WO2020083313A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

Info

Publication number
WO2020083313A1
WO2020083313A1 PCT/CN2019/112760 CN2019112760W WO2020083313A1 WO 2020083313 A1 WO2020083313 A1 WO 2020083313A1 CN 2019112760 W CN2019112760 W CN 2019112760W WO 2020083313 A1 WO2020083313 A1 WO 2020083313A1
Authority
WO
WIPO (PCT)
Prior art keywords
bush
scroll compressor
eccentric
scroll
counterweight
Prior art date
Application number
PCT/CN2019/112760
Other languages
French (fr)
Chinese (zh)
Inventor
纪高锋
沙海天
倪凌枫
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 CN201821719557.0U external-priority patent/CN208900360U/en
Priority claimed from CN201811238677.3A external-priority patent/CN111089055A/en
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 WO2020083313A1 publication Critical patent/WO2020083313A1/en

Links

Images

Classifications

    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00

Definitions

  • the present disclosure relates to a scroll compressor.
  • the contact force between the contact surfaces of the scroll blades will increase due to the increase in the centrifugal force of the movable scroll under especially high-speed operating conditions. Therefore, a counterweight needs to be provided to counteract the centrifugal force of part of the movable vortex.
  • the counterweight may be provided at an axial position consistent with the orbiting scroll hub (such as being connected to the bushing).
  • the counterweight may be provided at an axial position consistent with the orbiting scroll hub (such as being connected to the bushing).
  • the eccentric pin is often elongated and the axial dimension of the entire compressor is elongated.
  • a scroll compressor including: a movable scroll, the movable scroll including a handle; a drive shaft, the drive shaft including An eccentric recess; a bush, the handle is fitted in the eccentric recess via the bush so that the movable scroll is driven by the drive shaft, wherein the scroll compressor further includes a counterweight, the The counterweight is installed on the bush.
  • the bushing is capable of radial translation with respect to the drive shaft, a substantially flat drive surface is provided on the side surface of the eccentric recess, and the drive is provided on the outer surface of the bushing A substantially flat driven surface with a sliding fit on the surface.
  • the bushing is fixedly connected to the drive shaft.
  • a first positioning hole is provided on the outer surface of the bush, a second positioning hole corresponding to the first positioning hole is provided on the side surface of the eccentric recess, and a through hole is provided A transverse pin shaft of the first positioning hole and the second positioning hole; and / or a first positioning groove is provided on the outer surface of the bush, and a side surface of the eccentric recess is provided with A second positioning groove corresponding to the first positioning groove is provided with a vertical pin shaft accommodated in the first positioning groove and the second positioning groove.
  • the shape of the horizontal pin shaft is a cylinder, a rectangular parallelepiped or a truncated pyramid
  • the shape of the vertical pin shaft is a cylinder, a rectangular parallelepiped or a truncated pyramid.
  • the bushing is fixedly connected to the drive shaft by bolts.
  • the outer surface of the bushing is in interference, transition or clearance fit with the side surface of the eccentric recess.
  • a cylindrical drive bearing is provided between the bush and the handle, the inner cylindrical surface of the drive bearing is in interference fit with the outer surface of the handle, the outer cylinder of the drive bearing The surface is in clearance fit with the inner surface of the bush.
  • the counterweight includes a mounting portion and an eccentric weighting portion
  • the mounting portion has a complete or partial circular ring shape and is mounted to an end portion of the bush adjacent to the end plate of the movable scroll, so The eccentric weighting portion extends axially away from the end plate of the movable scroll from the mounting portion.
  • the counterweight includes a mounting portion and an eccentric weighting portion, the mounting portion is completely or partially circular, and the eccentric weighting portion extends axially, radially, or axially relative to the mounting portion It extends on the ground and radially to adjust the center of mass of the weight so that the centrifugal force of the weight is in the same plane as the driving force provided by the eccentric recess.
  • the counterweight includes a completely or partially circular mounting portion and an eccentric weighted portion extending from the mounting portion, the axial thickness of the mounting portion is set to be smaller than that of the eccentric weighted portion and the The thickness of the portion adjacent to the mounting portion.
  • the center of mass of the counterweight can be easily adjusted, so that the centrifugal force of the counterweight and the driving force of the drive shaft are on the same plane, reducing the bending moment of the bush, and at the same time reducing the wear on the drive bearing and improving the reliability of the compressor ; 2)
  • the height of the drive shaft can be shortened, and the height of the housing can be reduced, thereby reducing the cost of the compressor, and also the noise of the compressor; 3)
  • Figure 1 is a longitudinal sectional view of a scroll compressor
  • FIG. 2 is a schematic diagram of the centrifugal force of the movable scroll of the scroll compressor of FIG. 1, the driving force of the drive shaft, the contact force between the movable scroll and the fixed scroll, and the centrifugal force of the counterweight;
  • FIG. 3 shows a longitudinal sectional view of a scroll compressor according to an embodiment of the present disclosure
  • FIG. 4 shows an enlarged longitudinal cross-sectional view in which the handle of the movable scroll of the scroll compressor in FIG. 3 fits in the eccentric recess of the drive shaft, wherein the centrifugal force of the counterweight and the drive of the drive shaft are schematically shown. force;
  • FIG. 5 shows an enlarged cross-sectional view in which the handle of the movable scroll of the scroll compressor in FIG. 3 fits in the eccentric recess of the drive shaft, in which the centrifugal force of the counterweight and the drive of the drive shaft are schematically shown force;
  • FIG. 6 shows a combined perspective view of the weight and bushing of the scroll compressor in FIG. 3;
  • FIG. 7 shows a perspective view of the eccentric recess of the drive shaft in FIG. 3;
  • FIG. 8 shows a perspective view of the movable vortex including the handle in FIG. 3;
  • FIG. 9 shows a perspective view of the drive bearing in FIG. 4.
  • FIG. 10 shows a longitudinal cross-sectional view of a fixed connection of a bush and a drive shaft of a scroll compressor according to an aspect of an embodiment of the present disclosure
  • FIG. 11 shows a cross-sectional view of the bushing and the drive shaft of FIG. 10 fixedly connected;
  • FIG. 12 shows a combined perspective view of the weight of the scroll compressor of FIG. 10 and the bush with positioning holes
  • FIG. 13 shows a perspective view of the eccentric recessed portion of the drive shaft in FIG. 10 having a matching positioning hole
  • FIG. 14 shows a perspective view of the cross pin shaft as a fixing member in FIG. 10;
  • FIG. 15 shows a longitudinal cross-sectional view of a bush of a scroll compressor and a drive shaft fixedly connected by a vertical pin shaft according to another aspect of an embodiment of the present disclosure.
  • FIG. 16 shows a cross-sectional view of the bush of FIG. 15 fixedly connected to the drive shaft.
  • the scroll compressor 10 generally includes a housing 110, a top cover 112 provided at one end of the housing 110, a bottom cover 114 provided at the other end of the housing 110, and provided between the top cover 112 and the housing 110 to
  • the internal space of the compressor is divided into a partition 116 on the high-pressure side and the low-pressure side.
  • the partition 116 and the top cover 112 form a high-pressure side
  • the partition 116, the housing 110 and the bottom cover 114 form a low-pressure side.
  • An intake joint 118 for sucking fluid is provided on the low-pressure side
  • an exhaust joint 119 for discharging compressed fluid is provided on the high-pressure side.
  • a motor 120 composed of a stator 122 and a rotor 124 is provided in the housing 110.
  • the rotor 124 is provided with a drive shaft 30 to drive a compression mechanism composed of a fixed scroll 150 and a movable scroll 160.
  • the movable scroll 160 includes an end plate 164, a hub portion 162 formed on one side of the end plate, and a spiral blade 166 formed on the other side of the end plate.
  • the fixed scroll 150 includes an end plate 154, a spiral blade 156 formed on one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate. Between the spiral blade 156 of the fixed scroll 150 and the spiral blade 166 of the movable scroll 160 are formed a series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side.
  • a part of the drive shaft 30 is supported by the main bearing 144 provided in the main bearing housing 20.
  • An eccentric crank pin 32 is formed at one end of the drive shaft 30.
  • the eccentric crank pin 32 is fitted in the hub 162 of the movable scroll 160 via the bush 200 to drive the movable scroll 160.
  • the main bearing housing 20 is provided with a main bearing cover plate 50 as a thrust plate.
  • the main bearing cover 50 may be fixed to the main bearing housing 20 by a fixing device.
  • a space is formed between the main bearing housing 20 and the main bearing cover 50.
  • One side of the movable scroll 160 is supported by the main bearing cover 50.
  • the movable scroll 160 will rotate in translation relative to the fixed scroll 150 (ie, the central axis of the movable scroll 160 revolves around the central axis of the fixed scroll 150, but the movable scroll 160 itself does not revolve around itself The central axis of the rotation) to achieve fluid compression.
  • the above translational rotation is achieved by the cross slip ring 190 provided between the fixed scroll 150 and the movable scroll 160.
  • the fluid compressed by the fixed scroll 150 and the movable scroll 160 is discharged to the high-pressure side through the exhaust port 152.
  • a check valve or exhaust valve 170 is provided at the center orifice of the partition 116.
  • the movable scroll 160 will rotate in translation relative to the fixed scroll 150 (ie, the central axis of the movable scroll 160 revolves around the central axis of the fixed scroll 150, but The movable scroll 160 itself will not rotate around its own central axis), so that the movable scroll 160 will generate a centrifugal force F3. Due to the centrifugal force F3 and / or the gas force of the compression mechanism during the operation of the movable scroll 160, the fixed scroll A contact force F4 is generated between the side surface of the spiral blade 156 of the spiral 150 and the side surface of the spiral blade 166 of the movable scroll 160.
  • the indication of the direction of the force in FIG. 2 is only exemplary.
  • scroll compressors especially inverter scroll compressors, require changes in compressor speed to achieve changes in operating conditions, depending on ambient temperature.
  • the centrifugal force of the movable vortex becomes larger, and the contact force between the movable vortex and the fixed vortex also becomes greater.
  • the maximum strength of the vortex blade contact wall is exceeded, damage and failure may occur, resulting in unpredictable sudden situation.
  • the scroll compressor 10 may be further provided with a counterweight 300.
  • the counterweight 300 is configured to be able to rotate with the drive shaft 30 and the centrifugal force F1 due to the rotation of the counterweight 300 may act on the hub 162 of the movable scroll 160, for example.
  • the drive shaft 30 of the scroll compressor drives the movable scroll 160 of the scroll compressor via the bush 200
  • the counterweight includes a circular through hole 301
  • the bush 200 includes a cylindrical portion 201 that cooperates with the circular through hole 301
  • the weight 300 is attached to the bush 200 in such a manner that the inner peripheral surface of the circular through hole 301 and the outer peripheral surface of the cylindrical portion 201 are interference fitted.
  • the direction of the centrifugal force F1 of the counterweight 300 may be set to be substantially opposite to the direction of the centrifugal force F3 of the movable scroll 160. Therefore, the counterweight can effectively cancel the centrifugal force of the movable scroll 160 in order to reduce the contact force F4.
  • the centrifugal force F1 due to the rotation of the counterweight and the driving force F2 provided by the drive shaft 130 are not on the same plane, which produces clockwise rotation as shown in FIG. 2 The bending moment in the direction, so that the bushing produces a certain bending torque.
  • the structure of the counterweight in the scroll compressor described above makes the drive shaft (particularly, the eccentric crank pin) elongate, which causes the compressor housing to be elongated, increasing the cost and increasing the noise.
  • the scroll compressor 100 generally includes a housing 110, a top cover 112 provided at one end of the housing 110, a bottom cover 114 provided at the other end of the housing 110, and a top cover A partition 116 between the 112 and the housing 110 to divide the internal space of the compressor into a high-pressure side and a low-pressure side.
  • the partition 116 and the top cover 112 constitute a high-pressure side
  • the partition 116, the housing 110 and the bottom cover 114 constitute a low-pressure side.
  • An intake joint 118 for sucking fluid is provided on the low-pressure side
  • an exhaust joint 119 for discharging compressed fluid is provided on the high-pressure side.
  • a motor 120 composed of a stator 122 and a rotor 124 is provided in the housing 110.
  • the rotor 124 is provided with a drive shaft 130 to drive the compression mechanism composed of the fixed scroll 150 and the movable scroll 160.
  • the movable scroll 160 includes an end plate 164, a shank portion 163 formed on one side of the end plate, and a spiral blade 166 formed on the other side of the end plate.
  • the fixed scroll 150 includes an end plate 154, a spiral blade 156 formed on one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate. Between the spiral blade 156 of the fixed scroll 150 and the spiral blade 166 of the movable scroll 160 are formed a series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side.
  • the main bearing housing 20 is provided with a main bearing cover plate 50 as a thrust plate.
  • the main bearing cover 50 may be fixed to the main bearing housing 20 by a fixing device.
  • a space is formed between the main bearing housing 20 and the main bearing cover 50.
  • One side of the movable scroll 160 is supported by the main bearing cover 50.
  • the movable scroll 160 will rotate in translation relative to the fixed scroll 150 (ie, the central axis of the movable scroll 160 revolves around the central axis of the fixed scroll 150, but the movable scroll 160 itself does not revolve around itself The central axis of the rotation) to achieve fluid compression.
  • the above translational rotation is achieved by the cross slip ring 190 provided between the fixed scroll 150 and the movable scroll 160.
  • the fluid compressed by the fixed scroll 150 and the movable scroll 160 is discharged to the high-pressure side through the exhaust port 152.
  • a check valve or exhaust valve 170 is provided at the center orifice of the partition 116.
  • a part of the drive shaft 130 is supported by the main bearing 144 provided in the main bearing housing 20.
  • An eccentric recess 132 is formed at one end of the drive shaft 130.
  • the handle 163 is fitted in the eccentric recess 132 via the bushing 400 so that the movable scroll 160 is driven by the drive shaft 130, and the scroll compressor 100 includes a counterweight 600 installed on the bushing 400 and capable of rotating with the drive shaft 130 And the counterweight 300 generates centrifugal force due to rotation to balance the centrifugal force of the movable scroll 160 to reduce the contact force between the side surface of the spiral blade 156 of the fixed scroll 150 and the side surface of the spiral blade 166 of the movable scroll 160.
  • the centrifugal force F1 of the counterweight can be made It is on the same plane as the driving force F2 of the drive shaft, which reduces the bending moment to the bushing, and at the same time can reduce the wear on the drive bearing (usually provided between the bushing and the handle) and improve the reliability of the compressor.
  • the height of the drive shaft (especially the upper end of the drive shaft) can be shortened, and the height of the housing can be reduced, thereby reducing the cost of the compressor and also reducing the noise of the compressor.
  • the counterweight 600 may include a mounting portion 601 and an eccentric weighting portion 602.
  • the mounting portion 601 has a complete or partial ring shape and is mounted to the end plate 164 of the bushing 400 and the movable scroll 160.
  • the eccentric weighted portion 602 extends axially away from the end plate of the movable scroll 160 from the mounting portion 601.
  • the eccentric weighting portion 602 may extend axially, radially or axially and radially relative to the mounting portion 601 to adjust the center of mass of the weight 600 such that the centrifugal force of the weight 600 and the eccentric recess 132
  • the driving force provided is in the same plane.
  • the axial thickness of the mounting portion 601 can be set to be smaller than the thickness of the portion of the eccentric weighting portion 602 adjacent to the mounting portion 601, this configuration can further reduce the counterweight in the axial direction of the drive shaft The installation size, and thus the height of the housing, reduces the cost of the compressor.
  • the bush 400 may be an unloading bush capable of radial translation with respect to the drive shaft 130, and a substantially flat driving surface 1331 is provided on the side surface of the eccentric recess 132, outside the unloading bush 400 The surface is provided with a substantially flat driven surface 4001 that slide-fits with the driving surface 1331.
  • a cylindrical drive bearing 500 (see FIGS. 4 and 9) is provided between the bush 400 and the handle 163, the inner cylindrical surface of the drive bearing 500 and the outer surface of the handle 163 have an interference fit, and the drive bearing The outer cylindrical surface of 500 is in clearance fit with the inner surface of the bush 400.
  • the scroll compressor according to other aspects of the embodiments of the present disclosure will be described below with reference to FIGS. 10 to 16, wherein the bushes 400a, 400b are fixedly connected to the drive shaft, and differs from the aspects of the above-described embodiment in that:
  • the sleeve is not an unloading bush that can provide radial flexibility, but by using a fixed connection between the bush and the drive shaft, it is convenient to accurately position the weight and the installation angle of the bush relative to the drive shaft, to save costs.
  • a first positioning hole may be provided on the outer surface of the bush 400a, and a second positioning hole corresponding to the first positioning hole may be provided on the side surface of the eccentric recess 132a, and A cross pin shaft 700 passing through the first positioning hole and the second positioning hole is provided to fix the bush to the drive shaft.
  • the shape of the cross pin shaft 700 may be a cylinder, a rectangular parallelepiped, or a truncated pyramid. In this way, the vertical pin shaft of an appropriate shape can be selected according to needs to provide appropriate fixation.
  • a first positioning groove may be provided on the outer surface of the bush 400b, and a first positioning groove corresponding to the first positioning groove may be provided on the side surface of the eccentric recess 132b There are two positioning grooves, and a vertical pin shaft 800 which is accommodated in the first positioning groove and the second positioning groove is provided.
  • the shape of the vertical pin shaft 800 may be a cylinder, a rectangular parallelepiped, or a truncated pyramid. In this way, the vertical pin shaft of an appropriate shape can be selected according to needs to provide appropriate fixation.
  • the bushes 400a, 400b can also be fixedly connected to the drive shaft 130 by bolts.
  • the outer surface of the aforementioned bushings 400a, 400b may be interference, transition, or clearance fit with the side surfaces of the eccentric recesses 132a, 132b. In this way, an appropriate fitting method can be selected as required, for example, in the case of selecting an interference fit, the fixed connection of the bush and the eccentric recess can be further ensured.
  • FIGS. 3 to 9 relate to the drive bearing structure, the shape structure of the weight (mounting portion and eccentric weighting portion), and the split structure of the weight, etc. It can be applied to the embodiments in FIGS. 10 to 16.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

A scroll compressor (10) comprises: a moving scroll (160) comprising a shank portion (163); a driving shaft (130) comprising an eccentric recess (132, 132a, 132b); and a bushing (400, 400a, 400b). The shank portion (163) is fit inside the eccentric recess (132, 132a, 132b) by means of the bushing (400, 400a, 400b), such that the moving scroll (160) is driven by the driving shaft (130). The scroll compressor (100) further comprises a counterweight (600) provided on the bushing (400). The scroll compressor ensures safety and reliability under operating conditions of high rotational speed, has a compact structure, and reduces noise.

Description

涡旋压缩机Scroll compressor
本申请要求于2018年10月23日提交中国国家知识产权局、申请号为201811238677.3、名称为“涡旋压缩机”的中国专利申请的优先权，并且本申请要求于2018年10月23日提交中国国家知识产权局、申请号为201821719557.0、名称为“涡旋压缩机”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。This application requires the priority of the Chinese patent application filed with the State Intellectual Property Office of China on October 23, 2018, with the application number 201811238677.3 and the name "Scroll Compressor", and the application is required to be filed on October 23, 2018 The priority of the Chinese patent application of the State Intellectual Property Office of China with the application number 201821719557.0 and the name "Scroll Compressor" is incorporated by reference in this application.
技术领域Technical field
本公开涉及一种涡旋压缩机。The present disclosure relates to a scroll compressor.
背景技术Background technique
本部分的内容仅提供了与本公开相关的背景信息，其可能并不构成现有技术。The content of this section only provides background information related to the present disclosure, which may not constitute prior art.
涡旋压缩机(特别是变速涡旋压缩机)，在尤其是高转速工况下，涡旋叶片接触壁之间的接触力会由于动涡旋的离心力的增大而增大。因此，需要设置配重以抵消部分动涡旋的离心力。例如，配重可以设置在与动涡旋毂部一致的轴向位置处(比如连接至衬套)。然而，在一些情况下，由于主轴承座的凹部内的空间有限，难以使配重设置为使得配重的离心力与驱动轴的偏心销所施加的驱动力在同一平面上，这导致衬套和/或配重产生了弯矩。而且，在配重设置在与动涡旋毂部一致的轴向位置处的情况下，往往会导致偏心销加长进而导致整个压缩机的轴向尺寸加长。In scroll compressors (especially variable-speed scroll compressors), the contact force between the contact surfaces of the scroll blades will increase due to the increase in the centrifugal force of the movable scroll under especially high-speed operating conditions. Therefore, a counterweight needs to be provided to counteract the centrifugal force of part of the movable vortex. For example, the counterweight may be provided at an axial position consistent with the orbiting scroll hub (such as being connected to the bushing). However, in some cases, due to the limited space in the recess of the main bearing housing, it is difficult to set the counterweight so that the centrifugal force of the counterweight and the driving force applied by the eccentric pin of the drive shaft are on the same plane, which causes the bushing and / Or the counterweight produces a bending moment. Moreover, in the case where the weight is provided at an axial position consistent with the orbiting scroll hub portion, the eccentric pin is often elongated and the axial dimension of the entire compressor is elongated.
因此，需要一种能够在尤其是高转速工况下通过例如减小涡旋接触力和/或减小衬套的弯曲扭矩而确保安全可靠并且实现结构紧凑、降噪等的涡旋压缩机。Therefore, there is a need for a scroll compressor that can ensure safety and reliability and achieve a compact structure, noise reduction, etc., for example, by reducing scroll contact force and / or reducing the bending torque of the bushing under particularly high-speed operating conditions.
发明内容Summary of the invention
为了实现上述目的中的一个或多个，根据本公开一个方面，提供了一种涡旋压缩机，其包括：动涡旋，所述动涡旋包括柄部；驱动轴，所述驱动轴包括偏心凹部；衬套，所述柄部经由所述衬套配合在所述偏心凹部中使得所述动涡旋被所述驱动轴驱动，其中，所述涡旋压缩机还包括配重，所述配重安装在所述衬套上。In order to achieve one or more of the above objects, according to an aspect of the present disclosure, there is provided a scroll compressor including: a movable scroll, the movable scroll including a handle; a drive shaft, the drive shaft including An eccentric recess; a bush, the handle is fitted in the eccentric recess via the bush so that the movable scroll is driven by the drive shaft, wherein the scroll compressor further includes a counterweight, the The counterweight is installed on the bush.
有利地，所述衬套能够相对于所述驱动轴径向平移，在所述偏心凹部的侧表面上设置有大致平坦的驱动表面，在所述衬套的外表面上设置有与所述驱动 表面滑动配合的大致平坦的受驱动表面。Advantageously, the bushing is capable of radial translation with respect to the drive shaft, a substantially flat drive surface is provided on the side surface of the eccentric recess, and the drive is provided on the outer surface of the bushing A substantially flat driven surface with a sliding fit on the surface.
有利地，所述衬套固定连接至所述驱动轴。Advantageously, the bushing is fixedly connected to the drive shaft.
有利地，在所述衬套的外表面上设置有第一定位孔，在所述偏心凹部的侧表面上设置有与所述第一定位孔对应的第二定位孔，并且设置有穿过所述第一定位孔和所述第二定位孔的横销轴；并且/或者在所述衬套的外表面上设置有第一定位凹槽，在所述偏心凹部的侧表面上设置有与所述第一定位凹槽对应的第二定位凹槽，并且设置有配合容纳于所述第一定位凹槽和所述第二定位凹槽中的竖销轴。Advantageously, a first positioning hole is provided on the outer surface of the bush, a second positioning hole corresponding to the first positioning hole is provided on the side surface of the eccentric recess, and a through hole is provided A transverse pin shaft of the first positioning hole and the second positioning hole; and / or a first positioning groove is provided on the outer surface of the bush, and a side surface of the eccentric recess is provided with A second positioning groove corresponding to the first positioning groove is provided with a vertical pin shaft accommodated in the first positioning groove and the second positioning groove.
有利地，所述横销轴的形状为圆柱、长方体或锥棱台，所述竖销轴的形状为圆柱、长方体或锥棱台。Advantageously, the shape of the horizontal pin shaft is a cylinder, a rectangular parallelepiped or a truncated pyramid, and the shape of the vertical pin shaft is a cylinder, a rectangular parallelepiped or a truncated pyramid.
有利地，所述衬套通过螺栓固定连接至所述驱动轴。Advantageously, the bushing is fixedly connected to the drive shaft by bolts.
有利地，所述衬套的外表面与所述偏心凹部的侧表面过盈、过渡或间隙配合。Advantageously, the outer surface of the bushing is in interference, transition or clearance fit with the side surface of the eccentric recess.
有利地，在所述衬套与所述柄部之间设置有筒状的驱动轴承，所述驱动轴承的内圆柱面与所述柄部的外表面过盈配合，所述驱动轴承的外圆柱面与所述衬套的内表面间隙配合。Advantageously, a cylindrical drive bearing is provided between the bush and the handle, the inner cylindrical surface of the drive bearing is in interference fit with the outer surface of the handle, the outer cylinder of the drive bearing The surface is in clearance fit with the inner surface of the bush.
有利地，所述配重包括安装部和偏心加重部，所述安装部呈完全或部分圆环形并且安装至所述衬套的与所述动涡旋的端板相邻的端部，所述偏心加重部从所述安装部轴向地背离所述动涡旋的端板延伸。Advantageously, the counterweight includes a mounting portion and an eccentric weighting portion, the mounting portion has a complete or partial circular ring shape and is mounted to an end portion of the bush adjacent to the end plate of the movable scroll, so The eccentric weighting portion extends axially away from the end plate of the movable scroll from the mounting portion.
有利地，所述配重包括安装部和偏心加重部，所述安装部呈完全或部分圆环形，所述偏心加重部相对于所述安装部轴向地延伸、径向地延伸或者轴向地且径向地延伸，以调节所述配重的质心，使得所述配重的离心力与所述偏心凹部所提供的驱动力处于同一平面。Advantageously, the counterweight includes a mounting portion and an eccentric weighting portion, the mounting portion is completely or partially circular, and the eccentric weighting portion extends axially, radially, or axially relative to the mounting portion It extends on the ground and radially to adjust the center of mass of the weight so that the centrifugal force of the weight is in the same plane as the driving force provided by the eccentric recess.
有利地，所述配重包括呈完全或部分圆环形的安装部和从所述安装部延伸的偏心加重部，所述安装部的轴向厚度设置为小于所述偏心加重部的与所述安装部邻接的部分的厚度。Advantageously, the counterweight includes a completely or partially circular mounting portion and an eccentric weighted portion extending from the mounting portion, the axial thickness of the mounting portion is set to be smaller than that of the eccentric weighted portion and the The thickness of the portion adjacent to the mounting portion.
根据本公开的一种或几种实施方式的涡旋压缩机的优点例如在于：The advantages of the scroll compressor according to one or several embodiments of the present disclosure are, for example:
1)可以方便调节配重的质心，使得配重的离心力与驱动轴的驱动力在同一平面上，减小对衬套的弯矩，同时可以减小对驱动轴承的磨损，提高压缩机可靠性；2)可以缩短驱动轴的高度，并且减小壳体的高度，从而降低压缩机 的成本，同时也可以降低压缩机的噪音；3)通过将驱动轴和衬套通过销定位、螺栓连接等固定方式连接，以可靠地驱动动涡旋，同时也可以方便地定位配重相对于衬套的安装角度，从而节省成本。1) The center of mass of the counterweight can be easily adjusted, so that the centrifugal force of the counterweight and the driving force of the drive shaft are on the same plane, reducing the bending moment of the bush, and at the same time reducing the wear on the drive bearing and improving the reliability of the compressor ; 2) The height of the drive shaft can be shortened, and the height of the housing can be reduced, thereby reducing the cost of the compressor, and also the noise of the compressor; 3) By positioning the drive shaft and bushing through pins, bolting, etc. It is connected in a fixed way to reliably drive the orbiting scroll, and at the same time, it can also conveniently locate the installation angle of the counterweight relative to the bushing, thereby saving costs.
附图说明BRIEF DESCRIPTION
通过以下参照附图的描述，本公开的一个或几个实施方式的特征和优点将变得更加容易理解，在附图中：The features and advantages of one or several embodiments of the present disclosure will become easier to understand through the following description with reference to the drawings, in the drawings:
图1是涡旋压缩机的纵剖视图；Figure 1 is a longitudinal sectional view of a scroll compressor;
图2是图1中的涡旋压缩机的动涡旋的离心力、驱动轴的驱动力、动涡旋和定涡旋之间的接触力、配重的离心力的示意图；2 is a schematic diagram of the centrifugal force of the movable scroll of the scroll compressor of FIG. 1, the driving force of the drive shaft, the contact force between the movable scroll and the fixed scroll, and the centrifugal force of the counterweight;
图3示出了根据本公开的一个实施方式的涡旋压缩机的纵剖视图；3 shows a longitudinal sectional view of a scroll compressor according to an embodiment of the present disclosure;
图4示出了图3中的涡旋压缩机的动涡旋的柄部配合在驱动轴的偏心凹部中的放大的纵剖视图，其中示意性地示出了配重的离心力、驱动轴的驱动力；FIG. 4 shows an enlarged longitudinal cross-sectional view in which the handle of the movable scroll of the scroll compressor in FIG. 3 fits in the eccentric recess of the drive shaft, wherein the centrifugal force of the counterweight and the drive of the drive shaft are schematically shown. force;
图5示出了图3中的涡旋压缩机的动涡旋的柄部配合在驱动轴的偏心凹部中的放大的横剖视图，其中示意性地示出了配重的离心力、驱动轴的驱动力；FIG. 5 shows an enlarged cross-sectional view in which the handle of the movable scroll of the scroll compressor in FIG. 3 fits in the eccentric recess of the drive shaft, in which the centrifugal force of the counterweight and the drive of the drive shaft are schematically shown force;
图6示出了图3中的涡旋压缩机的配重和衬套的组合立体图；6 shows a combined perspective view of the weight and bushing of the scroll compressor in FIG. 3;
图7示出了图3中的驱动轴的偏心凹部的立体图；7 shows a perspective view of the eccentric recess of the drive shaft in FIG. 3;
图8示出了图3中的包括柄部的动涡旋的立体图；8 shows a perspective view of the movable vortex including the handle in FIG. 3;
图9示出了图4中的驱动轴承的立体图；9 shows a perspective view of the drive bearing in FIG. 4;
图10示出了根据本公开的实施方式的一个方面的涡旋压缩机的衬套与驱动轴固定连接的纵剖视图；10 shows a longitudinal cross-sectional view of a fixed connection of a bush and a drive shaft of a scroll compressor according to an aspect of an embodiment of the present disclosure;
图11示出了图10中的衬套与驱动轴固定连接的横剖视图；11 shows a cross-sectional view of the bushing and the drive shaft of FIG. 10 fixedly connected;
图12示出了图10中的涡旋压缩机的配重和具有定位孔的衬套的组合立体图；FIG. 12 shows a combined perspective view of the weight of the scroll compressor of FIG. 10 and the bush with positioning holes;
图13示出了图10中的驱动轴的具有配合定位孔的偏心凹部的立体图；13 shows a perspective view of the eccentric recessed portion of the drive shaft in FIG. 10 having a matching positioning hole;
图14示出了图10中的作为固定构件的横销轴的立体图；14 shows a perspective view of the cross pin shaft as a fixing member in FIG. 10;
图15示出了根据本公开的实施方式的另一方面的涡旋压缩机的衬套与驱动轴通过竖销轴固定连接的纵剖视图；以及15 shows a longitudinal cross-sectional view of a bush of a scroll compressor and a drive shaft fixedly connected by a vertical pin shaft according to another aspect of an embodiment of the present disclosure; and
图16示出了图15中的衬套与驱动轴固定连接的横剖视图。FIG. 16 shows a cross-sectional view of the bush of FIG. 15 fixedly connected to the drive shaft.
具体实施方式detailed description
下面对实施方式的描述仅仅是示范性的，而绝不是对本公开及其应用或用 法的限制。The following description of the embodiments is merely exemplary, and in no way limits the disclosure and its applications or uses.
在各个附图中采用相同的附图标记来表示相同的部件，因此相同部件的构造将不再重复描述。The same reference numerals are used in the various drawings to denote the same components, so the configuration of the same components will not be repeated.
首先，参照图1和图2描述根据相关技术的涡旋压缩机及其配重。First, the scroll compressor and its counterweight according to the related art will be described with reference to FIGS. 1 and 2.
参见图1，涡旋压缩机10一般包括壳体110、设置在壳体110一端的顶盖112、设置在壳体110另一端的底盖114以及设置在顶盖112和壳体110之间以将压缩机的内部空间分隔成高压侧和低压侧的隔板116。隔板116和顶盖112之间构成高压侧，而隔板116、壳体110和底盖114之间构成低压侧。在低压侧设置有用于吸入流体的进气接头118，在高压侧设置有用于排出压缩后的流体的排气接头119。壳体110中设置有由定子122和转子124构成的电机120。转子124中设置有驱动轴30以驱动由定涡旋150和动涡旋160构成的压缩机构。动涡旋160包括端板164、形成在端板一侧的毂部162和形成在端板另一侧的螺旋状的叶片166。定涡旋150包括端板154、形成在端板一侧的螺旋状的叶片156和形成在端板的大致中央位置处的排气口152。在定涡旋150的螺旋叶片156和动涡旋160的螺旋叶片166之间形成一系列体积从径向外侧向径向内侧逐渐减小的压缩腔。Referring to FIG. 1, the scroll compressor 10 generally includes a housing 110, a top cover 112 provided at one end of the housing 110, a bottom cover 114 provided at the other end of the housing 110, and provided between the top cover 112 and the housing 110 to The internal space of the compressor is divided into a partition 116 on the high-pressure side and the low-pressure side. The partition 116 and the top cover 112 form a high-pressure side, and the partition 116, the housing 110 and the bottom cover 114 form a low-pressure side. An intake joint 118 for sucking fluid is provided on the low-pressure side, and an exhaust joint 119 for discharging compressed fluid is provided on the high-pressure side. A motor 120 composed of a stator 122 and a rotor 124 is provided in the housing 110. The rotor 124 is provided with a drive shaft 30 to drive a compression mechanism composed of a fixed scroll 150 and a movable scroll 160. The movable scroll 160 includes an end plate 164, a hub portion 162 formed on one side of the end plate, and a spiral blade 166 formed on the other side of the end plate. The fixed scroll 150 includes an end plate 154, a spiral blade 156 formed on one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate. Between the spiral blade 156 of the fixed scroll 150 and the spiral blade 166 of the movable scroll 160 are formed a series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side.
驱动轴30的一部分由设置在主轴承座20中的主轴承144支撑。驱动轴30的一端形成有偏心曲柄销32。偏心曲柄销32经由衬套200配合在动涡旋160的毂部162中以驱动动涡旋160。A part of the drive shaft 30 is supported by the main bearing 144 provided in the main bearing housing 20. An eccentric crank pin 32 is formed at one end of the drive shaft 30. The eccentric crank pin 32 is fitted in the hub 162 of the movable scroll 160 via the bush 200 to drive the movable scroll 160.
主轴承座20上设置有作为止推板的主轴承盖板50。主轴承盖板50可以通过固定装置固定在主轴承座20上。在主轴承座20和主轴承盖板50之间形成空间。动涡旋160的一侧由主轴承盖板50支撑。通过电机120的驱动，动涡旋160将相对于定涡旋150平动转动(即，动涡旋160的中心轴线绕定涡旋150的中心轴线回转，但是动涡旋160本身不会绕自身的中心轴线旋转)以实现流体的压缩。上述平动转动通过定涡旋150和动涡旋160之间设置的十字滑环190来实现。经过定涡旋150和动涡旋160压缩后的流体通过排气口152排出到高压侧。为了防止高压侧的流体在特定情况下经由排气口152回流，在隔板116的中央孔口处设置有单向阀或排气阀170。The main bearing housing 20 is provided with a main bearing cover plate 50 as a thrust plate. The main bearing cover 50 may be fixed to the main bearing housing 20 by a fixing device. A space is formed between the main bearing housing 20 and the main bearing cover 50. One side of the movable scroll 160 is supported by the main bearing cover 50. Driven by the motor 120, the movable scroll 160 will rotate in translation relative to the fixed scroll 150 (ie, the central axis of the movable scroll 160 revolves around the central axis of the fixed scroll 150, but the movable scroll 160 itself does not revolve around itself The central axis of the rotation) to achieve fluid compression. The above translational rotation is achieved by the cross slip ring 190 provided between the fixed scroll 150 and the movable scroll 160. The fluid compressed by the fixed scroll 150 and the movable scroll 160 is discharged to the high-pressure side through the exhaust port 152. In order to prevent the fluid on the high-pressure side from flowing back through the exhaust port 152 under certain circumstances, a check valve or exhaust valve 170 is provided at the center orifice of the partition 116.
在运转过程中，参见图2，通过电机120的驱动，动涡旋160将相对于定涡旋150平动转动(即，动涡旋160的中心轴线绕定涡旋150的中心轴线回转， 但是动涡旋160本身不会绕自身的中心轴线旋转)，从而动涡旋160将产生离心力F3，由于动涡旋160在运转过程中的离心力F3和/或压缩机构的气体力，因此在定涡旋150的螺旋叶片156的侧表面与动涡旋160的螺旋叶片166的侧表面之间产生接触力F4。这里，需要指出的是，图2中的力的方向的标示仅是示例性的。During operation, referring to FIG. 2, driven by the motor 120, the movable scroll 160 will rotate in translation relative to the fixed scroll 150 (ie, the central axis of the movable scroll 160 revolves around the central axis of the fixed scroll 150, but The movable scroll 160 itself will not rotate around its own central axis), so that the movable scroll 160 will generate a centrifugal force F3. Due to the centrifugal force F3 and / or the gas force of the compression mechanism during the operation of the movable scroll 160, the fixed scroll A contact force F4 is generated between the side surface of the spiral blade 156 of the spiral 150 and the side surface of the spiral blade 166 of the movable scroll 160. Here, it should be pointed out that the indication of the direction of the force in FIG. 2 is only exemplary.
然而，涡旋压缩机，特别是变频涡旋压缩机，会根据环境温度而需求例如改变压缩机转速从而实现工况改变。随着转速的提高，动涡旋的离心力变大，动涡旋与定涡旋之间接触力也会变大，当超过涡旋叶片接触壁最大强度时可能会发生损坏失效，造成不可预料突发状况。However, scroll compressors, especially inverter scroll compressors, require changes in compressor speed to achieve changes in operating conditions, depending on ambient temperature. As the rotational speed increases, the centrifugal force of the movable vortex becomes larger, and the contact force between the movable vortex and the fixed vortex also becomes greater. When the maximum strength of the vortex blade contact wall is exceeded, damage and failure may occur, resulting in unpredictable sudden situation.
为了降低定涡旋150的螺旋叶片156的侧表面与动涡旋160的螺旋叶片166的侧表面之间的接触力，涡旋压缩机10可以进一步设置有配重300。配重300构造成能够随驱动轴30旋转并且配重300由于旋转而造成的离心力F1可以例如作用在动涡旋160的毂部162上。In order to reduce the contact force between the side surface of the spiral blade 156 of the fixed scroll 150 and the side surface of the spiral blade 166 of the movable scroll 160, the scroll compressor 10 may be further provided with a counterweight 300. The counterweight 300 is configured to be able to rotate with the drive shaft 30 and the centrifugal force F1 due to the rotation of the counterweight 300 may act on the hub 162 of the movable scroll 160, for example.
例如，涡旋压缩机的驱动轴30经由衬套200驱动涡旋压缩机的动涡旋160，配重包括圆形通孔301，衬套200包括与圆形通孔301配合的圆柱部201，其中，配重300以圆形通孔301的内周面与圆柱部201的外周面过盈装配的方式安装至衬套200。配重300的离心力F1的方向可以设置成与动涡旋160的离心力F3的方向大致相反。因此，配重能够有效地抵消动涡旋160的离心力以便减小接触力F4。For example, the drive shaft 30 of the scroll compressor drives the movable scroll 160 of the scroll compressor via the bush 200, the counterweight includes a circular through hole 301, the bush 200 includes a cylindrical portion 201 that cooperates with the circular through hole 301, The weight 300 is attached to the bush 200 in such a manner that the inner peripheral surface of the circular through hole 301 and the outer peripheral surface of the cylindrical portion 201 are interference fitted. The direction of the centrifugal force F1 of the counterweight 300 may be set to be substantially opposite to the direction of the centrifugal force F3 of the movable scroll 160. Therefore, the counterweight can effectively cancel the centrifugal force of the movable scroll 160 in order to reduce the contact force F4.
然而在上述的具有配重的示例性涡旋压缩机中，配重由于旋转造成的离心力F1与驱动轴130提供的驱动力F2不在一个平面上，这样产生了沿如图2所示的顺时针方向的弯矩，从而使得衬套产生一定弯曲扭矩。同时上述涡旋压缩机中的配重的构造使得驱动轴(特别地，偏心曲柄销)加长，这造成压缩机的壳体加长，增加了成本并且增大了噪音。However, in the above-mentioned exemplary scroll compressor with a counterweight, the centrifugal force F1 due to the rotation of the counterweight and the driving force F2 provided by the drive shaft 130 are not on the same plane, which produces clockwise rotation as shown in FIG. 2 The bending moment in the direction, so that the bushing produces a certain bending torque. At the same time, the structure of the counterweight in the scroll compressor described above makes the drive shaft (particularly, the eccentric crank pin) elongate, which causes the compressor housing to be elongated, increasing the cost and increasing the noise.
下面将参照图3至图9描述根据本公开的实施方式的涡旋压缩机100的基本构造和原理。The basic configuration and principle of the scroll compressor 100 according to an embodiment of the present disclosure will be described below with reference to FIGS. 3 to 9.
如图3所示，根据本公开实施方式的涡旋压缩机100一般包括壳体110、设置在壳体110一端的顶盖112、设置在壳体110另一端的底盖114以及设置在顶盖112和壳体110之间以将压缩机的内部空间分隔成高压侧和低压侧的隔板116。隔板116和顶盖112之间构成高压侧，而隔板116、壳体110和底盖 114之间构成低压侧。在低压侧设置有用于吸入流体的进气接头118，在高压侧设置有用于排出压缩后的流体的排气接头119。壳体110中设置有由定子122和转子124构成的电机120。转子124中设置有驱动轴130以驱动由定涡旋150和动涡旋160构成的压缩机构。动涡旋160包括端板164、形成在端板一侧的柄部163和形成在端板另一侧的螺旋状的叶片166。定涡旋150包括端板154、形成在端板一侧的螺旋状的叶片156和形成在端板的大致中央位置处的排气口152。在定涡旋150的螺旋叶片156和动涡旋160的螺旋叶片166之间形成一系列体积从径向外侧向径向内侧逐渐减小的压缩腔。As shown in FIG. 3, the scroll compressor 100 according to an embodiment of the present disclosure generally includes a housing 110, a top cover 112 provided at one end of the housing 110, a bottom cover 114 provided at the other end of the housing 110, and a top cover A partition 116 between the 112 and the housing 110 to divide the internal space of the compressor into a high-pressure side and a low-pressure side. The partition 116 and the top cover 112 constitute a high-pressure side, and the partition 116, the housing 110 and the bottom cover 114 constitute a low-pressure side. An intake joint 118 for sucking fluid is provided on the low-pressure side, and an exhaust joint 119 for discharging compressed fluid is provided on the high-pressure side. A motor 120 composed of a stator 122 and a rotor 124 is provided in the housing 110. The rotor 124 is provided with a drive shaft 130 to drive the compression mechanism composed of the fixed scroll 150 and the movable scroll 160. The movable scroll 160 includes an end plate 164, a shank portion 163 formed on one side of the end plate, and a spiral blade 166 formed on the other side of the end plate. The fixed scroll 150 includes an end plate 154, a spiral blade 156 formed on one side of the end plate, and an exhaust port 152 formed at a substantially central position of the end plate. Between the spiral blade 156 of the fixed scroll 150 and the spiral blade 166 of the movable scroll 160 are formed a series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side.
主轴承座20上设置有作为止推板的主轴承盖板50。主轴承盖板50可以通过固定装置固定在主轴承座20上。在主轴承座20和主轴承盖板50之间形成空间。动涡旋160的一侧由主轴承盖板50支撑。通过电机120的驱动，动涡旋160将相对于定涡旋150平动转动(即，动涡旋160的中心轴线绕定涡旋150的中心轴线回转，但是动涡旋160本身不会绕自身的中心轴线旋转)以实现流体的压缩。上述平动转动通过定涡旋150和动涡旋160之间设置的十字滑环190来实现。经过定涡旋150和动涡旋160压缩后的流体通过排气口152排出到高压侧。为了防止高压侧的流体在特定情况下经由排气口152回流，在隔板116的中央孔口处设置有单向阀或排气阀170。The main bearing housing 20 is provided with a main bearing cover plate 50 as a thrust plate. The main bearing cover 50 may be fixed to the main bearing housing 20 by a fixing device. A space is formed between the main bearing housing 20 and the main bearing cover 50. One side of the movable scroll 160 is supported by the main bearing cover 50. Driven by the motor 120, the movable scroll 160 will rotate in translation relative to the fixed scroll 150 (ie, the central axis of the movable scroll 160 revolves around the central axis of the fixed scroll 150, but the movable scroll 160 itself does not revolve around itself The central axis of the rotation) to achieve fluid compression. The above translational rotation is achieved by the cross slip ring 190 provided between the fixed scroll 150 and the movable scroll 160. The fluid compressed by the fixed scroll 150 and the movable scroll 160 is discharged to the high-pressure side through the exhaust port 152. In order to prevent the fluid on the high-pressure side from flowing back through the exhaust port 152 under certain circumstances, a check valve or exhaust valve 170 is provided at the center orifice of the partition 116.
驱动轴130的一部分由设置在主轴承座20中的主轴承144支撑。驱动轴130的一端形成有偏心凹部132。柄部163经由衬套400配合在偏心凹部132中使得动涡旋160被驱动轴130驱动，涡旋压缩机100包括配重600，配重600安装在衬套400上且能够随驱动轴130旋转并且配重300由于旋转而产生离心力以平衡动涡旋160的离心力，以降低定涡旋150的螺旋叶片156的侧表面与动涡旋160的螺旋叶片166的侧表面之间的接触力。A part of the drive shaft 130 is supported by the main bearing 144 provided in the main bearing housing 20. An eccentric recess 132 is formed at one end of the drive shaft 130. The handle 163 is fitted in the eccentric recess 132 via the bushing 400 so that the movable scroll 160 is driven by the drive shaft 130, and the scroll compressor 100 includes a counterweight 600 installed on the bushing 400 and capable of rotating with the drive shaft 130 And the counterweight 300 generates centrifugal force due to rotation to balance the centrifugal force of the movable scroll 160 to reduce the contact force between the side surface of the spiral blade 156 of the fixed scroll 150 and the side surface of the spiral blade 166 of the movable scroll 160.
如图4所示，由于动涡旋的柄部配合容纳于驱动轴的偏心凹部中以驱动动涡旋并且将配重安装在衬套上，与相关技术相比，能够使配重的离心力F1与驱动轴的驱动力F2处在同一平面上，减小对衬套的弯矩，同时可以减小对驱动轴承(通常设置在衬套与柄部之间)的磨损，提高压缩机可靠性。同时，借助于该构造，可以缩短驱动轴(特别是驱动轴的上端部)的高度，并且减小壳体的高度，从而降低压缩机的成本，同时也可以降低压缩机的噪音。As shown in FIG. 4, since the handle portion of the movable scroll fits and is accommodated in the eccentric concave portion of the drive shaft to drive the movable scroll and install the counterweight on the bush, compared with the related art, the centrifugal force F1 of the counterweight can be made It is on the same plane as the driving force F2 of the drive shaft, which reduces the bending moment to the bushing, and at the same time can reduce the wear on the drive bearing (usually provided between the bushing and the handle) and improve the reliability of the compressor. At the same time, with this configuration, the height of the drive shaft (especially the upper end of the drive shaft) can be shortened, and the height of the housing can be reduced, thereby reducing the cost of the compressor and also reducing the noise of the compressor.
具体地，参见图4和图6，配重600可以包括安装部601和偏心加重部602， 安装部601呈完全或部分圆环形并且安装至衬套400的与动涡旋160的端板164相邻的端部，偏心加重部602从安装部601轴向地背离动涡旋160的端板延伸。Specifically, referring to FIGS. 4 and 6, the counterweight 600 may include a mounting portion 601 and an eccentric weighting portion 602. The mounting portion 601 has a complete or partial ring shape and is mounted to the end plate 164 of the bushing 400 and the movable scroll 160. At the adjacent ends, the eccentric weighted portion 602 extends axially away from the end plate of the movable scroll 160 from the mounting portion 601.
有利地，偏心加重部602可以相对于安装部601轴向地延伸、径向地延伸或者轴向地且径向地延伸，以调节配重600的质心，使得配重600的离心力与偏心凹部132所提供的驱动力处于同一平面。其中，更有利地，安装部601的轴向厚度可以设置为小于偏心加重部602的与安装部601邻接的部分的厚度，该构造可以进一步地减小在驱动轴的轴向方向上的配重安装尺寸，并且因而减小壳体的高度，从而降低压缩机的成本。Advantageously, the eccentric weighting portion 602 may extend axially, radially or axially and radially relative to the mounting portion 601 to adjust the center of mass of the weight 600 such that the centrifugal force of the weight 600 and the eccentric recess 132 The driving force provided is in the same plane. Among them, more advantageously, the axial thickness of the mounting portion 601 can be set to be smaller than the thickness of the portion of the eccentric weighting portion 602 adjacent to the mounting portion 601, this configuration can further reduce the counterweight in the axial direction of the drive shaft The installation size, and thus the height of the housing, reduces the cost of the compressor.
参见图5至图7，衬套400可以为能够相对于驱动轴130径向平移的卸载衬套，在偏心凹部132的侧表面上设置有大致平坦的驱动表面1331，在卸载衬套400的外表面上设置有与驱动表面1331滑动配合的大致平坦的受驱动表面4001。借助于卸载衬套与凹部的驱动表面的这种滑动配合，为压缩机的动涡旋提供径向柔性。Referring to FIGS. 5 to 7, the bush 400 may be an unloading bush capable of radial translation with respect to the drive shaft 130, and a substantially flat driving surface 1331 is provided on the side surface of the eccentric recess 132, outside the unloading bush 400 The surface is provided with a substantially flat driven surface 4001 that slide-fits with the driving surface 1331. By means of this sliding fit of the unloading bush with the drive surface of the recess, radial flexibility is provided for the movable scroll of the compressor.
有利地，在衬套400与柄部163之间设置有筒状的驱动轴承500(参见图4和图9)，驱动轴承500的内圆柱面与柄部163的外表面过盈配合，驱动轴承500的外圆柱面与衬套400的内表面间隙配合。通过进一步以这种方式设置驱动轴承，能够提供可靠支承、降低摩擦从而确保可靠的驱动力传递。Advantageously, a cylindrical drive bearing 500 (see FIGS. 4 and 9) is provided between the bush 400 and the handle 163, the inner cylindrical surface of the drive bearing 500 and the outer surface of the handle 163 have an interference fit, and the drive bearing The outer cylindrical surface of 500 is in clearance fit with the inner surface of the bush 400. By further arranging the driving bearing in this way, it is possible to provide reliable support, reduce friction and ensure reliable transmission of driving force.
下面将参照图10至图16描述根据本公开的实施方式的其他方面的涡旋压缩机，其中，衬套400a、400b固定连接至驱动轴，与上述实施方式的方面的不同之处在于：衬套并非是能够提供径向柔性的卸载衬套，而是通过采用衬套和驱动轴固定连接的方式，从而方便精确定位配重和衬套相对于驱动轴的安装角度，以节省成本。The scroll compressor according to other aspects of the embodiments of the present disclosure will be described below with reference to FIGS. 10 to 16, wherein the bushes 400a, 400b are fixedly connected to the drive shaft, and differs from the aspects of the above-described embodiment in that: The sleeve is not an unloading bush that can provide radial flexibility, but by using a fixed connection between the bush and the drive shaft, it is convenient to accurately position the weight and the installation angle of the bush relative to the drive shaft, to save costs.
具体地，参见图10至图14，在衬套400a的外表面上可以设置有第一定位孔，在偏心凹部132a的侧表面上可以设置有与第一定位孔对应的第二定位孔，并且设置有穿过第一定位孔和第二定位孔的横销轴700，以将衬套固定至驱动轴。横销轴700的形状可以为圆柱、长方体或锥棱台。如此，可以根据需要选择适当形状的竖销轴，以提供合适的固定。Specifically, referring to FIGS. 10 to 14, a first positioning hole may be provided on the outer surface of the bush 400a, and a second positioning hole corresponding to the first positioning hole may be provided on the side surface of the eccentric recess 132a, and A cross pin shaft 700 passing through the first positioning hole and the second positioning hole is provided to fix the bush to the drive shaft. The shape of the cross pin shaft 700 may be a cylinder, a rectangular parallelepiped, or a truncated pyramid. In this way, the vertical pin shaft of an appropriate shape can be selected according to needs to provide appropriate fixation.
并且或可替代地，参见图15至图16，在衬套400b的外表面上可以设置有第一定位凹槽，在偏心凹部132b的侧表面上可以设置有与第一定位凹槽对 应的第二定位凹槽，并且设置有配合容纳于第一定位凹槽和第二定位凹槽中的竖销轴800。竖销轴800的形状可以为圆柱、长方体或锥棱台。如此，可以根据需要选择适当形状的竖销轴，以提供合适的固定。And or alternatively, referring to FIGS. 15 to 16, a first positioning groove may be provided on the outer surface of the bush 400b, and a first positioning groove corresponding to the first positioning groove may be provided on the side surface of the eccentric recess 132b There are two positioning grooves, and a vertical pin shaft 800 which is accommodated in the first positioning groove and the second positioning groove is provided. The shape of the vertical pin shaft 800 may be a cylinder, a rectangular parallelepiped, or a truncated pyramid. In this way, the vertical pin shaft of an appropriate shape can be selected according to needs to provide appropriate fixation.
此外，上述衬套400a、400b还可以通过螺栓固定连接至驱动轴130。有利地，上述衬套400a，400b的外表面可以与偏心凹部132a，132b的侧表面过盈、过渡或间隙配合。如此，可以根据需要选择适当配合方式，例如，在选择过盈配合的情况下，可以进一步确保衬套与偏心凹部的固定连接。In addition, the bushes 400a, 400b can also be fixedly connected to the drive shaft 130 by bolts. Advantageously, the outer surface of the aforementioned bushings 400a, 400b may be interference, transition, or clearance fit with the side surfaces of the eccentric recesses 132a, 132b. In this way, an appropriate fitting method can be selected as required, for example, in the case of selecting an interference fit, the fixed connection of the bush and the eccentric recess can be further ensured.
本领域的技术人员可以理解的是，在图3至图9中的实施方式所描述的涉及驱动轴承构造、配重(安装部和偏心加重部)的形状构造以及配重的分体构造等也可以应用于图10至图16中的实施方式中。Those skilled in the art can understand that the embodiments described in FIGS. 3 to 9 relate to the drive bearing structure, the shape structure of the weight (mounting portion and eccentric weighting portion), and the split structure of the weight, etc. It can be applied to the embodiments in FIGS. 10 to 16.
尽管在此已详细描述本公开的各种实施方式，但是应该理解本公开并不局限于这里详细描述和示出的具体实施方式，在不偏离本公开的实质和范围的情况下可由本领域的技术人员实现其它的变型和变体。所有这些变型和变体都落入本公开的范围内。而且，所有在此描述的构件都可以由其他技术性上等同的构件来代替。Although various embodiments of the present disclosure have been described in detail herein, it should be understood that the present disclosure is not limited to the specific embodiments described and shown in detail herein, and that it can be used in the field without departing from the spirit and scope of the present disclosure. The technician implements other variants and variants. All these variations and variants fall within the scope of the present disclosure. Moreover, all components described herein may be replaced by other technically equivalent components.

Claims (11)

  1. 一种涡旋压缩机(100)，包括：A scroll compressor (100), including:
    动涡旋(160)，所述动涡旋(160)包括柄部(163)；A movable vortex (160), the movable vortex (160) includes a handle (163);
    驱动轴(130)，所述驱动轴(130)包括偏心凹部(132，132a，132b)；A drive shaft (130), the drive shaft (130) includes an eccentric recess (132, 132a, 132b);
    衬套(400，400a，400b)，所述柄部(163)经由所述衬套(400，400a，400b)配合在所述偏心凹部(132，132a，132b)中使得所述动涡旋(160)被所述驱动轴(130)驱动，A bush (400, 400a, 400b), the handle (163) is fitted in the eccentric recess (132, 132a, 132b) via the bush (400, 400a, 400b) so that the movable vortex ( 160) Driven by the drive shaft (130),
    其中，所述涡旋压缩机(100)还包括配重(600)，所述配重(600)安装在所述衬套(400，400a，400b)上。Wherein, the scroll compressor (100) further includes a counterweight (600), and the counterweight (600) is installed on the bush (400, 400a, 400b).
  2. 如权利要求1所述的涡旋压缩机(100)，其中，所述衬套(400)能够相对于所述驱动轴(130)径向平移，在所述偏心凹部(132)的侧表面上设置有大致平坦的驱动表面(1331)，在所述衬套(400)的外表面上设置有与所述驱动表面(1331)滑动配合的大致平坦的受驱动表面(4001)。The scroll compressor (100) according to claim 1, wherein the bush (400) is capable of radial translation relative to the drive shaft (130) on the side surface of the eccentric recess (132) A substantially flat driving surface (1331) is provided, and on the outer surface of the bushing (400), a substantially flat driven surface (4001) slidingly fitted with the driving surface (1331) is provided.
  3. 如权利要求1所述的涡旋压缩机(100)，其中，所述衬套(400a，400b)固定连接至所述驱动轴(130)。The scroll compressor (100) according to claim 1, wherein the bush (400a, 400b) is fixedly connected to the drive shaft (130).
  4. 如权利要求3所述的涡旋压缩机(100)，其中：The scroll compressor (100) of claim 3, wherein:
    在所述衬套(400a)的外表面上设置有第一定位孔，在所述偏心凹部(132a)的侧表面上设置有与所述第一定位孔对应的第二定位孔，并且设置有穿过所述第一定位孔和所述第二定位孔的横销轴(700)；并且/或者A first positioning hole is provided on the outer surface of the bush (400a), a second positioning hole corresponding to the first positioning hole is provided on the side surface of the eccentric recess (132a), and a A cross pin shaft (700) passing through the first positioning hole and the second positioning hole; and / or
    在所述衬套(400b)的外表面上设置有第一定位凹槽，在所述偏心凹部(132b)的侧表面上设置有与所述第一定位凹槽对应的第二定位凹槽，并且设置有配合容纳于所述第一定位凹槽和所述第二定位凹槽中的竖销轴(800)。A first positioning groove is provided on the outer surface of the bush (400b), and a second positioning groove corresponding to the first positioning groove is provided on the side surface of the eccentric recess (132b), In addition, a vertical pin shaft (800) which is accommodated in the first positioning groove and the second positioning groove is provided.
  5. 如权利要求4所述的涡旋压缩机(100)，其中，所述横销轴(700)的形状为圆柱、长方体或锥棱台，所述竖销轴(800)的形状为圆柱、长方体或锥棱台。The scroll compressor (100) according to claim 4, wherein the shape of the horizontal pin shaft (700) is a cylinder, a rectangular parallelepiped or a truncated pyramid, and the shape of the vertical pin shaft (800) is a cylinder or a rectangular parallelepiped Or pyramid bevel.
  6. 如权利要求3所述的涡旋压缩机(100)，其中，所述衬套(400a，400b)通过螺栓固定连接至所述驱动轴(130)。The scroll compressor (100) according to claim 3, wherein the bush (400a, 400b) is fixedly connected to the drive shaft (130) by bolts.
  7. 如权利要求4至6中的任一项所述的涡旋压缩机(100)，其中，所述衬套(400a，400b)的外表面与所述偏心凹部(132a，132b)的侧表面过盈、过渡或间隙配合。The scroll compressor (100) according to any one of claims 4 to 6, wherein the outer surface of the bush (400a, 400b) passes over the side surface of the eccentric recess (132a, 132b) Surplus, transition or clearance fit.
  8. 如权利要求1至6中的任一项所述的涡旋压缩机(100)，其中，在所述衬套(400，400a，400b)与所述柄部(163)之间设置有筒状的驱动轴承(500)，所述驱动轴承(500)的内圆柱面与所述柄部(163)的外表面过盈配合，所述驱动轴承(500)的外圆柱面与所述衬套(400，400a，400b)的内表面间隙配合。The scroll compressor (100) according to any one of claims 1 to 6, wherein a cylindrical shape is provided between the bush (400, 400a, 400b) and the shank (163) Of the drive bearing (500), the inner cylindrical surface of the drive bearing (500) and the outer surface of the shank (163) are interference fit, the outer cylindrical surface of the drive bearing (500) and the bush ( 400, 400a, 400b) inner surface clearance fit.
  9. 如权利要求1至6中的任一项所述的涡旋压缩机(100)，其中，所述配重(600)包括安装部(601)和偏心加重部(602)，所述安装部(601)呈完全或部分圆环形并且安装至所述衬套(400，400a，400b)的与所述动涡旋(160)的端板相邻的端部，所述偏心加重部(602)从所述安装部(601)轴向地背离所述动涡旋(160)的端板延伸。The scroll compressor (100) according to any one of claims 1 to 6, wherein the counterweight (600) includes a mounting portion (601) and an eccentric weighting portion (602), the mounting portion ( 601) in a complete or partial circular ring shape and mounted to the end of the bush (400, 400a, 400b) adjacent to the end plate of the movable scroll (160), the eccentric weighted portion (602) An end plate extending axially away from the movable scroll (160) from the mounting portion (601).
  10. 如权利要求1至6中的任一项所述的涡旋压缩机(100)，其中，所述配重(600)包括安装部(601)和偏心加重部(602)，所述安装部呈完全或部分圆环形，所述偏心加重部(602)相对于所述安装部(601)轴向地延伸、径向地延伸或者轴向地且径向地延伸，以调节所述配重(600)的质心，使得所述配重(600)的离心力与所述偏心凹部(132，132a，132b)所提供的驱动力处于同一平面。The scroll compressor (100) according to any one of claims 1 to 6, wherein the counterweight (600) includes a mounting portion (601) and an eccentric weighting portion (602), the mounting portion is Fully or partially circular, the eccentric weighting portion (602) extends axially, radially, or axially and radially relative to the mounting portion (601) to adjust the weight ( The center of mass of 600) is such that the centrifugal force of the counterweight (600) is in the same plane as the driving force provided by the eccentric recess (132, 132a, 132b).
  11. 如权利要求1至6中的任一项所述的涡旋压缩机(100)，其中，所述配重(600)包括呈完全或部分圆环形的安装部(601)和从所述安装部(601)延伸的偏心加重部(602)，所述安装部(601)的轴向厚度设置为小于所述偏心加重部(602)的与所述安装部(601)邻接的部分的厚度。The scroll compressor (100) according to any one of claims 1 to 6, wherein the counterweight (600) includes a mounting portion (601) in a completely or partially toroidal shape and from the mounting The axial thickness of the mounting portion (601) is set to be smaller than the thickness of the portion of the eccentric weighting portion (602) adjacent to the mounting portion (601).
PCT/CN2019/112760 2018-10-23 2019-10-23 Scroll compressor WO2020083313A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN201821719557.0U CN208900360U (en) 2018-10-23 2018-10-23 Scroll compressor having a plurality of scroll members
CN201811238677.3 2018-10-23
CN201821719557.0 2018-10-23
CN201811238677.3A CN111089055A (en) 2018-10-23 2018-10-23 Scroll compressor having a plurality of scroll members

Publications (1)

Publication Number Publication Date
WO2020083313A1 true WO2020083313A1 (en) 2020-04-30

Family

ID=70331732

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2019/112760 WO2020083313A1 (en) 2018-10-23 2019-10-23 Scroll compressor

Country Status (1)

Country Link
WO (1) WO2020083313A1 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201202643Y (en) * 2008-05-17 2009-03-04 美的集团有限公司 Revolution vortex piece of vortex compressor
KR20090040151A (en) * 2007-10-19 2009-04-23 엘지전자 주식회사 Crankshaft and scroll compressor having this
CN203146326U (en) * 2012-04-11 2013-08-21 艾默生环境优化技术(苏州)有限公司 Scroll compressor having a plurality of scroll members
CN208900360U (en) * 2018-10-23 2019-05-24 艾默生环境优化技术(苏州)有限公司 Scroll compressor having a plurality of scroll members

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20090040151A (en) * 2007-10-19 2009-04-23 엘지전자 주식회사 Crankshaft and scroll compressor having this
CN201202643Y (en) * 2008-05-17 2009-03-04 美的集团有限公司 Revolution vortex piece of vortex compressor
CN203146326U (en) * 2012-04-11 2013-08-21 艾默生环境优化技术(苏州)有限公司 Scroll compressor having a plurality of scroll members
CN208900360U (en) * 2018-10-23 2019-05-24 艾默生环境优化技术(苏州)有限公司 Scroll compressor having a plurality of scroll members

Similar Documents

Publication Publication Date Title
US7070401B2 (en) Scroll machine with stepped sleeve guide
US7300265B2 (en) Flanged sleeve guide
CN209012065U (en) A counter weight subassembly and scroll compressor for scroll compressor
CN208900360U (en) Scroll compressor having a plurality of scroll members
JP4689050B2 (en) Scroll machine
JP4855788B2 (en) Reciprocating compressor
KR20140142046A (en) Scroll compressor
WO2020083313A1 (en) Scroll compressor
KR20140048823A (en) Rotary compressor
CN111089055A (en) Scroll compressor having a plurality of scroll members
CN217327670U (en) Bushing assembly and scroll compressor
CN220869651U (en) Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a
WO2021203636A1 (en) Scroll compressor
CN212389515U (en) Scroll compressor having a plurality of scroll members
CN212389516U (en) Scroll compressor having a plurality of scroll members
WO2022052297A1 (en) Scroll compressor
CN211288078U (en) Scroll compressor having a plurality of scroll members
WO2021203638A1 (en) Counterbalance assembly for scroll compressor, and scroll compressor
WO2020083312A1 (en) Counterweight, counterweight assembly and scroll compressor
JP2004218471A (en) Hermetic electric compressor
WO2013152705A1 (en) Scroll compressor
CN212360188U (en) Scroll compressor's counter weight subassembly and scroll compressor
US12006933B2 (en) Scroll compressor
JP4356375B2 (en) Compressor
CN113494450A (en) Scroll compressor having a plurality of scroll members

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: 19877292

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: 19877292

Country of ref document: EP

Kind code of ref document: A1