WO2020134451A1 - 推力轴承组件、压缩机和冷媒循环系统 - Google Patents

推力轴承组件、压缩机和冷媒循环系统 Download PDF

Info

Publication number
WO2020134451A1
WO2020134451A1 PCT/CN2019/113292 CN2019113292W WO2020134451A1 WO 2020134451 A1 WO2020134451 A1 WO 2020134451A1 CN 2019113292 W CN2019113292 W CN 2019113292W WO 2020134451 A1 WO2020134451 A1 WO 2020134451A1
Authority
WO
WIPO (PCT)
Prior art keywords
thrust
thrust bearing
positioning
bearing assembly
positioning ring
Prior art date
Application number
PCT/CN2019/113292
Other languages
English (en)
French (fr)
Inventor
刘华
张治平
钟瑞兴
李宏波
周宇
陈玉辉
亓静利
叶文腾
刘胜
Original Assignee
珠海格力电器股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Publication of WO2020134451A1 publication Critical patent/WO2020134451A1/zh

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element

Definitions

  • the present disclosure relates to the technical field of rotating machinery and refrigeration, in particular to a thrust bearing assembly, a compressor and a refrigerant circulation system.
  • Thrust bearings also known as thrust bearings
  • thrust bearings are often used to withstand the axial force of the rotating shaft and limit the axial position of the rotating shaft.
  • the clearance of the thrust bearing is very small.
  • the clearance of the gas bearing is very small, only to the order of micron or tens of microns, and the machining accuracy of parts is required to be sub-micron.
  • the precision of parts processing and assembly is very high.
  • two thrust bearings are often provided at one end of the shaft to perform two-way thrust thrust on the rotating shaft. In order to ensure high rotation speed and high-precision rotation of the rotating shaft, the accuracy requirements for the clearance of the thrust bearing are becoming higher and higher.
  • a first aspect of the present disclosure discloses a thrust bearing assembly, including:
  • the first thrust bearing includes a first thrust surface and a first positioning surface, the first thrust surface and the first positioning surface are disposed on the same side of the first thrust bearing, and are located on the diameter of the first positioning surface Protruding inward and axially outward relative to the first positioning surface;
  • the second thrust bearing includes a second thrust surface and a second positioning surface, the second thrust surface and the second positioning surface are disposed on the same side of the second thrust bearing, and are located at a diameter of the second positioning surface Protruding inward and axially outward with respect to the second positioning surface, the second thrust surface is opposite to the first thrust surface, and the second positioning surface is opposite to the first positioning surface; and
  • a positioning ring is provided between the first thrust bearing and the second thrust bearing, and includes a first mating surface that fits the first positioning surface and a second fit that fits the second positioning surface The surface is used to define the interval between the first thrust surface and the second thrust surface by the distance between the first mating surface and the second mating surface.
  • the first thrust bearing and the second thrust bearing are gas bearings.
  • the positioning ring includes a fluid channel connecting the radially inner side and the radially outer side of the positioning ring.
  • the fluid channel is located on one end face of the positioning ring.
  • the fluid channel includes at least one of a groove and a hole provided on the positioning ring.
  • the fluid channel includes a plurality of grooves distributed along the circumference of the positioning ring.
  • the grooves are radial grooves, and a plurality of the radial grooves are evenly distributed along the circumferential direction of the positioning ring.
  • the first mating surface and the second mating surface of the positioning ring are the outermost planes of the two end surfaces of the positioning ring.
  • the positioning ring is provided with a through hole for mounting the positioning ring on the first thrust bearing or the second thrust bearing.
  • a second aspect of the present disclosure discloses a compressor, including:
  • Compressor rotors including thrust disks
  • the thrust bearing assembly is the thrust bearing assembly of the first aspect of the present disclosure, and the two end surfaces of the thrust disk respectively cooperate with the first thrust surface and the second thrust surface of the thrust bearing assembly.
  • the compressor is a centrifugal compressor.
  • a third aspect of the present disclosure provides a refrigerant circulation system including the compressor described in the second aspect of the present disclosure.
  • the positioning ring when the rotating shaft is thrust in both directions by the thrust member of the rotating shaft, the positioning ring is used to utilize the first and second matching surfaces of the positioning ring and the first positioning of the first thrust bearing And the second positioning surface of the second thrust bearing to define the interval between the first thrust surface and the second thrust surface, you can adjust the positioning ring's first mating surface and the second mating surface
  • the gap adjusts the sum of the clearance between the thrust member of the rotating shaft and the first thrust bearing and the clearance between the second thrust bearing.
  • the first thrust surface of the first thrust bearing protrudes outward in the axial direction relative to the first positioning surface
  • the second thrust surface of the second thrust bearing protrudes outward in the axial direction relative to the first positioning surface.
  • the first thrust surface of the first thrust bearing and the second thrust surface of the second thrust bearing are more conveniently processed by grinding and other higher precision machining methods, which helps to ensure the accuracy of the first thrust bearing and the second thrust bearing, thereby also It further guarantees the clearance requirements of the thrust bearing assembly during operation.
  • the compressor based on the thrust bearing assembly provided by the present disclosure and the refrigerant circulation system provided with the compressor also have corresponding beneficial effects of the thrust bearing assembly provided by the present disclosure.
  • FIG. 1 is a schematic structural view of a thrust bearing assembly installed in a compressor according to an embodiment of the present disclosure
  • FIG. 2 is a schematic structural view of the positioning ring of the thrust bearing assembly of the embodiment shown in FIG. 1.
  • spatially relative terms such as “above”, “above”, “above”, “above”, etc. can be used here to describe as shown in the figure The spatial relationship between a device or feature shown and other devices or features. It should be understood that spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation of the device described in the figures. For example, if the device in the drawings is turned upside down, a device described as “above another device or configuration” or “above another device or configuration” will then be positioned as “below other device or configuration” or “in Under other devices or structures”. Thus, the exemplary term “above” may include both “above” and “below” orientations. The device can also be positioned in other different ways (rotated 90 degrees or at other orientations), and the relative description of the space used here is explained accordingly.
  • the thrust bearing assembly of some embodiments of the present disclosure includes a first thrust bearing 6, a second thrust bearing 9 and a positioning ring 8.
  • the first thrust bearing 6 includes a first thrust surface 62 and a first positioning surface 61.
  • the first thrust surface 62 and the first positioning surface 61 are provided on the same side of the first thrust bearing 6, are located radially inward of the first positioning surface 61, and protrude outward in the axial direction relative to the first positioning surface 61.
  • the second thrust bearing 9 includes a second thrust surface 92 and a second positioning surface 91.
  • the second thrust surface 92 and the second positioning surface 91 are provided on the same side of the second thrust bearing 9, are located radially inward of the second positioning surface 91, and protrude outward in the axial direction relative to the second positioning surface 91.
  • the second thrust surface 92 is opposed to the first thrust surface 62, and the second positioning surface 91 is opposed to the first positioning surface 61.
  • the positioning ring 8 is provided between the first thrust bearing 6 and the second thrust bearing 9 and includes a first mating surface 81 that fits the first positioning surface 61 and a second mating surface 82 that fits the second positioning surface 91.
  • the distance between the first thrust surface 62 and the second thrust surface 92 is defined by the distance between the first mating surface 81 and the second mating surface 82.
  • the first thrust surface 62 of the first thrust bearing 6 and the second thrust surface 92 of the second thrust bearing 9 are respectively used to cooperate with the mating surfaces on both sides of the thrust member of the rotating shaft 13, in the embodiment shown in FIG.
  • the first thrust surface 62 and the second thrust surface 92 respectively cooperate with the left and right end surfaces of the thrust plate 3 fixedly connected to the rotating shaft 13 of the compressor.
  • the first thrust surface 62 is used to receive the left axial force of the rotating shaft 13, and the second thrust surface 92 is used to receive the right axial force of the rotating shaft 13.
  • the first positioning surface 61 of the first thrust bearing 6 and the second positioning surface 91 of the second thrust bearing 9 are used to determine the interval between the first thrust surface 62 and the second thrust surface 92.
  • the first positioning surface 62 and the second positioning surface 92 are fitted to the first matching surface 81 and the second matching surface 82 of the positioning ring 8 respectively, so that the first matching surface 81 and the second positioning surface 8 of the positioning ring 8
  • the distance between the mating surfaces 82 defines the distance between the first thrust bearing 6 and the second thrust bearing 9, that is, the distance between the first thrust surface 62 and the second thrust surface 92, which also defines the simultaneous
  • the first thrust surface 62 of the first thrust bearing 6 and/or the second thrust surface 92 of the second thrust bearing 9 After a period of work wear, the interval between the first thrust surface 62 and the second thrust bearing 9 becomes larger, so that the clearance between the left end surface of the thrust plate 3 and the first thrust surface 62 and the right end surface and the second thrust The sum of the fitting clearances of the face 92 becomes larger, and it is necessary to reduce the clearance of the thrust bearing assembly.
  • the thrust bearing assembly can be taken out of the compressor, the gap after the thrust bearing assembly is worn out is measured, and the adjustment amount of the positioning ring 8 that is required is determined according to the gap.
  • the positioning ring 8 is fixedly connected to the second thrust bearing 9, and then the first positioning surface 62 of the first thrust bearing 6 is fitted with the first mating surface 81, and the diffuser 7 at the left end of the first thrust bearing 6 is installed. , Tighten the diffuser 7 to press the first thrust bearing 6 against the positioning ring 8.
  • the first thrust surface 62 of the first thrust bearing 6 is located radially inward of the first positioning surface 61, that is, the first thrust surface 62 is located in the middle of the first thrust bearing 6, and the first positioning surface 61 is located outside the first thrust bearing 6 .
  • the first thrust surface 62 protrudes outward in the axial direction with respect to the first positioning surface 61, that is, the first thrust bearing 6 has a stepped shape with a central protrusion on the side where the first positioning surface 61 and the first thrust surface 62 are located. Since the first thrust surface 62 is a working surface that cooperates with the thrust member, the accuracy requirement is high. Since the positioning accuracy of the first positioning surface 61 can be adjusted by the positioning ring 8, the accuracy requirement of the first positioning surface 61 is relatively low .
  • This arrangement is advantageous for high-precision machining of the first thrust surface 62 of the first thrust bearing 6, such as plane grinding.
  • the same arrangement of the second thrust surface 92 and the second positioning surface 91 of the second thrust bearing 9 also helps to realize the high-precision machining of the second thrust surface 92 of the second thrust bearing 9.
  • the clearance of the thrust bearing assembly of this embodiment is easy to adjust, and at the same time, the first thrust bearing 6 and the second thrust bearing 9 are easily processed with high precision.
  • the first thrust bearing 6 and the second thrust bearing 9 are gas bearings, such as static pressure gas bearings or dynamic pressure gas bearings.
  • the gas bearing uses gas to form a gas film between the thrust surface of the thrust bearing and the thrust member, which has the advantages of high speed and low noise.
  • pressure gas may be injected between the left end surface of the thrust plate 3 of the compressor and the first thrust surface 61 , So that a gas film can be formed between the left end surface of the thrust plate 3 and the first thrust surface 61.
  • first thrust bearing 6 and the second thrust bearing 9 adopt static pressure gas bearings, they can have the advantages of ultra-high rotation accuracy, ultra-low friction, ultra-low vibration, ultra-low noise, long life, no pollution, etc., suitable for high speed and High-precision applications are suitable for centrifugal compressors, especially miniaturized centrifugal compressors.
  • the positioning ring 8 includes a fluid channel connecting the radially inner side and the radially outer side of the positioning ring 8.
  • this arrangement can enable the exhaust gas between the thrust member and the thrust surface of the gas bearing to be smoothly discharged from the fluid channel to the outside of the positioning ring 8.
  • the back pressure of the gas bearing is increased to affect the gas film pressure distribution inside the bearing, thereby affecting the gas bearing stiffness and Carrying capacity, and prevent air hammer vibration.
  • This embodiment contributes to smooth exhaust of the gas bearing and improves the rotation stability of the gas bearing rotor system.
  • the fluid channel is located on one end face of the positioning ring 8.
  • the fluid channel is provided on the left end surface of the positioning ring 8. This arrangement can facilitate the processing of the fluid channel and make the structure of the positioning ring 8 more compact. Compared with the provision of fluid channels on both end surfaces, the processing impact on the mating surface of the positioning ring 8 is reduced.
  • the fluid channel includes a groove 83 provided on the end surface of the positioning ring 8.
  • This arrangement is convenient for processing the fluid channel, the structure of the positioning ring 8 is simple, and it also contributes to the smooth exhaust of the gas bearing.
  • the fluid channel includes a plurality of grooves 83 distributed circumferentially. This setting further contributes to the smooth exhaust of the gas bearing and improves the exhaust stability of the gas bearing.
  • the groove 83 is a radial groove, and a plurality of radial grooves are evenly distributed along the circumferential direction of the positioning ring 8. This setting helps to facilitate the processing of the positioning ring 8.
  • the fluid channel may be provided as a hole that penetrates the radially inner side and the radially outer side of the positioning ring 8.
  • the first mating surface 81 and the second mating surface 82 of the positioning ring 8 are the outermost planes of the two end surfaces of the positioning ring 8. This setting helps to facilitate the adjustment and processing of the mating surface of the positioning ring 8 by plane grinding, and helps to improve the dimensional accuracy, shape accuracy and positioning accuracy of the positioning ring 8.
  • the positioning ring 8 is provided with a through hole for mounting the positioning ring 8 on the first thrust bearing 6 or the second thrust bearing 9. As shown in FIGS. 1 and 2, the positioning ring 8 is provided with a through hole, and the positioning ring 8 can be installed and attached to the second thrust bearing 9 by using the screw 2, and the second thrust bearing can also be installed on the compressor On the bearing mount of the body 1.
  • Some embodiments of the present disclosure also provide a compressor including a compressor rotor and the aforementioned thrust bearing assembly.
  • the compressor rotor includes a rotating shaft 13 and a thrust disk 3 fixed on the rotating shaft 13; the two end surfaces of the thrust disk 3 cooperate with the first thrust surface 62 and the second thrust surface 92 of the thrust bearing assembly, respectively.
  • the compressor is a centrifugal compressor.
  • Some embodiments of the present disclosure also provide a refrigerant circulation system, including the compressor of the foregoing embodiments of the present disclosure.

Landscapes

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

Abstract

一种推力轴承组件、压缩机和冷媒循环系统。推力轴承组件包括：第一推力轴承（6），其第一推力面（62）与其第一定位面（61）设置于第一推力轴承（6）的同一侧，第一推力面（62）位于第一定位面（61）的径向内侧且相对于第一定位面（61）沿轴向向外侧凸出；第二推力轴承（9），其第二推力面（92）与其第二定位面（91）设置于第二推力轴承（9）的同一侧，第二推力面（92）位于第二定位面（91）的径向内侧且相对于第二定位面（91）沿轴向向外侧凸出，第二推力面（92）与第一推力面（62）相对，第二定位面（91）与第一定位面（61）相对；定位环（8），设于第一推力轴承（6）和第二推力轴承（9）之间，包括与第一定位面（61）贴合的第一配合面（81）和与第二定位面（91）贴合的第二配合面（82）。该推力轴承通过定位环可以方便地调整推力轴承组件的间隔。

Description

推力轴承组件、压缩机和冷媒循环系统
相关申请
本公开是以申请号为201811593272.1，申请日为2018年12月25日，发明名称为“推力轴承组件、压缩机和冷媒循环系统”的中国专利申请为基础，并主张其优先权，该中国专利申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及旋转机械和制冷技术领域，特别涉及一种推力轴承组件、压缩机和冷媒循环系统。
背景技术
推力轴承又叫止推轴承，常用于承受转轴的轴向力和对转轴进行轴向限位。在一些高转速、高精度的场合中，对推力轴承的安装和加工要求很高。推力轴承的间隙很小，例如对于静压气体轴承，由于气膜很薄，气体轴承的间隙非常小，只有微米级或数十微米级的程度，且要求零件的加工精度为亚微米级，对部件加工和装配精度要求很高。在一些转轴的应用场合中，常常在轴的一端设置两个推力轴承对转轴进行双向止推，为了保证转轴的高转速和高精度的转动，对于推力轴承的间隙的精度要求越来越高。
发明内容
本公开第一方面公开一种推力轴承组件，包括：
第一推力轴承，包括第一推力面和第一定位面，所述第一推力面与所述第一定位面设置于所述第一推力轴承的同一侧，位于所述第一定位面的径向内侧且相对于所述第一定位面沿轴向向外侧凸出；
第二推力轴承，包括第二推力面和第二定位面，所述第二推力面与所述第二定位面设置于所述第二推力轴承的同一侧，位于所述第二定位面的径向内侧且相对于所述第二定位面沿轴向向外侧凸出，所述第二推力面与所述第一推力面相对，所述第二定位面与所述第一定位面相对；和
定位环，设于所述第一推力轴承和所述第二推力轴承之间，包括与所述第一定位 面贴合的第一配合面和与所述第二定位面贴合的第二配合面，用于通过所述第一配合面与所述第二配合面的间距限定所述第一推力面与所述第二推力面之间的间隔。
在一些实施例中，所述第一推力轴承和所述第二推力轴承为气体轴承.
在一些实施例中，所述定位环包括连通所述定位环的径向内侧与径向外侧的流体通道。
在一些实施例中，所述流体通道位于所述定位环的一侧端面上。
在一些实施例中，所述流体通道包括设于所述定位环上的槽和孔至少之一。
在一些实施例中，所述流体通道包括沿所述定位环的周向分布的多个槽。
在一些实施例中，所述槽为径向槽，多个所述径向槽沿所述定位环的周向均匀分布。
在一些实施例中，所述定位环的所述第一配合面和所述第二配合面为所述定位环的两端面的最外侧的平面。
在一些实施例中，所述定位环设有用于与将所述定位环安装在所述第一推力轴承或所述第二推力轴承上的通孔。
本公开第二方面公开一种压缩机，包括：
压缩机转子，包括推力盘；和
推力轴承组件，为本公开第一方面的推力轴承组件，所述推力盘的两个端面分别与所述推力轴承组件的所述第一推力面和所述第二推力面配合。
在一些实施例中，所述压缩机为离心式压缩机。
本公开第三方面提供一种冷媒循环系统，包括本公开第二方面所述的压缩机。
基于本公开提供的推力轴承组件，在通过转轴的推力件对转轴进行双向止推时，通过设置定位环，利用定位环的第一配合面和第二配合面与第一推力轴承的第一定位面和第二推力轴承的第二定位面之间的配合来对第一推力面和的第二推力面之间的间隔进行限定，可以通过调整定位环的第一配合面与第二配合面的间距来调整转轴的推力件与第一推力轴承的间隙和第二推力轴承的间隙之和。同时，第一推力轴承的第一推力面相对于第一定位面沿轴向向外侧凸出，第二推力轴承的第二推力面相对于第一定位面沿轴向向外侧凸出，也使得对第一推力轴承的第一推力面和第二推力轴承的第二推力面通过磨削等较高精度加工方式的加工更加方便，有助于保证第一推力轴承和第二推力轴承的精度，从而也进一步保证了对推力轴承组件在工作时的间隙要求。
基于本公开提供的应用该推力轴承组件的压缩机和具有该压缩机的冷媒循环系 统，也具有本公开提供的推力轴承组件相应的有益效果。
通过以下参照附图对本公开的示例性实施例的详细描述，本公开的其它特征及其优点将会变得清楚。
附图说明
此处所说明的附图用来提供对本公开的进一步理解，构成本公开的一部分，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：
图1为本公开一实施例的推力轴承组件安装在压缩机中的结构示意图；
图2为图1所示实施例的推力轴承组件的定位环的结构示意图。
具体实施方式
下面将结合本公开实施例中的附图，对本公开实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本公开一部分实施例，而不是全部的实施例。以下对至少一个示例性实施例的描述实际上仅仅是说明性的，决不作为对本公开及其应用或使用的任何限制。基于本公开中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本公开保护的范围。
除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、数字表达式和数值不限制本公开的范围。同时，应当明白，为了便于描述，附图中所示出的各个部分的尺寸并不是按照实际的比例关系绘制的。对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，所述技术、方法和设备应当被视为授权说明书的一部分。在这里示出和讨论的所有示例中，任何具体值应被解释为仅仅是示例性的，而不是作为限制。因此，示例性实施例的其它示例可以具有不同的值。应注意到：相似的标号和字母在下面的附图中表示类似项，因此，一旦某一项在一个附图中被定义，则在随后的附图中不需要对其进行进一步讨论。
为了便于描述，在这里可以使用空间相对术语，如“在……之上”、“在……上方”、“在……上表面”、“上面的”等，用来描述如在图中所示的一个器件或特征与其他器件或特征的空间位置关系。应当理解的是，空间相对术语旨在包含除了器件在图中所描述的方位之外的在使用或操作中的不同方位。例如，如果附图中的器件被倒置，则描述为“在其他器件或构造上方”或“在其他器件或构造之上”的器件之后 将被定位为“在其他器件或构造下方”或“在其他器件或构造之下”。因而，示例性术语“在……上方”可以包括“在……上方”和“在……下方”两种方位。该器件也可以其他不同方式定位(旋转90度或处于其他方位)，并且对这里所使用的空间相对描述作出相应解释。
如图1、图2所示，本公开一些实施例的推力轴承组件包括第一推力轴承6、第二推力轴承9和定位环8。第一推力轴承6包括第一推力面62和第一定位面61。第一推力面62与第一定位面61设置于第一推力轴承6的同一侧，位于第一定位面61的径向内侧且相对于第一定位面61沿轴向向外侧凸出。第二推力轴承9包括第二推力面92和第二定位面91。第二推力面92与第二定位面91设置于第二推力轴承9的同一侧，位于第二定位面91的径向内侧且相对于第二定位面91沿轴向向外侧凸出。第二推力面92与第一推力面62相对，第二定位面91与第一定位面61相对。定位环8设于第一推力轴承6和第二推力轴承9之间，包括与第一定位面61贴合的第一配合面81和与第二定位面91贴合的第二配合面82，用于通过第一配合面81与第二配合面82的间距限定第一推力面62与第二推力面92之间的间隔。
第一推力轴承6的第一推力面62和第二推力轴承9的第二推力面92分别用于与转轴13的止推件的两侧的配合面相配合，在图1所示的实施例中第一推力面62和第二推力面92分别与压缩机的转轴13上固定连接的推力盘3的左端面和右端面相配合。第一推力面62用于承受转轴13的向左的轴向力，第二推力面92用于承受转轴13的向右的轴向力。
第一推力轴承6的第一定位面61和第二推力轴承9的第二定位面91用于确定第一推力面62与第二推力面92之间的间隔。在本实施例中第一定位面62和第二定位面92通过分别与定位环8的第一配合面81和第二配合面82贴合，从而定位环8的第一配合面81和第二配合面82之间的距离限定了第一推力轴承6和第二推力轴承9之间的距离，即限定了第一推力面62与第二推力面92之间的间隔，也即限定了同时与第一推力面62和第二推力面92配合的止推件与第一推力面62的配合间隙和第二推力面92的配合间隙之和。从而通过调整定位环8的第一配合面81和第二配合面82的距离可以调整推力轴承组件的工作时的间隙。
在需要调小推力轴承组件的工作间隙时，例如在如图1所示的压缩机中，第一推力轴承6的第一推力面62和/或第二推力轴承9的第二推力面92由于经过一段时间的工作磨损，导致第一推力面62和第二推力轴承9之间的间隔变大，从而止推盘3的 左端面与第一推力面62的配合间隙与右端面和第二推力面92的配合间隙之和变大，需要减小推力轴承组件的间隙。此时可以将推力轴承组件从压缩机中取出，测量推力轴承组件磨损后的间隙，根据该间隙确定需要对定位环8的调整量。然后将定位环8从推力轴承组件中取出，根据确定的调整量通过磨削等加工方式对定位环8的第一配合面81和/或第二配合面82进行加工，以减小第一配合面81和第二配合面82之间的间距，然后将第二推力轴承9固定在压缩机的机体1的轴承安装座上，将定位环8的第二配合面82与第二定位面92贴合后将定位环8固定连接于第二推力轴承9，然后再将第一推力轴承6的第一定位面62与第一配合面81贴合，安装第一推力轴承6左端的扩压器7，紧固扩压器7以将第一推力轴承6压紧在定位环8上。
在需要调大推力轴承的工作间隙时，更换一个第一配合面81和第二配合面82距离合适的定位环8即可。通过设置定位环8，可以方便地调整推力轴承组件的间隙。
第一推力轴承6的第一推力面62位于第一定位面61的径向内侧，即第一推力面62位于第一推力轴承6的中部，第一定位面61位于第一推力轴承6的外部。第一推力面62相对于第一定位面61沿轴向向外侧凸出，即第一推力轴承6在第一定位面61和第一推力面62所在的一侧为中部凸出的台阶状。由于第一推力面62为与止推件配合工作的工作表面，其精度要求高，第一定位面61的定位精度由于可以靠定位环8来调整，第一定位面61的精度要求相对较低。该种设置有利于对第一推力轴承6的第一推力面62的高精度加工，例如平面磨削加工。同理，第二推力轴承9的第二推力面92和第二定位面91的同种设置也有助于实现对第二推力轴承9的第二推力面92的高精度加工。
本实施例的推力轴承组件的间隙易于调整，同时第一推力轴承6和第二推力轴承9易于实现高精度加工。
在一些实施例中，第一推力轴承6和第二推力轴承9为气体轴承，例如可以为静压气体轴承或动压气体轴承。气体轴承采用利用气体在推力轴承的推力面与推力件之间形成气膜，具有高转速、低噪音等优点。例如，在图1所示的压缩机的实施例中，第一推力轴承6为静压气体轴承时，可以在压缩机的止推盘3的左端面和第一推力面61之间注入压力气体，使止推盘3的左端面和第一推力面61之间可以形成气膜。第一推力轴承6和第二推力轴承9采用静压气体轴承后，可以具有超高回转精度、超低摩擦、超低振动、超低噪音、寿命长、无污染等优点，适用于高转速和高精度场合，例如适合在离心压缩机特别是小型化离心压缩机中应用。
在一些实施例中，定位环8包括连通定位环8的径向内侧与径向外侧的流体通道。在第一推力轴承6和第二推力轴承9为气体轴承的实施例中，该设置可以使气体轴承的止推件和推力面之间的排气从流体通道向定位环8的外侧顺利排出，从而防止排气滞留在第一推力轴承6和第二推力轴承9的推力面和止推件之间，防止由于气体轴承的背压升高影响轴承内部气膜压力分布，从而影响气体轴承刚度和承载力，以及防止发生气锤振动。本实施例有助于使气体轴承的排气顺畅，提高气体轴承转子系统的转动稳定性。
在一些实施例中，流体通道位于定位环8的一侧端面上。如图1、图2所示的实施例中，流体通道设于定位环8的左端面上。该设置可以使流体通道加工方便，使定位环8的结构更紧凑，相比较于在两侧端面都设有流体通道，减少了对定位环8的配合面的加工影响。
在一些实施例中，如图1、图2所示，流体通道包括设于定位环8的端面上的槽83。该设置便于加工流体通道，定位环8的结构简单，同时也有助于气体轴承的顺利排气。
在一些实施例中，如图2所示，流体通道包括沿周向分布的多个槽83。该设置进一步有助于气体轴承的顺利排气，提高了气体轴承的排气稳定性。
在一些实施例中，槽83为径向槽，多个径向槽沿定位环8的周向均匀分布。该设置有助于方便对定位环8的加工。
在未图示的实施例中，流体通道也可以设置为贯穿定位环8的径向内侧和径向外侧的孔。
在一些实施例中，定位环8的第一配合面81和第二配合面82为定位环8的两端面的最外侧的平面。该设置有助于方便通过平面磨削方式对定位环8的配合面的调整和加工，有助于提高定位环8的尺寸精度、形状精度和定位精度。
在一些实施例中，定位环8设有用于与将定位环8安装在第一推力轴承6或第二推力轴承9上的通孔。如图1、图2所示，定位环8上设有通孔，可以利用螺钉2将定位环8安装并贴合在第二推力轴承9上，同时还可以将第二推力轴承安装在压缩机的机体1的轴承安装座上。
本公开一些实施例还提供一种压缩机，压缩机包括压缩机转子和前述的推力轴承组件。如图1所示，压缩机转子包括转轴13和固定在转轴13上的推力盘3；推力盘3的两个端面分别与推力轴承组件的第一推力面62和第二推力面92配合。
在一些实施例中，压缩机为离心式压缩机。
本公开一些实施例还提供一种冷媒循环系统，包括本公开前述实施例的压缩机。
最后应当说明的是：以上实施例仅用以说明本公开的技术方案而非对其限制；尽管参照较佳实施例对本公开进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本公开的具体实施方式进行修改或者对部分技术特征进行等同替换；而不脱离本公开技术方案的精神，其均应涵盖在本公开请求保护的技术方案范围当中。

Claims (12)

  1. 一种推力轴承组件，包括：
    第一推力轴承(6)，包括第一推力面(62)和第一定位面(61)，所述第一推力面(62)与所述第一定位面(61)设置于所述第一推力轴承(6)的同一侧，所述第一推力面(62)位于所述第一定位面(61)的径向内侧且相对于所述第一定位面(61)沿轴向向外侧凸出；
    第二推力轴承(9)，包括第二推力面(92)和第二定位面(91)，所述第二推力面(92)与所述第二定位面(91)设置于所述第二推力轴承(9)的同一侧，所述第二推力面(92)位于所述第二定位面(91)的径向内侧且相对于所述第二定位面(91)沿轴向向外侧凸出，所述第二推力面(92)与所述第一推力面(62)相对，所述第二定位面(91)与所述第一定位面(61)相对；和
    定位环(8)，设于所述第一推力轴承(6)和所述第二推力轴承(9)之间，包括与所述第一定位面(61)贴合的第一配合面(81)和与所述第二定位面(91)贴合的第二配合面(82)，用于通过所述第一配合面(81)与所述第二配合面(82)的间距限定所述第一推力面(62)与所述第二推力面(92)之间的间隔。
  2. 如权利要求1所述的推力轴承组件，其中所述第一推力轴承(6)和所述第二推力轴承(9)为气体轴承。
  3. 如权利要求1所述的推力轴承组件，其中所述定位环(8)包括连通所述定位环(8)的径向内侧与径向外侧的流体通道。
  4. 如权利要求3所述的推力轴承组件，其中所述流体通道位于所述定位环(8)的一侧端面上。
  5. 如权利要求3所述的推力轴承组件，其中所述流体通道包括设于所述定位环(8)上的槽(83)和孔至少之一。
  6. 如权利要求3所述的推力轴承组件，其中所述流体通道包括沿所述定位环(8) 的周向分布的多个槽(83)。
  7. 如权利要求6所述的推力轴承组件，其中所述槽(83)为径向槽，多个所述径向槽沿所述定位环(8)的周向均匀分布。
  8. 如权利要求1所述的推力轴承组件，其中所述定位环(8)的所述第一配合面(81)和所述第二配合面(82)为所述定位环(8)的两端面的最外侧的平面。
  9. 如权利要求1至8任一所述的推力轴承组件，其中所述定位环(8)设有用于与将所述定位环(8)安装在所述第一推力轴承(6)或所述第二推力轴承(9)上的通孔。
  10. 一种压缩机，包括：
    压缩机转子，包括推力盘；和
    推力轴承组件，为权利要求1至9任一所述的推力轴承组件，所述推力盘的两个端面分别与所述推力轴承组件的所述第一推力面(62)和所述第二推力面(92)配合。
  11. 如权利要求10所述的压缩机，其中所述压缩机为离心式压缩机。
  12. 一种冷媒循环系统，包括权利要求10或11所述的压缩机。
PCT/CN2019/113292 2018-12-25 2019-10-25 推力轴承组件、压缩机和冷媒循环系统 WO2020134451A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201811593272.1 2018-12-25
CN201811593272.1A CN111365278A (zh) 2018-12-25 2018-12-25 推力轴承组件、压缩机和冷媒循环系统

Publications (1)

Publication Number Publication Date
WO2020134451A1 true WO2020134451A1 (zh) 2020-07-02

Family

ID=71126875

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2019/113292 WO2020134451A1 (zh) 2018-12-25 2019-10-25 推力轴承组件、压缩机和冷媒循环系统

Country Status (2)

Country Link
CN (1) CN111365278A (zh)
WO (1) WO2020134451A1 (zh)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002206554A (ja) * 2001-01-11 2002-07-26 Origin Electric Co Ltd ベアリングユニット及びそれを用いた駆動装置、回転円板支承装置
CN2832364Y (zh) * 2005-10-26 2006-11-01 广东工业大学 高速高刚度复合多支承气体静压轴承电主轴
JP2009124900A (ja) * 2007-11-16 2009-06-04 Asmo Co Ltd ブラシレスモータ
CN202082296U (zh) * 2011-05-25 2011-12-21 江苏齐航数控机床有限责任公司 组合轴承间隙调整结构
JP2014139462A (ja) * 2013-01-21 2014-07-31 Nsk Ltd ステアリング装置
CN104828744A (zh) * 2015-03-17 2015-08-12 如皋市非标轴承有限公司 一种叉车用新型复合轴承
CN209195802U (zh) * 2018-12-25 2019-08-02 珠海格力电器股份有限公司 推力轴承组件、压缩机和冷媒循环系统
CN209414201U (zh) * 2018-12-25 2019-09-20 珠海格力电器股份有限公司 压缩机和冷媒循环系统

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002206554A (ja) * 2001-01-11 2002-07-26 Origin Electric Co Ltd ベアリングユニット及びそれを用いた駆動装置、回転円板支承装置
CN2832364Y (zh) * 2005-10-26 2006-11-01 广东工业大学 高速高刚度复合多支承气体静压轴承电主轴
JP2009124900A (ja) * 2007-11-16 2009-06-04 Asmo Co Ltd ブラシレスモータ
CN202082296U (zh) * 2011-05-25 2011-12-21 江苏齐航数控机床有限责任公司 组合轴承间隙调整结构
JP2014139462A (ja) * 2013-01-21 2014-07-31 Nsk Ltd ステアリング装置
CN104828744A (zh) * 2015-03-17 2015-08-12 如皋市非标轴承有限公司 一种叉车用新型复合轴承
CN209195802U (zh) * 2018-12-25 2019-08-02 珠海格力电器股份有限公司 推力轴承组件、压缩机和冷媒循环系统
CN209414201U (zh) * 2018-12-25 2019-09-20 珠海格力电器股份有限公司 压缩机和冷媒循环系统

Also Published As

Publication number Publication date
CN111365278A (zh) 2020-07-03

Similar Documents

Publication Publication Date Title
US6623164B1 (en) Hydrodynamic journal bearing
US11608833B2 (en) Centrifugal compressor and air conditioning equipment
CN105202014B (zh) 一种槽式动压气体径向轴承
WO2020134430A1 (zh) 轴承支撑组件及其加工方法、离心压缩机
CN209414201U (zh) 压缩机和冷媒循环系统
CN109707637B (zh) 一种双气悬浮支撑的小微型离心压缩机
CN207709894U (zh) 一种复合节流式静压气浮电主轴
WO2020134451A1 (zh) 推力轴承组件、压缩机和冷媒循环系统
WO2020134518A1 (zh) 轴承承载部件、压缩机和冷媒循环系统
CN108941623B (zh) 一种复合节流式静压气浮电主轴
US9765791B2 (en) Turbo compressor
CN109899303B (zh) 一种无径向轴承的小微型离心压缩机
CN209195802U (zh) 推力轴承组件、压缩机和冷媒循环系统
JP3779186B2 (ja) 静圧気体軸受
CN113685440B (zh) 气浮旋转组件以及包含其的磁流体密封件
CN109707638B (zh) 一种轴承和密封一体化的小微型离心压缩机
CN209340195U (zh) 推力盘两侧设置推力轴承的转子装配组件、压缩机及空调
TWI646271B (zh) 多孔質氣靜壓軸承
WO2020134424A1 (zh) 压缩机转子、压缩机和冷媒循环系统
WO2020134516A1 (zh) 轴封部件、压缩机和冷媒循环系统
CN111365257A (zh) 压缩机和冷媒循环系统
WO2020134435A1 (zh) 压缩机以及冷媒循环系统
TWI612232B (zh) 液靜壓主軸軸向油腔裝置
CN218509979U (zh) 静压气体轴承组件和压缩机
CN109751254B (zh) 一种立式小微型气悬浮离心压缩机

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19902872

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19902872

Country of ref document: EP

Kind code of ref document: A1