WO2022021663A1 - 压缩机 - Google Patents

压缩机 Download PDF

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Publication number
WO2022021663A1
WO2022021663A1 PCT/CN2020/127437 CN2020127437W WO2022021663A1 WO 2022021663 A1 WO2022021663 A1 WO 2022021663A1 CN 2020127437 W CN2020127437 W CN 2020127437W WO 2022021663 A1 WO2022021663 A1 WO 2022021663A1
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WO
WIPO (PCT)
Prior art keywords
rotor
compressor
shaft
counterweight assembly
upper counterweight
Prior art date
Application number
PCT/CN2020/127437
Other languages
English (en)
French (fr)
Inventor
吴严欢
贾祥敏
吴建刚
刘刚
Original Assignee
艾默生环境优化技术(苏州)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
Priority claimed from CN202010751034.XA external-priority patent/CN114060276A/zh
Priority claimed from CN202021551090.0U external-priority patent/CN212717165U/zh
Application filed by 艾默生环境优化技术(苏州)有限公司 filed Critical 艾默生环境优化技术(苏州)有限公司
Publication of WO2022021663A1 publication Critical patent/WO2022021663A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/04—Balancing means

Definitions

  • the present disclosure relates to a compressor.
  • the present disclosure relates to inverter scroll compressors.
  • the rotor of the motor (drive assembly) is fixed to the shaft so that the rotor can rotate with the shaft of the motor.
  • an upper counterweight assembly is mounted to the shaft with an interference fit to balance the vibration of the scroll compressor.
  • the rotor of the drive assembly is made of superimposed steel sheets and assembled with fastener features. If the upper balance assembly is installed with an interference fit, it abuts against the rotor during the installation process, which may cause the upper balance assembly to come into hard contact with the rotor. During the installation process, a lot of pressure is often applied to the upper balance component, which will cause a large amount of deformation of the steel sheet of the rotor, and even collapse the rotor, affecting the positioning of the rotor and the shaft, resulting in misalignment.
  • the material of the upper weight assembly is usually iron-based to achieve optimal cost, but there may be a problem of magnetic flux leakage when the upper weight assembly is in contact with the rotor.
  • the upper counterweight assembly is allowed to be close to the rotor to effectively utilize the limited installation space (especially the axial space) in the scroll compressor and allow the upper counterweight assembly to be close to the rotor.
  • the weight assembly is fixed to the rotor to improve the stable positioning of the upper weight assembly and the balancing effect of the upper weight assembly. Therefore, the upper balance assembly is usually an interference fit on the shaft at a predetermined distance from the rotor.
  • the motor When the motor is energized, under the action of the magnetic field, the rotor drives the shaft to rotate together. In this way, the upper balance assembly becomes loose due to the action of the magnetic force of the motor and the rotational torque generated by the rotation of the rotor.
  • the shaft and the upper balance assembly are of different materials and therefore have different coefficients of thermal expansion, the upper balance assembly may also become loose due to the operating temperature inside the compressor and the high temperature of the external environment. When there is a large displacement due to loosening, it will have a great impact on the entire dynamic balance system of the compressor, and even lead to the performance of the compressor being degraded or invalid.
  • the holding force of the interference fit between the upper balance assembly and the shaft can be improved.
  • the holding force cannot be increased indefinitely due to the limitation of the processing technology of the balance weight or the tensile strength of the material. Therefore, the predetermined distance between the upper weight assembly and the rotor needs to be controlled.
  • the purpose of the present disclosure is to provide a compressor that overcomes the above-mentioned defects in the prior art.
  • the present disclosure relates to a compressor comprising: a compression mechanism configured to compress a working fluid; a drive assembly including a stator, a rotor, and a shaft, the shaft being rotatable relative to the stator with the rotor , thereby driving the compression mechanism; and an upper counterweight assembly, the upper counterweight assembly is mounted on the shaft with an interference fit and is located above the rotor, wherein the lower surface of the upper counterweight assembly is at a predetermined distance from the top surface of the rotor, predetermined distance The distance is greater than 0 and less than or equal to 5mm.
  • the upper counterweight assembly includes a boss protruding toward the top surface of the rotor, the lower end face of the boss forming the lower surface of the upper counterweight assembly.
  • the boss is a ring.
  • the top surface of the rotor includes a magnetic region provided with magnets and a non-magnetic region provided with no magnets, and the projection of the boss on the top surface of the rotor is within the non-magnetic region.
  • a stop is provided between the upper weight assembly and the rotor, the stop being configured to further limit the maximum displacement of the upper weight assembly.
  • the top surface of the rotor includes a magnetic region provided with magnets and a non-magnetic region provided with no magnets, and the projection of the stopper on the top surface of the rotor is within the non-magnetic region.
  • the stop is integrally provided with a collar on the shaft.
  • the outer peripheral surface of the shaft is provided with a first mounting plane
  • the upper counterweight assembly is provided with a second mounting plane
  • the first mounting plane cooperates with the second mounting plane to prevent rotation of the upper counterweight assembly relative to the shaft
  • the limiting member is a step portion extending from the first installation plane.
  • the stop is a collar mounted to the shaft with an interference fit.
  • the material of the collar is a ferrous matrix material or a cemented carbide material.
  • the cross-section of the collar is rectangular or "L" shaped.
  • the compressor is an inverter scroll compressor.
  • the upper counterweight assembly is provided with a boss, and the distance between the boss and the top surface of the rotor is less than or equal to the maximum allowable displacement, and the impact on the vibration of the scroll compressor is within an acceptable range, Minimal impact on scroll compressor operation.
  • the boss and/or the limiting member can prevent magnetic flux leakage, so that the performance of the scroll compressor is limited.
  • FIG. 1 is a cross-sectional view of a scroll compressor according to the present disclosure
  • FIG. 2A shows a cross-sectional view of a rotor, a shaft, and an upper counterweight assembly cooperating with the scroll compressor according to the first embodiment of the present disclosure
  • FIG. 2B shows a cross-sectional view of a rotor, a shaft, and an upper counterweight assembly cooperating therewith of a scroll compressor according to a second embodiment of the present disclosure
  • FIG. 3 is a top perspective view of the upper counterweight assembly shown in FIG. 2B;
  • Fig. 4 is the bottom perspective view of the upper counterweight assembly shown in Fig. 2B;
  • Figure 5 is a perspective view of the shaft shown in Figure 2B;
  • Figure 6 is a schematic top cross-sectional view of the magnetic region of the rotor shown in Figure 2B;
  • FIG. 7 shows a cross-sectional view of a rotor, a shaft, and an upper counterweight assembly cooperating therewith of a scroll compressor according to a second embodiment of the present disclosure
  • Figure 8 is a perspective view of the shaft shown in Figure 7;
  • FIG. 9 is a cross-sectional view of the rotor, shaft and upper counterweight assembly shown in FIG. 7 after being assembled with other components;
  • Figure 10 is a partial perspective view of an alternative embodiment of the shaft shown in Figure 7;
  • FIG. 11 shows a cross-sectional view of a rotor, a shaft, and an upper counterweight assembly cooperating therewith of a scroll compressor according to a third embodiment of the present disclosure
  • Figure 12 is a perspective view of the collar shown in Figure 11;
  • Figure 13 is a cross-sectional view of the collar shown in Figure 11;
  • Figure 14 is a perspective view of an alternative embodiment of the collar shown in Figure 11;
  • Figure 15 is a cross-sectional view of the collar shown in Figure 14;
  • FIG. 16 is a cross-sectional view of one manner in which the collar shown in FIG. 14 is mounted to the rotor, shaft of the scroll compressor;
  • FIG. 17 is a cross-sectional view of another manner in which the collar shown in FIG. 14 is mounted on the rotor and shaft of the scroll compressor.
  • Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods in order to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and should not be construed to limit the scope of the disclosure. In some example embodiments, well-known methods, well-known device structures, and well-known technologies are not described in detail.
  • first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by These terms are restricted. These terms may only be used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as “first,” “second,” and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.
  • compressor 10 in particular an inverter scroll compressor
  • compressor 10 is shown as a low-pressure side-type hermetic scroll refrigeration compressor (ie, a compressor in which the motor is positioned in the suction pressure region of the compressor) , as shown in Figure 1.
  • high side compressors ie, compressors in which the motor is positioned in the discharge pressure region of the compressor.
  • FIG. 1 shows a compressor 10 .
  • the compressor 10 may include a sealed housing assembly 12 , a bearing block assembly 14 , a drive assembly 16 , a compression mechanism 18 , a seal assembly 20 , a lower counterweight assembly 22 and an upper counterweight assembly 24 .
  • Bearing block assembly 14 , drive assembly 16 , compression mechanism 18 , seal assembly 20 , and lower and upper weight assemblies 22 , 24 may be housed within housing assembly 12 .
  • the casing assembly 12 may generally form a compressor housing and may include a cylindrical casing 26 , an end cap 28 at an upper end of the casing assembly 12 , a laterally extending divider 30 , and a base at a lower end of the casing assembly 12 32. End cap 28 and divider 30 may generally define discharge chamber 34 . Housing 26 , divider 30 and base 32 may generally define suction chamber 40 . Suction inlet fitting 38 may be attached to housing assembly 12 and may communicate with suction chamber 40 . Divider 30 may include a discharge passage 42 via which compression mechanism 18 communicates with discharge chamber 34 .
  • the bearing adapter assembly 14 may be attached to the housing assembly 12 (specifically the housing 26 in the figures) and may include a main bearing adapter 44 and a bearing 46 housed in the main bearing adapter 44 .
  • the drive assembly 16 may include a stator 50 , a rotor 52 and a shaft 54 .
  • the stator 50 may be press fit into the housing assembly 12 (specifically housing 26 in the figures).
  • the rotor 52 may be attached to the shaft 54 and may rotatably drive the shaft 54 .
  • the shaft 54 may be rotatably supported by the main bearing block 44 via the bearing 46 near the upper end.
  • a bottom bearing assembly 48 is provided in the base 32 .
  • the shaft 54 may be rotatably supported near the lower end via the bottom bearing assembly 48 .
  • the compression mechanism 18 may generally include an orbiting scroll 58 and a fixed scroll 60 .
  • the orbiting scroll 58 may include an end plate 62 having an orbiting spiral wrap 64 on an upper surface of the end plate 62 .
  • the fixed scroll 60 may include an end plate 74 and a fixed spiral wrap 76 projecting downwardly from the end plate 74 .
  • the orbiting wrap 76 of the fixed scroll 60 may meshingly engage the orbiting wrap 64 of the orbiting scroll 58 to create a series of moving fluid chambers.
  • the fluid cavity defined by the orbiting wrap 64, the fixed wrap 76 may follow from the radially outer position (suction pressure) through the radially intermediate position (intermediate pressure) Moving to the radially inward position (at the discharge pressure) reduces the volume thereby compressing the working fluid.
  • the end plate 62 of the driven scroll 58 may project downwardly with a cylindrical hub 68 .
  • the cylindrical hub 68 may have a drive bushing 70 rotatably disposed therein.
  • the shaft 54 may include an eccentric crank pin 56 (also referred to as an eccentric).
  • the eccentric crank pin 56 is drivingly engaged in the transmission bushing 70 to provide radially flexible transmission.
  • the driving force generated by the drive assembly 16 is transmitted to the transmission bushing 70 via the crank pin 56 of the shaft 54, and then transmitted to the cylindrical hub 68 of the orbiting scroll 58 by the transmission bushing 70, thereby driving the orbiting scroll 58 spins.
  • the compressor 10 is energized, thereby causing the stator 50 to generate a rotating magnetic field and interacting with the magnetic field of the rotor 52 to generate a rotational torque on the rotor 52 .
  • the material of the lower counterweight assembly 22 is non-magnetic leakage material such as copper, high manganese steel, etc., and is assembled to the rotor 52 by means of bolts 53 , as shown in FIG. 1 .
  • the material of the upper counterweight assembly 24 is usually iron-based material (lower cost), which is assembled on the shaft 54 by means of interference fit (more reliable than screws, snap rings, etc.) and rotates with the shaft 54, and the upper counterweight assembly 24 is assembled with The heavy assembly 24 is located above the rotor 52 .
  • the holding force generated by the interference fit between the upper counterweight assembly 24 and the shaft 54 is used to overcome: the gravity of the upper counterweight assembly 24 itself, the downward magnetic force generated by the upper counterweight assembly 24 by the magnetic field of the rotor 52, and the upper counterweight The torque produced by the member 24 in the rotational direction as the rotor 52 rotates.
  • the upper weight assembly 24 generally includes a weight portion 25 and a mounting portion 27 .
  • Mounting portion 27 is configured to interference fit upper weight assembly 24 on shaft 54 .
  • the counterweight portion 25 extends radially outward and axially upward from the mounting portion 27 to achieve dynamic balance of the drive assembly and the compressor.
  • the mounting portion 27 has the lower end surface 33 facing the top surface 55 of the rotor 52 .
  • the lower end surface 33 of the mounting portion 27 constitutes the lower surface of the upper weight assembly 24 .
  • the inventor found that when the distance between the upper counterweight assembly 24 and the rotor 52 is not greater than 5 mm, the dynamic balance can be effectively ensured, and the vibration caused by the damage of the dynamic balance can be reduced or avoided.
  • the distance between the lower surface of the upper weight assembly 24 and the top surface 55 of the rotor 52 is greater than zero, that is, the upper weight assembly 24 is not in contact with the top surface 55 . Therefore, the upper weight assembly 24 is carried by the shaft (rather than the rotor), which prevents damage to the rotor 52 from being stressed by the rotor 52 . Moreover, possible magnetic flux leakage caused by the upper weight assembly 24 is avoided or reduced.
  • the upper counterweight assembly 24 is provided with a boss 35 on a side close to the rotor 52 .
  • the bosses 35 may be integrally formed with the upper weight assembly 24 .
  • the boss 35 is generally annular and extends axially downward from the lower end face 33 of the mounting portion 27 .
  • the boss 35 may have a non-circular shape, such as a square, a polygon, or the like.
  • the boss 35 is a single annular piece, or that the boss 35 includes a plurality of members arranged in a circumferential direction (eg, evenly distributed).
  • the boss 35 has a boss lower end surface 37 on the side close to the rotor 52 .
  • the lower end surface 37 of the boss constitutes the lower surface of the upper counterweight assembly 24 .
  • the lower end surface 37 of the boss is separated from the top surface 55 of the rotor 52 by a predetermined axial distance H, and the predetermined axial distance H is greater than 0 and less than or equal to 5 mm.
  • the top surface 55 of the rotor 52 includes a magnetic area with magnets 59 and a non-magnetic area without magnets 59 .
  • the outer diameter D of the boss 35 of the upper counterweight assembly 24 is within the non-magnetic region of the rotor 52 outside its rotor magnets 59 .
  • the upper counterweight assembly 24 can effectively ensure the dynamic balance, and reduce or avoid the vibration caused by the damage of the dynamic balance.
  • the upper counterweight assembly 24 is not in contact with the top surface 55 , thus preventing the rotor 52 from being damaged by applying pressure to the rotor 52 .
  • the boss 35 of the upper counterweight assembly 24 since the outer diameter D of the boss 35 of the upper counterweight assembly 24 is within the non-magnetic region of the rotor 52, the boss 35 can prevent magnetic flux leakage.
  • a limiter is provided between the boss 35 and the rotor 52 , and the limiter is configured to further limit the maximum displacement of the upper counterweight assembly 24 .
  • a collar 51 is integrally provided on the shaft 54 (limiting pieces).
  • the upper counterweight assembly 24 may or may not be provided with a boss 35 .
  • the axial distance between the lowermost end surface of the upper counterweight assembly 24 and the top surface 55 of the rotor 52 is still H, And 0mm ⁇ H ⁇ 5mm. Meanwhile, the axial distance between the lowermost end surface and the collar top surface 61 of the collar 51 is H1.
  • the lowermost end face of the upper counterweight assembly 24 is the boss lower end face 37 of the boss 35; in the case where the upper counterweight assembly 24 is not provided with the boss 35 Below, the lowermost end face of the upper counterweight assembly 24 is the lower end face 33 of the mounting portion 27 of the upper counterweight assembly 24 .
  • the projection of the stopper on the top surface 55 of the rotor 52 is in the non-magnetic region.
  • the outer diameter D1 of the collar 51 needs to be within the non-magnetic region of the rotor 52 .
  • the axial distance H is controlled as: 0mm ⁇ H ⁇ 5mm.
  • the maximum axial displacement of the upper counterweight assembly 24 is less than 5 mm, the impact on the vibration of the compressor 10 is within an acceptable range, and the impact on the operation of the compressor 10 is minimal.
  • the collar 51 since the outer diameter D1 of the collar 51 (and the outer diameter D if the upper weight assembly 24 is provided with the boss 35 ) is within the non-magnetic region of the rotor 52 , the collar 51 (the boss 35 ) has a limited impact on the performance of the compressor 10 .
  • the collar 51 is not provided on the mounting section 55 of the shaft 54 , but a stepped portion 63 (stopper) is provided.
  • the mounting portion 27 has an annular shape and is provided with a mounting hole 29 .
  • the shaft 54 includes a mounting section 55 adjacent the eccentric crank pin 56 .
  • the mounting section 55 of the shaft 54 is received in the mounting hole 29 of the mounting portion 27 with an interference fit.
  • the inner peripheral surface of the mounting portion 27 is provided with a mounting plane 31 (second mounting plane).
  • a mounting plane 57 is provided on the mounting section 55 .
  • Mounting plane 31 of mounting portion 27 matches mounting plane 57 (first mounting plane) on mounting section 55 for circumferentially positioning upper weight assembly 24 and preventing rotation of upper weight assembly 24 relative to shaft 54 .
  • the stepped portion 63 is a portion protruding with respect to the mounting plane 57 .
  • the mounting plane 57 may be formed by processing a part of the mounting section 55 in the axial direction to remove material, while also forming the stepped portion 63 . It should be understood that the structure of the step portion 63 may not be limited to the specific example shown in the figure, as long as it can stop the upper counterweight assembly 24 from moving downward.
  • the lowermost end face of the upper counterweight assembly 24 (for example, in the case where the upper counterweight assembly 24 is provided with the boss 35 , the lowermost end face is The axial distance between the lower end surface 37) of the boss 35 and the top surface 55 of the rotor 52 is still H, and 0mm ⁇ H ⁇ 5mm. Meanwhile, the axial distance between the lowermost end surface and the stepped top surface 65 of the stepped portion 63 is H1.
  • the lowermost end surface of the upper counterweight assembly 24 may abut against the stepped top surface 65 of the stepped portion 63, thereby preventing the upper counterweight assembly 24 Shift further down.
  • the material of the collar 72 is an iron base material or a cemented carbide material.
  • the lowermost end face of the upper counterweight assembly 24 (for example, in the case where the upper counterweight assembly 24 is provided with the boss 35 , the lowermost end face is The axial distance between the lower end surface 37) of the boss 35 and the top surface 55 of the rotor 52 is still H, and 0mm ⁇ H ⁇ 5mm. Meanwhile, the axial distance between the lowermost end surface and the collar top surface 73 of the collar 72 is H1.
  • the lowermost end surface of the upper counterweight assembly 24 may abut against the collar top surface 73 of the collar 72, thereby preventing the upper counterweight assembly 24 is shifted further down.
  • the outer diameter D1 of the collar 72 needs to be within the non-magnetic region of the rotor 52 .
  • the maximum axial displacement of the upper counterweight assembly 24 is less than 5 mm, the impact on the vibration of the compressor 10 is within an acceptable range, and the impact on the operation of the compressor 10 is minimal.
  • the outer diameter D1 of the collar 51 (and its outer diameter D if the upper weight assembly 24 is provided with the boss 35 ) is within the non-magnetic region of the rotor 52 , the collar 72 (the boss 35 ) has a limited impact on the performance of the compressor 10 .
  • the cross-section of the collar 72 is generally rectangular.
  • the cross-section of the collar 72' may be generally "L" shaped.
  • the collar 72&apos has a smaller area collar top surface 75 and a larger area collar bottom surface 77 opposite the collar top surface 75.
  • the collar top surface 75 can be in contact with the top surface 55 of the rotor 52, and the collar bottom surface 77 can also be in contact with the top surface 55 of the rotor 52, as shown in FIGS. 16 and 17 . shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Abstract

一种压缩机（10），包括：压缩机构（18），压缩机构（18）构造成对工作流体进行压缩；驱动组件（16），驱动组件（16）包括定子（50）、转子（52）和轴（54），轴（54）能够随转子（52）一起相对于定子（50）旋转，由此驱动压缩机构（18）；以及上配重组件（24），上配重组件（24）以过盈配合的方式安装于轴（54）并且位于转子（52）上方，其中，上配重组件（24）的下表面与转子（52）的顶面（55）相距预定距离，预定距离大于0并且小于等于5mm。

Description

压缩机
本申请要求以下中国专利申请的优先权：于2020年07月30日提交国家知识产权局的申请号为202010751034.X、发明创造名称为“压缩机”的中国专利申请；于2020年07月30日提交国家知识产权局的申请号为202021551090.0、发明创造名称为“压缩机”的中国专利申请。这些专利申请的全部内容通过引用结合在本申请中。
技术领域
本公开涉及一种压缩机。特别地，本公开涉及变频涡旋压缩机。
背景技术
本部分提供与本公开相关的背景信息，而本部分不一定是现有技术。
在变频式涡旋压缩机中，马达(驱动组件)的转子固定至轴，使得转子能够带动马达的轴一起旋转。在马达的转子的上方，上配重组件以过盈配合的方式安装至轴，用以平衡涡旋压缩机的振动。
在变频式涡旋压缩机中，通常驱动组件的转子由钢片叠加并以扣件特征组装而成。如果将上平衡组件在以过盈配合的方式安装，在安装过程中与转子抵接，可能会造成上平衡组件与转子硬接触。在安装过程中，往往对上平衡组件施加很大压力，这会导致转子的钢片产生较大变形量，乃至将转子压塌，影响转子与轴的定位而导致错位。
另外，上配重组件的材料通常为铁基材料以实现最优的成本，但有在上配重组件与转子接触时可能存在漏磁问题。在避免形成漏磁通道(或者减弱漏磁通道的形成)的情况下，允许上配重组件接近转子而有效地利用涡旋压缩机内的有限安装空间(特别是轴向空间)并且允许上配重组件固定至转子而提高上配重组件的稳定定位和上配重组件的平衡效果。因此，上平衡组件通常以与转子相距预定距离的方式过盈配合在轴上。
在马达通电时，在磁场作用下，转子带动轴一起旋转。这样，上平衡组件由于受到马达的磁力作用和转子旋转所产生的旋转力矩的作用而变得松动。此外，在轴与上平衡组件的材料不同并因此具有不同的热膨胀系数时，受到压缩 机内部运行温度和外部环境高温影响，上平衡组件也可能会松动。当因为松动而产生很大位移时，对压缩机的整个动平衡系统产生很大影响，甚至导致压缩机的性能下降或失效。
为了防止松动，可以提高上平衡组件与轴的过盈配合的保持力。然而，由于平衡块的加工工艺或材料抗拉强度的限制，该保持力不能无限增加。因而，需要对上配重组件与转子之间的预定距离进行控制。
因此，本领域期望提供一种能够合适地设置上配重组件与转子之间的轴向间隙的动平衡系统。
发明内容
本部分提供本公开的总体概述，而不是本公开的全部范围或其所有特征的全面公开。
本公开的目的在于提供一种压缩机，克服了现有技术中的上述缺陷。
在一种形式中，本公开涉及一种压缩机，包括：压缩机构，压缩机构构造成对工作流体进行压缩；驱动组件，驱动组件包括定子、转子和轴，轴能够随转子一起相对于定子旋转，由此驱动压缩机构；以及上配重组件，上配重组件以过盈配合的方式安装于轴并且位于转子上方，其中，上配重组件的下表面与转子的顶面相距预定距离，预定距离大于0并且小于等于5mm。
在一些形式中，上配重组件包括朝向转子的顶面突出的凸台，凸台的下端面构成了上配重组件的下表面。
在一些形式中，凸台为环形件。
在一些形式中，转子的顶面包括设置有磁体的磁性区域和没有设置磁体的非磁性区域，以及凸台在转子的顶面上的投影处于非磁性区域内。
在一些形式中，在上配重组件与转子之间设置有限位件，限位件构造成进一步限制上配重组件的最大位移。
在一些形式中，转子的顶面包括设置有磁体的磁性区域和没有设置磁体的非磁性区域，以及限位件在转子的顶面上的投影处于非磁性区域内。
在一些形式中，限位件为一体地设置在轴上的轴环。
在一些形式中，轴的外周面上设置有第一安装平面，上配重组件设置有第二安装平面，第一安装平面与第二安装平面配合以防止上配重组件相对于轴旋 转；以及限位件为从第一安装平面延伸的台阶部。
在一些形式中，限位件为以过盈配合的方式安装于轴的套环。
在一些形式中，套环的材料为铁基体材料或者硬质合金材料。
在一些形式中，套环的横截面呈矩形或者呈“L”形。
在一些形式中，压缩机为变频涡旋压缩机。
根据本公开的压缩机中，上配重组件上设置有凸台并且凸台与转子顶面的距离小于等于最大允许位移量，这对涡旋压缩机的振动造成的影响在可接受范围内，对涡旋压缩机运行的影响极小。另一方面，由于凸台和/或限位件的外径在转子的非磁性区域内，故而该凸台和/或限位件能够防止漏磁，从而对涡旋压缩机的性能影响有限。
根据本文提供的描述，其他应用领域将变得明显。本概述中的描述和具体示例仅用于说明的目的，而不意在限制本公开的范围。
附图说明
本文中描述的附图仅出于说明选定实施方式而非所有可能的实施方案的目的，而不意在限制本公开的范围。
图1是根据本公开的涡旋压缩机的横截面图；
图2A示出了根据本公开第一实施方式的涡旋压缩机的转子、轴及与其配合的上配重组件的横截面图；
图2B示出了根据本公开第二实施方式的涡旋压缩机的转子、轴及与其配合的上配重组件的横截面图；
图3是图2B所示上配重组件的俯视立体图；
图4是图2B所示上配重组件的仰视立体图；
图5是图2B所示的轴的立体图；
图6是图2B所示的转子的磁性区域的示意性俯视截面图；
图7示出了根据本公开第二实施方式的涡旋压缩机的转子、轴及与其配合的上配重组件的横截面图；
图8是图7所示的轴的立体图；
图9是图7所示的转子、轴及上配重组件与其他部件组装后的截面图；
图10是图7所示的轴的替代性实施方式的局部立体图；
图11示出了根据本公开第三实施方式的涡旋压缩机的转子、轴及与其配合的上配重组件的横截面图；
图12是图11所示套环的立体图；
图13是图11所示套环的横截面图；
图14是图11所示套环的替代性实施方式的立体图；
图15是图14所示套环的横截面图；
图16是图14所示套环安装于涡旋压缩机的转子、轴的一种方式的横截面图；以及
图17是图14所示套环安装于涡旋压缩机的转子、轴的另一种方式的横截面图。
贯穿附图中的若干视图，对应的附图标记指示对应的部件。
具体实施方式
现在将参照附图更充分地描述示例性实施方式。
提供了示例性实施方式以使得本公开将是透彻的并且将向本领域技术人员充分地传达范围。阐述了许多具体细节例如特定部件、装置和方法的示例，以提供对本公开的实施方式的透彻理解。对于本领域技术人员而言将明显的是，不需要采用具体细节，示例性实施方式可以以许多不同的形式来实施并且不应被解释为限制本公开的范围。在一些示例性实施方式中，对公知的方法、公知的装置结构和公知的技术不再进行详细描述。
当元件或层被提及为“位于另一元件或层上”、“接合至”、“连接至”或“联接至”另一元件或层时，元件或层可以直接位于其他元件或层上、接合至、连接至或联接至其他元件或层，或者可以存在中间元件或层。相反，当元件被提及为“直接位于另一元件或层上”、“直接接合至”、“直接连接至”或“直接联接至”另一元件或层时，不会存在中间元件或层。用以描述元件之间的关系的其他用语(例如“位于……之间”与“直接位于……之间”、“相邻”与“直接相邻”等)应当以相似的方式来解释。如本文中使用的，术语“和/或”包括相关列举项目中的一个或更多个项目的任何组合和全部组合。
尽管在本文中可以使用术语第一、第二、第三等来描述各种元件、部件、区域、层和/或部段，但是这些元件、部件、区域、层和/或部段不应当受这些 术语限制。这些术语可以仅用于区分一个元件、部件、区域、层或部段与另一区域、层或部段。除非上下文明确表明，否则诸如“第一”、“第二”和其他数字术语之类的术语在本文中使用时并不意味着顺序或次序。因此，下面论述的第一元件、部件、区域、层或部段在不脱离示例性实施方式的教示的情况下可以被称为第二元件、部件、区域、层或部段。
本公开的原理适于结合在许多不同类型的设备、例如涡旋压缩机和旋转压缩机中，包括密封式机器、开放式驱动机器和非密封式机器。出于例示的目的，压缩机10(特别是变频涡旋压缩机)被示出为低压侧型密封式涡旋制冷压缩机(即，马达设置在压缩机的抽吸压力区域中的压缩机)，如图1中所示。将理解的是，本公开的原理还适用于高压侧压缩机(即，马达设置在压缩机的排放压力区域中的压缩机)。
图1示出了压缩机10。压缩机10可以包括密封的外壳组件12、轴承座组件14、驱动组件16、压缩机构18、密封组件20、下配重组件22和上配重组件24。轴承座组件14、驱动组件16、压缩机构18、密封组件20以及下配重组件22和上配重组件24可以容置在外壳组件12中。
外壳组件12可以大体上形成压缩机壳体，并且可以包括筒形外壳26、位于外壳组件12的上端部处的端盖28、横向延伸的分隔部30以及位于外壳组件12的下端部处的基部32。端盖28和分隔部30可以大体上限定排放室34。外壳26、分隔部30和基部32可以大体上限定抽吸室40。吸气入口配件38可以附接至外壳组件12并且可以与抽吸室40连通。分隔部30可以包括排放通道42，压缩机构18经由排放通道42与排放室34连通。
轴承座组件14可以附接至外壳组件12(图中具体为外壳26)并且可以包括主轴承座44和容置在主轴承座44中的轴承46。
驱动组件16可以包括定子50、转子52和轴54。定子50可以压配合到外壳组件12(图中具体为外壳26)中。转子52可以附接在轴54上并且可以以可旋转的方式驱动轴54。轴54在靠近上端处可以经由轴承46由主轴承座44以可旋转的方式支承。在基部32中设置有底轴承组件48。轴54在靠近下端处可以经由底轴承组件48以可旋转的方式支承。
压缩机构18可以大体上包括动涡旋件58和定涡旋件60。动涡旋件58可以包括端板62，端板62具有位于端板62的上表面上的动螺旋涡卷64。定涡 旋件60可以包括端板74和从端板74向下突出的定螺旋涡卷76。定涡旋件60的定螺旋涡卷76可以以啮合的方式接合动涡旋件58的动螺旋涡卷64，从而产生一系列移动的流体腔。在压缩机构18的整个压缩周期中，由动螺旋涡卷64、定螺旋涡卷76限定的流体腔可以随着从径向外侧位置(抽吸压力处)经过径向中间位置(中间压力处)向径向内侧位置(排放压力处)移动而减小体积由此压缩工作流体。
从动涡旋件58的端板62可以向下突出有筒形毂68。筒形毂68可以具有以可旋转的方式设置在该筒形毂68中的传动衬套70。轴54可以包括偏心曲柄销56(也称为偏心部)。偏心曲柄销56以传动的方式配合在传动衬套70中以提供径向柔性传动。由此，将驱动组件16产生的驱动力经由轴54的曲柄销56传递至传动衬套70，再由传动衬套70传递至动涡旋件58的筒形毂68，从而带动动涡旋件58旋转。
如上所述，为了使驱动组件16产生驱动力，为压缩机10通电，由此使定子50产生旋转磁场与转子52的磁场相互作用，使转子52产生旋转力矩。下配重组件22的材料为非漏磁材料例如铜、高锰钢等，利用螺栓53组装于转子52，如图1所示。上配重组件24的材料通常为铁基材料(成本更低)，利用过盈配合(相较于螺钉、卡环等方式可靠性更佳)组装于轴54而随轴54旋转，并且上配重组件24位于转子52上方。上配重组件24与轴54过盈配合所产生的保持力用以克服：上配重组件24自身的重力、上配重组件24受到转子52的磁场产生的向下的磁力、以及上配重组件24随转子52旋转而在旋转方向上产生的转矩。
第一实施方式
如图2A所示，上配重组件24大体包括配重部25和安装部27。安装部27构造成将上配重组件24过盈配合在轴54上。配重部25从安装部27沿径向向外且沿轴向向上延伸，以实现驱动组件以及压缩机的动平衡。
在图2A的示例中，安装部27具有面向转子52的顶面55的下端面33。安装部27的下端面33构成上配重组件24的下表面。安装部27的下端面33与转子52的顶面55之间相距预定的轴向距离H，该预定的轴向距离H大于0并且小于等于5mm。
技术效果
发明人经过实验验证发现，上配重组件24与转子52之间的距离不大于5mm时能够有效保证动平衡，而减小或避免因动平衡破坏引起的振动。
另一方面，上配重组件24的下表面与转子52的顶面55的距离大于零，即，上配重组件24与顶面55不接触。因此，由轴(而不是转子)对上配重组件24承载，这可以防止对转子52施加压力而对转子52造成损坏。而且，避免或减小了上配重组件24造成可能的漏磁。
第二实施方式
替代性地，在本公开的第二实施方式中，如图4所示，上配重组件24在靠近转子52的一侧设置有凸台35。凸台35可以与上配重组件24一体地形成。例如，如图所示，凸台35大体呈圆环状并且从安装部27的下端面33沿轴向向下延伸。替代性地，本领域技术人员可以设想，凸台35可以具有非圆环形状，例如方形、多边形等。替代性地，本领域技术人员可以设想，凸台35为单独地环形件，或者凸台35包括沿圆周方向布置(例如，均布)的多个构件。
凸台35在靠近转子52的一侧具有凸台下端面37。凸台下端面37构成上配重组件24的下表面。凸台下端面37与转子52的顶面55相距预定的轴向距离H，该预定的轴向距离H大于0并且小于等于5mm。
转子52的顶面55包括设置有磁体59的磁性区域和没有设置磁体59的非磁性区域，上配重组件24的凸台35在转子52的顶面55上的投影处于非磁性区域内。特别地，上配重组件24的凸台35的外径D在转子52的位于其转子磁体59以外的非磁性区域内。
技术效果
上配重组件24能够有效保证动平衡，而减小或避免因动平衡破坏引起的振动。上配重组件24与顶面55不接触，因此可以防止对转子52施加压力而对转子52造成损坏。此外，由于上配重组件24的凸台35的外径D在转子52的非磁性区域内，故而凸台35可以防止漏磁。
第三实施方式
在凸台35与转子52之间设置有限位件，限位件构造成进一步限制上配重组件24的最大位移。
例如，替代性地或者附加地，如图7至图9所示，在与轴54的安装部段55的安装平面57相邻的下方，在轴54上一体地设置有轴环51(限位件)。在 本实施方式中，上配重组件24可以设置凸台35，也可以不设置凸台35。
如图7所示，当上配重组件24以过盈配合的方式安装于轴54时，上配重组件24的最下端面与转子52的顶面55之间的轴向距离仍为H，并且0mm<H<5mm。同时，该最下端面与轴环51的轴环顶面61的轴向距离为H1。其中，在上配重组件24设置有凸台35的情况下，上配重组件24的最下端面为凸台35的凸台下端面37；在上配重组件24未设置凸台35的情况下，上配重组件24的最下端面为上配重组件24的安装部27的下端面33。
限位件在转子52的顶面55上的投影处于非磁性区域内。特别地，轴环51的外径D1需要在转子52的非磁性区域内。
技术效果
当上配重组件24在重力以及磁性力的作用下向下移位时，上配重组件间24的最下端面可能抵靠于轴环51的轴环顶面61，从而防止上配重组件24进一步向下移位。由此，确保轴向距离H控制为：0mm<H<5mm。如上所述，上配重组件24的最大轴向位移量小于5mm对压缩机10的振动造成的影响在可接受范围内，对压缩机10运行的影响极小。另一方面，由于轴环51的外径D1(以及在上配重组件24设置有凸台35的情况下其外径D)在转子52的非磁性区域内，故而轴环51(凸台35)对压缩机10的性能影响有限。
替代性地，如图10所示，在轴54的安装部段55上未设置轴环51，而是设置有台阶部63(限位件)。
参见图3和图10，安装部27呈环形并且设有安装孔29。轴54包括靠近偏心曲柄销56的安装部段55。轴54的安装部段55以过盈配合的方式接收在安装部27的安装孔29中。安装部27的内周面设置有安装平面31(第二安装平面)。在安装部段55上设置有安装平面57。安装部27的安装平面31与安装部段55上的安装平面57(第一安装平面)相匹配，用以使上配重组件24在周向上定位并且防止上配重组件24相对于轴54旋转。台阶部63为相对于安装平面57突出的部分。例如，可以通过对安装部段55的轴向方向上的一部分进行去除材料的加工而形成安装平面57，同时也形成了台阶部63。应理解的是，台阶部63的结构可以不限于图示的具体示例，只要其能够止挡上配重组件24向下移动即可。
当上配重组件24以过盈配合的方式安装于轴54时，上配重组件24的最 下端面(例如，在上配重组件24设置有凸台35的情况下，该最下端面为凸台35的凸台下端面37)与转子52的顶面55之间的轴向距离仍为H，并且0mm<H<5mm。同时，该最下端面与台阶部63的台阶顶面65的轴向距离为H1。当上配重组件24在重力以及磁性力的作用下向下移位时，上配重组件间24的最下端面可能抵靠于台阶部63的台阶顶面65，从而防止上配重组件24进一步向下移位。
第四实施方式
替代与轴54一体形成的轴环51或者台阶部63，如图11所示，可以设置与转子52的顶面55抵接的大体呈圆环状的套环72(套环)，套环72与轴54过盈配合。套环72的材料为铁基体材料或者硬质合金材料。当上配重组件24以过盈配合的方式安装于轴54时，上配重组件24的最下端面(例如，在上配重组件24设置有凸台35的情况下，该最下端面为凸台35的凸台下端面37)与转子52的顶面55之间的轴向距离仍为H，并且0mm<H<5mm。同时，该最下端面与套环72的套环顶面73的轴向距离为H1。当上配重组件24在重力以及磁性力的作用下向下移位时，上配重组件间24的最下端面可能抵靠于套环72的套环顶面73，从而防止上配重组件24进一步向下移位。
优选地，在套环72由铁基材料制成的情况下，套环72的外径D1需要在转子52的非磁性区域内。
技术效果
如上所述，上配重组件24的最大轴向位移量小于5mm对压缩机10的振动造成的影响在可接受范围内，对压缩机10运行的影响极小。另一方面，由于轴环51的外径D1(以及在上配重组件24设置有凸台35的情况下其外径D)在转子52的非磁性区域内，故而套环72(凸台35)对压缩机10的性能影响有限。
如图12和图13所示，套环72的横截面大体呈矩形。替代性地，如图14和图15所示，套环72’的横截面可以大体呈“L”形。套环72’具有面积较小的套环顶面75以及与套环顶面75相反的面积较大的套环底面77。在套环72安装于轴54时，可以使套环顶面75抵接于转子52的顶面55，也可以使套环底面77抵接于转子52的顶面55，如图16和图17所示。
已出于说明和描述的目的提供了实施方式的前述描述。这些描述并不意在 穷举或限制本公开。特定实施方式的各个元件或特征通常并不局限于该特定实施方式，而是在适用的情况下，即使没有具体地示出或描述，也是能够互换的并且能够在选定实施方式中使用。特定实施方式的各个元件或特征还可以以许多方式进行改变。这样的改变不应当被认为是与本公开相背离，并且所有这样的改型均意在被包括于本公开的范围内。

Claims (12)

  1. 一种压缩机，包括：
    压缩机构，所述压缩机构构造成对工作流体进行压缩；
    驱动组件，所述驱动组件包括定子、转子和轴，所述轴能够随所述转子一起相对于所述定子旋转，由此驱动所述压缩机构；以及
    上配重组件，所述上配重组件以过盈配合的方式安装于所述轴并且位于所述转子上方，
    其中，所述上配重组件的下表面与所述转子的顶面相距预定距离，所述预定距离大于0并且小于等于5mm。
  2. 根据权利要求1所述的压缩机，其特征在于，所述上配重组件包括朝向所述转子的顶面突出的凸台，所述凸台的下端面构成了所述上配重组件的所述下表面。
  3. 根据权利要求2所述的压缩机，其特征在于，所述凸台为环形件。
  4. 根据权利要求2所述的压缩机，其特征在于，所述转子的顶面包括设置有磁体的磁性区域和没有设置磁体的非磁性区域，以及
    所述凸台在所述转子的顶面上的投影处于所述非磁性区域内。
  5. 根据权利要求1至4中的任一项所述的压缩机，其特征在于，在所述上配重组件与所述转子之间设置有限位件。
  6. 根据权利要求5所述的压缩机，其特征在于，所述转子的顶面包括设置有磁体的磁性区域和没有设置磁体的非磁性区域，以及
    所述限位件在所述转子的顶面上的投影处于所述非磁性区域内。
  7. 根据权利要求5所述的压缩机，其特征在于，所述限位件为一体地设置在所述轴上的轴环。
  8. 根据权利要求5所述的压缩机，其特征在于，所述轴的外周面上设置有第一安装平面，所述上配重组件设置有第二安装平面，所述第一安装平面与所述第二安装平面配合以防止上配重组件相对于所述轴旋转；以及
    所述限位件为从所述第一安装平面延伸的台阶部。
  9. 根据权利要求5所述的压缩机，其特征在于，所述限位件为以过盈配合的方式安装于所述轴的套环。
  10. 根据权利要求9所述的压缩机，其特征在于，所述套环的材料为铁基体材料或者硬质合金材料。
  11. 根据权利要求9所述的压缩机，其特征在于，所述套环的横截面呈矩形或者呈“L”形。
  12. 根据权利要求1至4中任一项所述的压缩机，其特征在于，所述压缩机为变频涡旋压缩机。
PCT/CN2020/127437 2020-07-30 2020-11-09 压缩机 WO2022021663A1 (zh)

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CN202010751034.XA CN114060276A (zh) 2020-07-30 2020-07-30 压缩机
CN202021551090.0U CN212717165U (zh) 2020-07-30 2020-07-30 压缩机
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101153593A (zh) * 2006-09-28 2008-04-02 日立空调·家用电器株式会社 流体压缩机
CN101749236A (zh) * 2008-12-15 2010-06-23 日立空调·家用电器株式会社 旋转型压缩机
CN103051087A (zh) * 2011-10-14 2013-04-17 三菱电机株式会社 旋转电机的转子
CN106089702A (zh) * 2015-04-27 2016-11-09 艾默生环境优化技术有限公司 具有配重组件的压缩机
CN107709783A (zh) * 2015-05-19 2018-02-16 日立江森自控空调有限公司 涡旋式压缩机

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Publication number Priority date Publication date Assignee Title
CN101153593A (zh) * 2006-09-28 2008-04-02 日立空调·家用电器株式会社 流体压缩机
CN101749236A (zh) * 2008-12-15 2010-06-23 日立空调·家用电器株式会社 旋转型压缩机
CN103051087A (zh) * 2011-10-14 2013-04-17 三菱电机株式会社 旋转电机的转子
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