 , a motor 40 and at least one compression unit 20 , 30 .
机壳10限定有容纳空间，电机40安装于机壳10内。电机40包括定子41和转子42，定子41固定于机壳10，转子42可相对定子41转动。压缩单元20,30的数量可为一个或多个。例如，可使离心压缩机1为单级压缩式，仅设置一个压缩单元。也可使离心压缩机1为多级压缩式，其设置多个压缩单元20,30。每个压缩单元20,30包括安装于机壳10的蜗壳100和设置在蜗壳100内的闭式叶轮200。闭式叶轮200配置成在电机40驱动下转动，以对进入蜗壳100的气流进行压缩并将其经蜗壳100的出口排出。The casing 10 defines an accommodating space, and the motor 40 is installed in the casing 10 . The motor 40 includes a stator 41 and a rotor 42 , the stator 41 is fixed to the casing 10 , and the rotor 42 is rotatable relative to the stator 41 . The number of compression units 20, 30 may be one or more. For example, the centrifugal compressor 1 may be a single-stage compression type, and only one compression unit may be provided. The centrifugal compressor 1 may also be of a multi-stage compression type in which a plurality of compression units 20, 30 are provided. Each compression unit 20 , 30 includes a volute 100 mounted to the casing 10 and a closed impeller 200 disposed within the volute 100 . The closed impeller 200 is configured to rotate under the driving of the motor 40 to compress the airflow entering the volute 100 and discharge it through the outlet of the volute 100 .
在一些具体的实施例中，例如图1和图2所示，离心压缩机1可为双级压缩式，压缩单元的数量为两个。可知，两个压缩单元20,30中必然有一个为低压级，另一个为高压级，如图1和图2中，位于图面左侧的压缩单元20为低压级，右侧的压缩单元30为高压级。低压级的压缩单元20的蜗壳100的出口通过连接管50与高压级的压缩单元30的蜗壳100的进口连通。具体地，连接管50的进口端设置法兰51以与低压级的压缩单元20的蜗壳100出口的法兰60相接，连接管50出口端设置法兰52以与高压级压缩单元30的蜗壳100连接。优选使低压级的压缩单元20与高压级的压缩单元20分别位于电机40的轴向两侧，以便两个压缩单元20,30的闭式叶轮200分别直接连接于电机40，且利于使两个闭式叶轮200的轴向力进行部分抵消。In some specific embodiments, such as shown in FIG. 1 and FIG. 2 , the centrifugal compressor 1 can be a two-stage compression type, and the number of compression units is two. It can be seen that one of the two compression units 20 and 30 must be a low pressure stage and the other is a high pressure stage. As shown in FIG. 1 and FIG. 2 , the compression unit 20 on the left side of the drawing is the low pressure stage, and the compression unit 30 on the right side is the low pressure stage. for the high pressure level. The outlet of the volute 100 of the compression unit 20 of the low pressure stage communicates with the inlet of the volute 100 of the compression unit 30 of the high pressure stage through the connecting pipe 50 . Specifically, the inlet end of the connection pipe 50 is provided with a flange 51 to connect with the flange 60 of the outlet of the volute 100 of the compression unit 20 of the low pressure stage, and the outlet end of the connection pipe 50 is provided with a flange 52 to be connected to the outlet of the compression unit 30 of the high pressure stage. The volute 100 is connected. Preferably, the compression unit 20 of the low pressure stage and the compression unit 20 of the high pressure stage are located on both sides of the motor 40 in the axial direction, so that the closed impellers 200 of the two compression units 20 and 30 are directly connected to the motor 40, and it is convenient for the two The axial force of the closed impeller 200 is partially offset.
蜗壳100内限定有沿气流方向依次相连的进气流道101、蜗形流道102 和出气流道103，即蜗壳100流道分为三个区段。进气流道101的进口即构成本文所述的蜗壳100的进口，出气流道103的出口构成蜗壳100的出口。进气流道101沿闭式叶轮200的轴线方向(x轴方向)延伸。The volute 100 defines an inlet flow channel 101, a scroll-shaped flow channel 102 and an outlet flow channel 103 which are connected in sequence along the airflow direction, that is, the flow channel of the volute 100 is divided into three sections. The inlet of the intake runner 101 constitutes the inlet of the volute 100 described herein, and the outlet of the outlet runner 103 constitutes the outlet of the volute 100 . The intake flow passage 101 extends in the axial direction (x-axis direction) of the closed impeller 200 .
请参见图2和图3，该离心压缩机还可以包括至少一个径向轴承70和至少一个轴向轴承80，径向轴承70和轴向轴承80设置于机壳10内，以支撑电机40的转子42，其中径向轴承70用于限定转子42在其径向的位移，轴向轴承80用于限定转子42在其轴向的位移。Referring to FIGS. 2 and 3 , the centrifugal compressor may further include at least one radial bearing 70 and at least one axial bearing 80 . The radial bearing 70 and the axial bearing 80 are arranged in the casing 10 to support the motor 40 . The rotor 42, wherein the radial bearing 70 is used to limit the displacement of the rotor 42 in its radial direction, and the axial bearing 80 is used to limit the displacement of the rotor 42 in its axial direction.
在一些实施例中，径向轴承70和轴向轴承80还可以为气体轴承。在离心压缩机1中，气体轴承可以利用该离心压缩机1的工作流体作为润滑剂。在运行时，该气体轴承可以与转子42之间形成气膜间隙，气体进入气膜间隙形成动压气膜，使转子42悬浮起来。相对于传统的滑动轴承，气体轴承由于没有机械接触，磨损程度降到了最低，从而确保精度始终保持稳定；相对于磁悬浮轴承，气体轴承也具有结构简单、制造成本低等优势，尤其是当该离心压缩机1被应用在制冷设备(如冰箱等)领域，该气体轴承可以利用气体冷媒作为润滑剂，不用再使用额外的润滑剂，使得离心压缩机1的结构简单且紧凑，同时又可以降低转动过程产生的磨损，延长气体轴承的使用寿命。In some embodiments, radial bearing 70 and axial bearing 80 may also be gas bearings. In the centrifugal compressor 1, the gas bearing can utilize the working fluid of the centrifugal compressor 1 as a lubricant. During operation, a gas film gap can be formed between the gas bearing and the rotor 42 , and the gas enters the gas film gap to form a dynamic pressure gas film, so that the rotor 42 is suspended. Compared with traditional sliding bearings, gas bearings have no mechanical contact, and the degree of wear is minimized, thereby ensuring that the accuracy is always stable; compared with magnetic bearings, gas bearings also have the advantages of simple structure and low manufacturing cost, especially when the centrifugal The compressor 1 is used in the field of refrigeration equipment (such as refrigerators, etc.), the gas bearing can use the gas refrigerant as a lubricant, and no additional lubricant is needed, so that the structure of the centrifugal compressor 1 is simple and compact, and at the same time, the rotation can be reduced. Process wear and prolong the service life of gas bearings.
请参见图4至图8，图4是根据本发明一个实施例的离心压缩机中径向轴承的示意图；图5是图4的B处放大图；图6是根据本发明一个实施例的离心压缩机中轴向轴承的立体图；图7是根据本发明一个实施例的离心压缩机中轴向轴承的侧视图；图8是图7的C处放大图。在一些实施例中，该气体轴承还可以包括轴承基体110、波箔120和顶箔130，波箔120设置于轴承基体110和顶箔130之间，并且波箔120还包括多个间隔设置的拱起部122，且每个拱起部122具有朝向顶箔130的贴合面122a，贴合面122a以面接触的方式贴合于顶箔130表面。Please refer to FIGS. 4 to 8 , FIG. 4 is a schematic diagram of a radial bearing in a centrifugal compressor according to an embodiment of the present invention; FIG. 5 is an enlarged view of part B of FIG. 4 ; A perspective view of an axial bearing in a compressor; FIG. 7 is a side view of an axial bearing in a centrifugal compressor according to an embodiment of the present invention; FIG. 8 is an enlarged view of C in FIG. 7 . In some embodiments, the gas bearing may further include a bearing base 110, a corrugated foil 120 and a top foil 130, the corrugated foil 120 is disposed between the bearing base 110 and the top foil 130, and the corrugated foil 120 further includes a plurality of spaced apart Each of the arched portions 122 has an adhering surface 122a facing the top foil 130 , and the adhering surface 122a is adhered to the surface of the top foil 130 in a surface-contact manner.
在本实施例中，波箔120设置于轴承基体110和顶箔130之间，以使得波箔120能够为顶箔130提供远离轴承基体110的支撑力，使得气体轴承满足离心压缩机1的强度需求。具体地，波箔120固定设置于轴承基体110上，并且波箔120向顶箔130凸出形成多个拱起部122，拱起部122能够将顶箔130朝远离轴承基体110的方向顶起。并且拱起部122的贴合面122a以面接触的方式贴合于顶箔130表面，增加波箔120与顶箔130之间的摩擦面积， 进而增加了波箔120与顶箔130之间的阻尼系数，提高了该气体轴承的支撑力和稳定性，延长了其使用寿命。In this embodiment, the corrugated foil 120 is disposed between the bearing base 110 and the top foil 130 , so that the corrugated foil 120 can provide the top foil 130 with a supporting force away from the bearing base 110 , so that the gas bearing meets the strength of the centrifugal compressor 1 need. Specifically, the corrugated foil 120 is fixed on the bearing base 110 , and the corrugated foil 120 protrudes toward the top foil 130 to form a plurality of arched portions 122 , and the arched portions 122 can push up the top foil 130 in a direction away from the bearing base 110 . And the bonding surface 122a of the arched portion 122 is bonded to the surface of the top foil 130 in a surface contact manner, which increases the friction area between the corrugated foil 120 and the top foil 130, thereby increasing the friction between the corrugated foil 120 and the top foil 130. The damping coefficient improves the support force and stability of the gas bearing and prolongs its service life.
如背景技术部分所述，现有技术中的气体轴承由于其支撑面过小，这可能导致气体轴承整体的强度不合格，导致在实际运行中产生异常振动，降低了气体轴承的使用寿命，难以适应高速运行的工况。As mentioned in the background art section, the gas bearing in the prior art has a too small supporting surface, which may lead to unqualified strength of the gas bearing as a whole, resulting in abnormal vibration in actual operation, reducing the service life of the gas bearing, and it is difficult to Adapt to high-speed operation conditions.
因此，为了克服现有技术的缺陷，本实施例的气体轴承采用将波箔120以面接触的方式贴合于顶箔130表面，增加波箔120与顶箔130之间的摩擦面积，使得在运行过程中波箔120与顶箔130之间的结构更加稳定，提高了顶箔130的刚度和抗压能力。Therefore, in order to overcome the defects of the prior art, the gas bearing of this embodiment uses the corrugated foil 120 to be attached to the surface of the top foil 130 in a surface-contact manner, so as to increase the friction area between the corrugated foil 120 and the top foil 130, so that in the During operation, the structure between the corrugated foil 120 and the top foil 130 is more stable, which improves the rigidity and compression resistance of the top foil 130 .
请参见图4和图5，在一些实施例中，当该气体轴承作为径向轴承70时，轴承基体110和顶箔130的形状可以被配置成圆柱状，并且轴承基体110的直径大于顶箔130，顶箔130间隔地设置于轴承基体110的内部，顶箔130的内部限定出可用于转子42穿过的空间，并且转子42可相对顶箔130转动，顶箔130与转子42之间形成气膜间隙，气体进入气膜间隙形成动压气膜，使转子42悬浮在该空间中，不仅可以限定转子42的径向位移，还降低了磨损。Referring to FIGS. 4 and 5 , in some embodiments, when the gas bearing is used as the radial bearing 70 , the shape of the bearing base 110 and the top foil 130 may be configured as a cylinder, and the diameter of the bearing base 110 is larger than that of the top foil 130, the top foil 130 is arranged at intervals inside the bearing base 110, the interior of the top foil 130 defines a space that can be used for the rotor 42 to pass through, and the rotor 42 can rotate relative to the top foil 130, and the top foil 130 and the rotor 42 form a space. In the air film gap, the gas enters the air film gap to form a dynamic pressure air film, so that the rotor 42 is suspended in the space, which can not only limit the radial displacement of the rotor 42, but also reduce the wear.
波箔120整体还可以被配置成圆柱状，并且设置于轴承基体110与顶箔130之间，波箔120沿其周向均匀地朝向顶箔130凸起形成多个拱起部122，每个拱起部122的贴合面122a可以配置成圆弧面。由于在径向轴承70中，顶箔130为圆柱状，贴合面122a设置成与顶箔130外圆面相同的圆弧面，能够实现贴合面122a与顶箔130以面接触的方式贴合，增大了拱起部122与顶箔130之间的接触面积，提高了顶箔130的刚度和抗压能力。The corrugated foil 120 can also be configured in a cylindrical shape as a whole, and is disposed between the bearing base 110 and the top foil 130. The corrugated foil 120 is uniformly protruded toward the top foil 130 along its circumferential direction to form a plurality of arched portions 122, each of which is The adhering surface 122a of the arched portion 122 may be configured as a circular arc surface. In the radial bearing 70, the top foil 130 is cylindrical, and the attaching surface 122a is set to be the same arc surface as the outer circular surface of the top foil 130, so that the attaching surface 122a and the top foil 130 can be attached in a surface-contact manner. In combination, the contact area between the arched portion 122 and the top foil 130 is increased, and the rigidity and compression resistance of the top foil 130 are improved.
在一些具体的实施例中，当该气体轴承作为径向轴承70时，贴合面122a的直径还可以配置成小于或等于顶箔130的直径，以保证贴合面122a与顶箔130外圆面贴合时之间不产生间隙。In some specific embodiments, when the gas bearing is used as the radial bearing 70 , the diameter of the abutting surface 122 a can also be configured to be smaller than or equal to the diameter of the top foil 130 , so as to ensure that the outer circumference of the abutting surface 122 a and the top foil 130 are There is no gap between the surfaces when they are attached.
请参见图4和图5，在一些实施例中，当该气体轴承作为径向轴承70时，波箔120在该气体轴承的周向方向上以梯形波浪状延伸，且波箔120朝向顶箔130的梯形顶面构成贴合面122a。4 and 5, in some embodiments, when the gas bearing is used as the radial bearing 70, the corrugated foil 120 extends in a trapezoidal wave shape in the circumferential direction of the gas bearing, and the corrugated foil 120 faces the top foil The trapezoidal top surface of 130 constitutes the contact surface 122a.
在本实施例中，由于波箔120整体还可以被配置成圆柱状，拱起部122形成于波箔120，使得波箔120整体呈梯形波浪状并沿气体轴承的周向延伸，波箔120朝向顶箔130的梯形顶面构成贴合面122a，拱起部122的两个侧面 分别从贴合面122a两侧延伸至波箔120上，以形成稳定的梯形结构。In this embodiment, since the entire corrugated foil 120 can also be configured in a cylindrical shape, the arched portion 122 is formed on the corrugated foil 120, so that the entire corrugated foil 120 has a trapezoidal wave shape and extends along the circumferential direction of the gas bearing, and the corrugated foil 120 faces The trapezoidal top surface of the top foil 130 constitutes the adhering surface 122a, and the two side surfaces of the arched portion 122 respectively extend from the two sides of the adhering surface 122a to the corrugated foil 120 to form a stable trapezoidal structure.
在一些实施例中，当该气体轴承作为径向轴承70时，顶箔130与轴承基体110直径比在0.8至1.2之间，例如0.8、1或1.2等。发明人通过多次试验后意识到，通过上述限定可以使得顶箔130与轴承基体110之间的间隙处于合理的范围内，也即限定了波箔120最高点至最低点的距离，使得气体轴承的结构更加合理和稳定。In some embodiments, when the gas bearing is used as the radial bearing 70, the diameter ratio of the top foil 130 to the bearing base 110 is between 0.8 and 1.2, eg, 0.8, 1, or 1.2, etc. After many experiments, the inventor realized that the above definition can make the gap between the top foil 130 and the bearing base 110 within a reasonable range, that is, the distance from the highest point to the lowest point of the corrugated foil 120 is limited, so that the gas bearing The structure is more reasonable and stable.
请参见图6至图8，在一些实施例中，当气体轴承作为轴向轴承80时，顶箔130的形状可以配置成平板状，转子42沿其径向形成有止推盘(图中未示出)，顶箔130与止推盘的一面相对，顶箔130与转子42之间形成气膜间隙，气体进入气膜间隙形成动压气膜，不仅可以限定转子42的径向位移，又降低了磨损。Referring to FIGS. 6 to 8 , in some embodiments, when the gas bearing is used as the axial bearing 80 , the shape of the top foil 130 can be configured as a flat plate, and the rotor 42 is formed with a thrust plate (not shown in the figure) along its radial direction. shown), the top foil 130 is opposite to one side of the thrust plate, a gas film gap is formed between the top foil 130 and the rotor 42, and the gas enters the gas film gap to form a dynamic pressure gas film, which can not only limit the radial displacement of the rotor 42, but also reduce the worn out.
在本实施例中，由于顶箔130的形状为平板状，拱起部122的贴合面122a也可以适配地设置成平面，实现该贴合面122a与顶箔130以面接触的方式贴合，增大了拱起部122与顶箔130之间的接触面积，提高了顶箔130的刚度和抗压能力。In this embodiment, since the shape of the top foil 130 is a flat plate, the abutting surface 122a of the arched portion 122 can also be adapted to be flat, so that the abutting surface 122a and the top foil 130 are in surface contact with each other. In combination, the contact area between the arched portion 122 and the top foil 130 is increased, and the rigidity and compression resistance of the top foil 130 are improved.
请参见图6至图8，特别地，当气体轴承作为轴向轴承80时，轴承基体110还可以配置成环形平板状，轴承基体110的内圈用于转子42穿过，并且使得顶箔130与转子42的止推盘相对。优选地，一个止推盘的两侧同时设置顶箔130，以夹持转子42的止推盘，进而限定转子42的轴向位移。Referring to FIGS. 6 to 8 , in particular, when the gas bearing is used as the axial bearing 80 , the bearing base 110 can also be configured as an annular flat plate, the inner ring of the bearing base 110 is used for the rotor 42 to pass through, and the top foil 130 is made to pass through. Opposite to the thrust plate of the rotor 42 . Preferably, top foils 130 are provided on both sides of a thrust disk to clamp the thrust disks of the rotor 42 , thereby limiting the axial displacement of the rotor 42 .
请参见图7和图8，波箔120在轴承基体110的径向方向上呈梯形波浪状延伸，且波箔120朝向顶箔130的梯形顶面构成贴合面122a。由于拱起部122向顶箔130方向凸起，并且波箔120沿轴承基体110的径向延伸，使得波箔120在轴承基体110的径向方向上呈梯形波浪状，拱起部122朝向顶箔130的梯形顶面作为贴合面122a。Referring to FIG. 7 and FIG. 8 , the corrugated foil 120 extends in a trapezoidal wave shape in the radial direction of the bearing base 110 , and the trapezoidal top surface of the corrugated foil 120 facing the top foil 130 forms a bonding surface 122 a. Since the arched portion 122 protrudes toward the top foil 130 , and the corrugated foil 120 extends in the radial direction of the bearing base 110 , the corrugated foil 120 has a trapezoidal wave shape in the radial direction of the bearing base 110 , and the arched portion 122 faces the top. The trapezoidal top surface of the foil 130 serves as the adhering surface 122a.
请参见图6至图8，当气体轴承作为轴向轴承80时，顶箔130的数量为多个，对应地，波箔120的数量可以为多个，顶箔130沿轴承基体110的周向间隔均匀布置，相邻两个顶箔130之间形成间隙，以便于润滑气体流通。Referring to FIGS. 6 to 8 , when the gas bearing is used as the axial bearing 80 , the number of the top foils 130 is multiple, and correspondingly, the number of the corrugated foils 120 can be multiple, and the top foil 130 is along the circumferential direction of the bearing base 110 . The intervals are evenly arranged, and a gap is formed between two adjacent top foils 130 to facilitate the flow of lubricating gas.
在一些实施例中，当气体轴承作为轴向轴承80时，轴承基体110的外径与内径的比值在2至2.4之间，例如2、2.2或者2.4等。发明人通过多次试验后意识到，通过上述限定可以使得轴承基体110的圆环面处于一个合理的范围，有利于设置波箔120和顶箔130，并且使得顶箔130与转子42的止 推盘的相对面积处于合理的范围内，进一步保证了顶箔130的刚度和抗压能力。In some embodiments, when the gas bearing is used as the axial bearing 80, the ratio of the outer diameter to the inner diameter of the bearing base 110 is between 2 and 2.4, such as 2, 2.2, or 2.4. The inventor realized after many experiments that the above-mentioned limitation can make the annular surface of the bearing base 110 be in a reasonable range, which is favorable for setting the corrugated foil 120 and the top foil 130, and makes the thrust of the top foil 130 and the rotor 42 possible. The relative area of the discs is within a reasonable range, which further ensures the rigidity and compression resistance of the top foil 130 .
请参见图9，图9是根据本发明一个实施例的径向轴承中波箔的示意图。在一些实施例中，波箔120上开设有至少一个用于连通波箔120两侧区域的流通孔124。Please refer to FIG. 9 , which is a schematic diagram of a corrugated foil in a radial bearing according to an embodiment of the present invention. In some embodiments, the corrugated foil 120 is provided with at least one flow hole 124 for connecting regions on both sides of the corrugated foil 120 .
在本实施例中，轴承基体110上还可以开设多个进气孔(图中未示出)，用于将润滑气体从该进气孔导出至轴承基体110与顶箔130之间的间隙，使得润滑气体充满该间隙，润滑气体可以直接作用到处于轴承基体110与顶箔130之间的波箔120，进一步提高波箔120的刚度。波箔120上还开设有流通孔124，流通孔124连通波箔120两侧区域，处于波箔120一侧的润滑气体可以通过该流通孔124流至波箔120的另一侧，使润滑气体在气体轴承内更好的流动，防止了转子42与气体轴承接触，避免了接触后对气体轴承的磨损，保证了转子42能够高速运转。In this embodiment, the bearing base 110 may also be provided with a plurality of air inlet holes (not shown in the figure) for guiding the lubricating gas from the air inlet holes to the gap between the bearing base 110 and the top foil 130, When the lubricating gas fills the gap, the lubricating gas can directly act on the corrugated foil 120 between the bearing base 110 and the top foil 130 , thereby further improving the stiffness of the corrugated foil 120 . The corrugated foil 120 is also provided with a circulation hole 124. The circulation hole 124 communicates with the regions on both sides of the corrugated foil 120. The lubricating gas on one side of the corrugated foil 120 can flow to the other side of the corrugated foil 120 through the circulation hole 124, so that the lubricating gas can flow to the other side of the corrugated foil 120. The better flow in the gas bearing prevents the rotor 42 from contacting the gas bearing, avoids the wear of the gas bearing after contact, and ensures that the rotor 42 can run at high speed.
至此，本领域技术人员应认识到，虽然本文已详尽示出和描述了本发明的多个示例性实施例，但是，在不脱离本发明精神和范围的情况下，仍可根据本发明公开的内容直接确定或推导出符合本发明原理的许多其他变型或修改。因此，本发明的范围应被理解和认定为覆盖了所有这些其他变型或修改。By now, those skilled in the art will recognize that although various exemplary embodiments of the present invention have been shown and described in detail herein, the present invention may still be implemented in accordance with the present disclosure without departing from the spirit and scope of the present invention. The content directly determines or derives many other variations or modifications consistent with the principles of the invention. Accordingly, the scope of the present invention should be understood and deemed to cover all such other variations or modifications.

Claims (10)

  1. 一种气体轴承，其特征在于包括：A gas bearing, characterized by comprising:
    轴承基体、顶箔和设置于所述轴承基体和所述顶箔之间的波箔；其中，A bearing base, a top foil, and a corrugated foil disposed between the bearing base and the top foil; wherein,
    所述波箔包括多个间隔设置的拱起部，且每个所述拱起部具有朝向所述顶箔的贴合面，所述贴合面以面接触的方式贴合于所述顶箔表面。The corrugated foil includes a plurality of arched portions arranged at intervals, and each of the arched portions has an adhering surface facing the top foil, and the adhering surface is adhered to the top foil in a surface-contact manner surface.
  2. 根据权利要求1所述的气体轴承，其特征在于，The gas bearing of claim 1, wherein:
    所述气体轴承为径向轴承，所述波箔整体为圆柱状；且The gas bearing is a radial bearing, and the wave foil is cylindrical as a whole; and
    每个所述拱起部的所述贴合面为与所述顶箔外圆面形状匹配的圆弧面。The abutting surface of each of the arched portions is a circular arc surface that matches the shape of the outer circular surface of the top foil.
  3. 根据权利要求2所述的气体轴承，其特征在于，The gas bearing of claim 2, wherein:
    所述波箔在所述气体轴承的周向方向上以梯形波浪状延伸，且所述波箔朝向所述顶箔的梯形顶面构成所述贴合面。The corrugated foil extends in a trapezoidal wave shape in the circumferential direction of the gas bearing, and a trapezoidal top surface of the corrugated foil facing the top foil constitutes the bonding surface.
  4. 根据权利要求2所述的气体轴承，其特征在于，The gas bearing of claim 2, wherein:
    所述顶箔与所述轴承基体直径比在0.8至1.2之间。The top foil to the bearing base diameter ratio is between 0.8 and 1.2.
  5. 根据权利要求1所述的气体轴承，其特征在于，The gas bearing of claim 1, wherein:
    所述气体轴承为轴向轴承，所述顶箔整体为平板状；且The gas bearing is an axial bearing, and the top foil is a flat plate as a whole; and
    每个所述拱起部的所述贴合面为平面。The abutting surface of each of the arched portions is flat.
  6. 根据权利要求5所述的气体轴承，其特征在于，The gas bearing of claim 5, wherein:
    所述轴承基体为环形平板状；The bearing base is in the shape of an annular flat plate;
    所述波箔在所述轴承基体的径向方向上呈梯形波浪状延伸，且其朝向所述顶箔的梯形顶面构成所述贴合面。The corrugated foil extends in a trapezoidal wave shape in the radial direction of the bearing base, and the trapezoidal top surface of the corrugated foil facing the top foil constitutes the bonding surface.
  7. 根据权利要求6所述的气体轴承，其特征在于，The gas bearing of claim 6, wherein:
    所述顶箔的数量为多个且沿所述轴承基体的周向间隔均匀布置。The top foils are plural in number and evenly spaced along the circumferential direction of the bearing base.
  8. 根据权利要求6所述的气体轴承，其特征在于，The gas bearing of claim 6, wherein:
    所述轴承基体的外径与内径的比值在2至2.4之间。The ratio of the outer diameter to the inner diameter of the bearing base is between 2 and 2.4.
  9. 根据权利要求1所述的气体轴承，其特征在于，The gas bearing of claim 1, wherein:
    所述波箔上开设有至少一个用于连通所述波箔两侧区域的流通孔。The corrugated foil is provided with at least one flow hole for connecting the regions on both sides of the corrugated foil.
  10. 一种离心压缩机，其特征在于，包括权利要求1至9中任一项所述的气体轴承。A centrifugal compressor, characterized by comprising the gas bearing according to any one of claims 1 to 9.
PCT/CN2021/130110 2020-11-24 2021-11-11 Gas bearing and centrifugal compressor having same WO2022111294A1 (en)

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CN214274252U (en) * 2020-11-24 2021-09-24 青岛海尔智能技术研发有限公司 Gas bearing and centrifugal compressor with same

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Publication number Priority date Publication date Assignee Title
JP2003148461A (en) * 2001-11-15 2003-05-21 Mitsubishi Heavy Ind Ltd Dynamic pressure type gas bearing and micro gas turbine with dynamic pressure type gas bearing
CN101709747A (en) * 2009-11-17 2010-05-19 西安交通大学 Foil dynamical pressure radial air journal bearing with backward wave foil support
CN101839281A (en) * 2010-05-27 2010-09-22 西安交通大学 Foil dynamical pressure radial gas bearing provided with sectionally-combined composite support
JP2012177458A (en) * 2011-02-28 2012-09-13 Ntn Corp Foil bearing
CN211398261U (en) * 2020-01-09 2020-09-01 珠海格力电器股份有限公司 Dynamic pressure gas radial bearing
CN214274252U (en) * 2020-11-24 2021-09-24 青岛海尔智能技术研发有限公司 Gas bearing and centrifugal compressor with same

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003148461A (en) * 2001-11-15 2003-05-21 Mitsubishi Heavy Ind Ltd Dynamic pressure type gas bearing and micro gas turbine with dynamic pressure type gas bearing
CN101709747A (en) * 2009-11-17 2010-05-19 西安交通大学 Foil dynamical pressure radial air journal bearing with backward wave foil support
CN101839281A (en) * 2010-05-27 2010-09-22 西安交通大学 Foil dynamical pressure radial gas bearing provided with sectionally-combined composite support
JP2012177458A (en) * 2011-02-28 2012-09-13 Ntn Corp Foil bearing
CN211398261U (en) * 2020-01-09 2020-09-01 珠海格力电器股份有限公司 Dynamic pressure gas radial bearing
CN214274252U (en) * 2020-11-24 2021-09-24 青岛海尔智能技术研发有限公司 Gas bearing and centrifugal compressor with same

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