WO2022127768A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

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Publication number
WO2022127768A1
WO2022127768A1 PCT/CN2021/137743 CN2021137743W WO2022127768A1 WO 2022127768 A1 WO2022127768 A1 WO 2022127768A1 CN 2021137743 W CN2021137743 W CN 2021137743W WO 2022127768 A1 WO2022127768 A1 WO 2022127768A1
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WO
WIPO (PCT)
Prior art keywords
fixed scroll
scroll
sealing
region
scroll compressor
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PCT/CN2021/137743
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English (en)
French (fr)
Inventor
郭伟平
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艾默生环境优化技术(苏州)有限公司
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Priority claimed from CN202011477466.2A external-priority patent/CN114635855A/zh
Priority claimed from CN202023007464.5U external-priority patent/CN214196666U/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 WO2022127768A1 publication Critical patent/WO2022127768A1/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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids

Definitions

  • the present disclosure relates to scroll compressors, and more particularly, to scroll compressors with improvements in seal and discharge configurations.
  • Scroll compressors usually include a compression mechanism consisting of a fixed scroll and a movable scroll, and the fixed scroll can adopt a floating fixed scroll design, for example, through a fixed scroll and a casing or a main bearing seat for supporting the fixed scroll
  • axial flexibility and radial flexibility are provided for the fixed scroll, so as to provide the possibility of unloading for start-up with liquid and adjust the machining error.
  • a floating seal is provided, the floating seal is arranged in and cooperates with the annular recess of the fixed scroll.
  • a back pressure cavity is formed, and the annular recess (that is, the back pressure cavity) can communicate with the compression cavity (usually called the medium pressure cavity) in the middle of the scroll compression structure. Float under action.
  • the diaphragm divides the interior space of the scroll compressor into high pressure side and low pressure side, the upper surface of the floating seal and the diaphragm or the lower surface of the diaphragm seal attachment (such as a collar) contact and generate contact pressure, forming an end face Sealing effect to isolate the high pressure side from the low pressure side.
  • lip seals are respectively arranged on the inner and outer sides of the floating seal to contact and seal with the radially inner annular wall and the radially outer annular wall of the annular recess (back pressure chamber) respectively, so as to separate the back pressure chamber and the low pressure side. between the back pressure chamber and the high pressure side.
  • the area of the annular recess of the fixed scroll (between the radially inner sidewall and the radially outer sidewall of the annular recess) needs to be large enough, so that the pressure of the sealing assembly disposed in the annular recess is sufficient to float up Large enough to contact the diaphragm or the sealing attachment of the diaphragm to meet the axial sealing pressure, on the other hand, the high pressure chamber inside the radially inner sidewall of the annular recess (exhaust gas in fluid communication with the exhaust port of the compression mechanism) The area of the cavity) is set smaller to reduce the axial load.
  • An object of the present disclosure is to maximize the exhaust configuration space by abutting the sealing part of the sealing assembly against the fixed scroll to isolate the high pressure space from the low pressure area to eliminate the back pressure cavity and realize a scroll compressor with single-side sealing.
  • Another object of the present disclosure is to eliminate the defect that the seal assembly cannot be activated due to the inability of the seal assembly to rise in time, and reduce contact wear by fixing or integrally forming the seal assembly with the diaphragm or the seal attachment of the diaphragm instead of abutting contact sealing. scroll compressor.
  • the present disclosure provides a scroll compressor comprising: a casing defining a low pressure region at suction pressure within the casing; a compression mechanism disposed within the casing and including a fixed scroll and a A movable scroll, the fixed scroll includes a fixed scroll end plate, an exhaust port formed in the fixed scroll end plate, and a helical fixed scroll blade formed on one side of the fixed scroll end plate and a high-pressure space at the exhaust pressure formed on the other side of the fixed scroll end plate and communicating with the exhaust port; and a sealing assembly including a first sealing portion, the first sealing portion configured to abut the fixed scroll to isolate the high pressure space from the low pressure region.
  • the scroll compressor includes a partition dividing the interior space within the housing into a first region and a second region, the first region including the low pressure region and containing the compression a mechanism, the second region receives compressed high pressure working fluid from the high pressure space, the diaphragm is provided with an orifice, and the seal assembly includes a seal for isolating the high pressure space from the low pressure region A second sealing portion configured to abut against the baffle or an attachment attached to the baffle at the aperture.
  • the sealing assembly includes a top plate and a bottom plate, the first sealing portion includes a connecting portion interposed between the top plate and the bottom plate and a lip portion abutting against the fixed scroll, and the The second sealing portion is formed at the top plate.
  • the scroll compressor further comprises an activation spring adapted to urge the seal assembly towards the diaphragm.
  • the scroll compressor includes a partition dividing the interior space within the housing into a first region and a second region, the first region including the low pressure region and containing the compression a mechanism, the second region receives compressed high pressure working fluid from the high pressure space, the diaphragm is provided with an orifice at which an attachment is attached, and the seal assembly includes a top plate , the top plate is fixed to or integral with the attachment.
  • the sealing assembly includes a bottom plate attached to the top plate, and the first sealing portion includes a connecting portion interposed between the top plate and the bottom plate and abutting against the fixed The lip portion of the vortex.
  • the fixed scroll includes a hub that partially defines the high-pressure space, and the first sealing portion abuts against the radially inner sidewall of the hub, or the first sealing portion and the The radially outer side walls of the hub portion are in contact with each other.
  • the fixed scroll includes a fixed scroll body and a fixed scroll cover
  • the fixed scroll body includes the fixed scroll end plate
  • the fixed scroll cover is attached to the fixed scroll an end plate
  • the hub portion is formed at the fixed scroll cover plate.
  • the first sealing portion abuts the radially outer sidewall of the hub portion
  • the seal assembly includes an extension extending radially inwardly beyond the radially inner sidewall of the hub portion, and preferably, The second sealing portion is formed at the extending portion.
  • variable volume ratio valve is provided in the high pressure space.
  • the present disclosure provides an improved seal and discharge design: 1) By abutting the seal portion of the seal assembly against the fixed scroll to isolate the high pressure space from the low pressure area, while allowing certain When the scroll is axially floating, the back pressure chamber is eliminated, which maximizes the space for the exhaust structure, thereby improving the design freedom of the exhaust hole arrangement and the exhaust valve assembly, realizing the scroll compressor and
  • the system using the scroll compressor maintains high energy efficiency in a wider operating range, simplifies the sealing structure and thus the structure of the fixed scroll; due to the elimination of the back pressure cavity, a single-sided (radial) seal can be achieved, reducing the number of seals
  • the number of parts is increased; the starting elastic member is increased to ensure the top (axial) sealing of the sealing assembly at the moment of starting the compressor, so as to prevent the high-pressure side fluid from leaking to the low-pressure side at the moment of starting.
  • the sealing assembly is provided on the hub of the cover plate, so that the size of the sealing assembly is reduced. 3) Fixing or integrally forming the seal assembly with the diaphragm or the seal attachment of the diaphragm to replace the (axial) abutment contact seal, eliminating the activation elastic member, so that there is no prior art e.g. in low temperature conditions Because the sealing components cannot float up in time (for example, PTFE seals should not deform and get stuck at low temperatures, or, low suction pressure and low medium pressure chamber pressure or back pressure chamber pressure at low ambient temperature) cause the high pressure side and the back pressure chamber pressure. The defect that the low pressure side is turned on and cannot work, and at the same time, there is no wear caused by the end face of the seal assembly contacting the seal (such as micro displacement under the action of fluid pulsation), which reduces the number of parts and costs.
  • FIG. 1 is a schematic cross-sectional view of a scroll compressor including a seal assembly and a fixed scroll according to an aspect of an embodiment of the present disclosure.
  • FIG. 2 is an enlarged schematic cross-sectional view of a seal assembly and a fixed scroll of the scroll compressor of FIG. 1 .
  • FIG. 3 is an exploded perspective view of a seal assembly and a fixed scroll of the scroll compressor of FIG. 1 .
  • FIG. 4 is a schematic cross-sectional view of a scroll compressor including a seal assembly disposed on a hub of a cover plate of a fixed scroll according to another aspect of an embodiment of the present disclosure.
  • FIG. 5 is an exploded perspective view of a seal assembly and a fixed scroll of the scroll compressor of FIG. 4 .
  • FIG. 6 is a schematic cross-sectional view of a scroll compressor including a seal assembly according to yet another aspect of an embodiment of the present disclosure.
  • FIG. 7 is a variation of the scroll compressor of FIG. 4 including a seal assembly, the top plate of the seal assembly and the attachment of the diaphragm are integrally formed.
  • FIG. 8 is a variation of the scroll compressor of FIG. 1 including a seal assembly, the top plate of the seal assembly and the attachment of the diaphragm are integrally formed.
  • FIG. 9 is a schematic cross-sectional view of a related art scroll compressor including a seal assembly and a fixed scroll disposed within an annular recess.
  • FIG. 10 is an enlarged schematic cross-sectional view of the seal assembly configuration and fixed scroll of the scroll compressor of FIG. 9 .
  • a scroll compressor (also sometimes referred to hereinafter as a compressor) generally includes a housing 110 .
  • the casing 110 may include a substantially cylindrical body 111, a top cover 112 provided at one end of the body 111, a bottom cover 114 provided at the other end of the body 111, and a top cover 112 and the body 111 to connect the inside of the compressor.
  • the space is divided into high pressure side and low pressure side partitions 116 .
  • the space between the partition plate 116 and the top cover 112 constitutes the high pressure side
  • the space between the partition plate 116, the body 111 and the bottom cover 114 constitutes the low pressure side.
  • An intake port (not shown) for sucking fluid is provided on the low pressure side, and an exhaust port 119 for discharging the compressed fluid is provided on the high pressure side.
  • a motor 120 including a stator 122 and a rotor 124 is provided in the housing 110 .
  • a drive shaft 130 is provided in the rotor 124 to drive the compression mechanism composed of the fixed scroll 150 and the movable scroll 160 .
  • the orbiting scroll 160 includes an end plate 164, a hub 162 formed on one side of the end plate, and helical vanes 166 formed on the other side of the end plate.
  • the fixed scroll 150 includes an end plate 154, helical vanes 156 formed on one side of the end plate, and an annular recess 158 formed on the other side of the end plate, the annular recess including a radially outer sidewall and a radially inner sidewall.
  • An exhaust port 159 is formed at a substantially central position of the end plate. The space around the exhaust port 159 also constitutes the high pressure side.
  • a series of compression cavities C1 , C2 and C3 whose volumes gradually decrease from the radially outer side to the radially inner side are formed between the helical blades 156 of the fixed scroll 150 and the helical blades 166 of the movable scroll 160 .
  • the radially outermost compression chamber C1 is at the suction pressure
  • the radially innermost compression chamber C3 is at the exhaust pressure
  • the middle compression chamber C2 is located between the suction pressure and the discharge pressure, and is thus also referred to as the middle pressure chamber.
  • One side of the movable scroll 160 is supported by the upper portion (ie, the support portion) of the main bearing seat 140 , and one end of the drive shaft 130 is supported by the main bearing provided in the main bearing seat 140 .
  • One end of the drive shaft 130 is provided with an eccentric crank pin 132 , and an unloading bushing is provided between the eccentric crank pin 132 and the hub portion 162 of the movable scroll 160 .
  • the orbiting scroll 160 will rotate relative to the fixed scroll 150 in translation (ie, the central axis of the orbiting scroll 160 rotates around the central axis of the fixed scroll 150, but the orbiting scroll 160 itself does not rotate around itself Rotation of the central axis) to achieve fluid compression.
  • the above-mentioned translational rotation is realized by an Oldham slip ring disposed 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 159 .
  • a one-way valve or an exhaust valve 190 may be provided at the exhaust port 159, and the valve may be a variable volume ratio valve, for example, it may be Exhaust in advance for some low compression ratio working conditions where the ratio of discharge pressure to suction pressure is relatively low, so as to avoid the loss of power consumption caused by over-compression of the refrigerant, so that the scroll compressor can maintain a high level in a wider operating range. efficiency.
  • the fixed scroll 150 is provided with a positioning hole 151
  • the main bearing seat 140 is provided with a bolt 141 for passing through the positioning hole 151
  • the positioning hole 151 and the bolt 141 are configured to form an axial gap and a radial gap therebetween, so that Provides axial and radial flexibility for the fixed scroll (relative to the main bearing housing).
  • a seal assembly S is provided in the annular recess 158 of the fixed scroll 150 . That is, the seal assembly S is provided between the separator 116 and the fixed scroll 150 .
  • the annular recess 158 is in fluid communication with one of the series of compression chambers C1 , C2 , C3 via a through hole 155 (also referred to as a medium pressure passage) formed in the fixed scroll end plate 154 .
  • the annular recess 158 is in fluid communication with the intermediate compression chamber C2 via the through hole 155 . Therefore, the sealing assembly S cooperates with the annular recess 158 to form a back pressure chamber BC that provides back pressure for the orbiting scroll 150 .
  • the axial displacement of the seal assembly S is limited by the diaphragm 116 .
  • the pressure in each compression chamber exceeds the set value, the resultant force generated by the pressures in these compression chambers will exceed the down pressure provided in the back pressure chamber BC so that the fixed scroll 150 moves upward.
  • the fluid in the compression chamber will pass through the gap between the top end of the helical blade 156 of the fixed scroll 150 and the end plate 164 of the movable scroll 160 and the gap between the top of the helical blade 166 of the movable scroll 160 and the fixed scroll 150
  • the gap between the end plates 154 leaks to the low pressure side for unloading, thereby providing axial flexibility to the scroll compressor. Therefore, the seal assembly is axially floating under the action of the compression chamber fluid from the medium pressure passage to match the axial floating of the fixed scroll.
  • the sealing assembly S may include an upper plate S1 , a lower plate S2 , and a first sealing member S3 and a third sealing member S5 disposed between the upper plate S1 and the lower plate S2 .
  • the shape of the seal assembly S substantially corresponds to the shape of the annular recess 158 (back pressure chamber BC), so that the first seal S3 can seal against the radially inner sidewall of the annular recess 158, and the third seal S5 can abut the annular The radially outer side wall of the recess 158 achieves sealing.
  • the upper end of the upper plate S1 may be sealed against the partition plate 116 or the collar 117 provided on the partition plate 116 .
  • the sealing assembly S achieves the following sealing in the compressor: 1) the upper end of the upper plate S1 abuts against the collar 117 on the partition plate 116 to realize the separation of the high pressure side and the low pressure side; 2) the first seal S3 abuts against the collar 117 on the partition plate 116 3) The third seal S5 abuts against the radially outer side wall of the annular recess 158 to realize the separation between the back pressure chamber BC and the low pressure side open.
  • the above-mentioned back pressure chamber for the floating seal needs to be provided with an annular concave portion on the top plate of the fixed scroll, and a back pressure chamber is formed between the radially inner sidewall and the radially outer sidewall of the annular recessed portion.
  • the area of the annular recess (back pressure cavity) needs to be large enough to ensure sufficient axial sealing pressure between the upper end of the sealing assembly (upper plate) and the diaphragm or the collar of the diaphragm
  • the area of the high pressure chamber (exhaust chamber) inside the radially inner sidewall is usually set smaller to reduce the axial load.
  • the exhaust holes are usually arranged as a plurality of exhaust holes arranged in the radial direction to be suitable for a plurality of compression ratios, while considering the arrangement of the exhaust valve assembly to cooperate with the exhaust holes, which requires a large space Therefore, the arrangement of the prior art will result in the exhaust valve assembly and the exhaust hole disposed in the radially inner side wall being limited to a small area, reducing the design freedom of the exhaust assembly and failing to satisfy a wider range of compression
  • the demand for a range of ratios results in particularly low energy efficiency of compressors at low compression ratios.
  • the present disclosure provides a compressor with an improved seal assembly and discharge configuration, and the seal assembly and discharge configuration are described in conjunction with FIGS. 1-8 .
  • the scroll compressor 100 includes: a casing 110 defining a low pressure region LR at suction pressure within the casing; a compression mechanism CM provided in the casing
  • the fixed scroll 150 includes a fixed scroll end plate 154, an exhaust port 159 formed in the fixed scroll end plate, and a fixed scroll end plate 159 formed on one side of the fixed scroll end plate.
  • the sealing assembly may include a first sealing portion S140, The first seal portion is configured to abut against the fixed scroll to isolate the high pressure space from the low pressure region.
  • a one-way valve or exhaust valve which may be a variable volume ratio valve 190 , is provided in the high pressure space DC.
  • the back pressure chamber is eliminated, so that the high pressure space for the exhaust structure is maximized, and the exhaust hole is improved.
  • Design freedom for layout and exhaust valve assemblies In particular, the high-pressure space can expand radially outward, thereby allowing the variable volume ratio exhaust valve and thus the variable volume ratio orifice to be disposed radially outward, which realizes the scroll compressor and the system using the scroll compressor in the Maintain high energy efficiency over a wider operating range.
  • the scroll compressor may include a partition 116 that divides the interior space within the housing into a first region and a second region, the first region may include the low pressure region LR and house the compression mechanism, and the second region receives The compressed high pressure working fluid of the high pressure space DC.
  • the sealing assembly S100 may include a second sealing portion S142 adapted to abut against the attachment S120 attached to the diaphragm 116 in an operating state, and of course, the second sealing portion may also be configured to be adapted to abut on the partition.
  • the seal assembly S100 may include a top plate S110 and a bottom plate S130, and as shown, the first sealing portion S140 may advantageously include a connecting portion (not shown) interposed between the top plate and the bottom plate and a lip abutting against the fixed scroll Also, a second sealing portion S142 is formed at the top plate S110.
  • the lip portion can be implemented as a flexible sealing lip that allows a certain flexibility of the fixed scroll in the axial and radial directions, for adjusting the space, for compensating for manufacturing tolerances and for liquid conditions, etc. unloading, and the double-plate structure allows the first seal to be securely and easily secured.
  • those skilled in the art can think of other ways to achieve the sealing between the first sealing portion and the fixed scroll, for example, arranging an annular sealing ring between the first sealing portion and the fixed scroll.
  • the scroll compressor also includes an activation spring S150 adapted to urge the seal assembly S100 towards the diaphragm 116 .
  • the activation spring S150 can urge the top plate S110 and the bottom plate S130 of the seal assembly S100 toward the partition plate 116 .
  • the baffle 116 is provided with an orifice at which an attachment S120 is attached, which is an interference fit with the orifice and can be used as a sound dampening seal to dampen the exhaust gas.
  • an attachment S120 is attached to the baffle 116.
  • the top plate S110 of the sealing assembly S100 the top plate being fixed to or integral with the attachment.
  • the top plate can also be fixed to the attachment.
  • Fixing or integrally forming the seal assembly with the diaphragm or diaphragm attachments to replace (axial) abutment contact seals (particularly in metal-to-metal abutment contact seals) eliminates the actuation elastic member so that there is no existing
  • the sealing component cannot float in time (for example, the PTFE seal should not be deformed and stuck at low temperature, or, under low ambient temperature, low suction pressure and low medium pressure chamber pressure)
  • the defect that causes the high-pressure side and the low-pressure side to be turned on and cannot work, and there is no wear caused by the end face of the seal assembly contacting the seal for example, micro-dislocation under the action of fluid pulsation), which reduces the number of parts and costs.
  • the fixed scroll may include a hub portion 181 that partially defines the high pressure space DC, and the first seal portion S140 may abut a radially inner sidewall of the hub portion 181 (as shown in FIGS. 2 and 8 ), or , the first sealing portion S140 may be in contact with the radially outer sidewall of the hub portion 181 (as shown in FIG. 6 ).
  • the first sealing part S140 may be provided as a single sealing part to simplify the structure of the sealing assembly.
  • the fixed scroll 150 may include a fixed scroll body and a fixed scroll cover plate 170
  • the fixed scroll body may include a fixed scroll end plate 154
  • the fixed scroll cover plate 170 is attached to the fixed scroll
  • the rotating end plate 154 and the hub 171 are formed at the fixed scroll cover plate 170 .
  • the fixed scroll cover plate allows the seal assembly to be attached to the fixed scroll cover plate without being attached to the fixed scroll body, thereby allowing the fixed scroll body to be connected to the fixed scroll cover plate.
  • a high-pressure space with a larger volume that is more suitable for installing various valves is formed therebetween.
  • the sealing assembly is arranged on the hub portion of the cover plate, so that the size of the sealing assembly can be reduced and the cost can be reduced.
  • the seal assembly S100 may include a single first seal portion abutting the radially outer sidewall of the hub portion 181 , the single first seal portion in FIG. 6 is provided on the fixed scroll (not present On the hub portion 181 of the cover plate), the seal assembly S100 may include an extension portion S141 extending radially inward beyond the radially outer sidewall of the hub portion 181 , in other words, the inner diameter dimension D1 of the extension portion is smaller than that of the hub portion 181 The outer diameter dimension D2. More preferably, the extending portion S141 may extend beyond the radially inner sidewall of the hub portion 181 . Similarly, in FIG.
  • the sealing assembly S100 may also include an extension portion S141 extending radially inward beyond the radially outer sidewall of the hub portion 171 , namely , the inner diameter dimension D3 of the extension portion is smaller than the outer diameter dimension D4 of the hub portion 171 . More preferably, the extending portion S141 may extend beyond the radially inner sidewall of the hub portion 171 .
  • the extension allows a high pressure pressurized portion to be formed below it, thereby using the high pressure in the high pressure region to push the seal assembly upwards during operation of the compressor.
  • the second sealing part S142 may be formed at the extension part S141.

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

Abstract

一种涡旋压缩机(100)，包括：壳体(110)，在壳体内限定有处于吸气压力的低压区域(LR)；压缩机构(CM)，压缩机构设置在壳体内并且包括定涡旋(150)和动涡旋(160)，定涡旋包括定涡旋端板(154)、形成在定涡旋端板中的排气口(159)、形成在定涡旋端板一侧的螺旋状的定涡旋叶片(156)以及形成在定涡旋端板另一侧的与排气口连通的处于排气压力的高压空间(DC)；以及密封组件(S100)，密封组件包括第一密封部(S140)，第一密封部构造成抵接于定涡旋以将高压空间与低压区域隔绝。提供了不设置背压腔使得排气构造空间最大化、实现单侧密封的涡旋压缩机。

Description

涡旋压缩机
本申请要求于2020年12月15日提交中国国家知识产权局、申请号为202011477466.2、名称为“涡旋压缩机”的中国专利申请的优先权以及要求于2020年12月15日提交中国国家知识产权局、申请号为202023007464.5、名称为“涡旋压缩机”的中国专利申请的优先权，这些申请的全部内容通过引用结合在本申请中。
技术领域
本公开涉及涡旋压缩机，特别是，涉及密封和排气构造方面做出改进的涡旋压缩机。
背景技术
涡旋压缩机通常包括由定涡旋和动涡旋构成的压缩机构，定涡旋可以采用浮动定涡旋设计，例如，通过定涡旋与用于支撑定涡旋的壳体或主轴承座借助于定位孔和螺栓配合间隙构造，以为定涡旋提供轴向柔性和径向柔性，从而为带液启动提供卸载可能以及调整加工误差。
进一步地，为了将涡旋压缩机的高压侧和低压侧隔绝并且配合定涡旋的轴向浮动提供了浮动密封件，该浮动密封件设置在定涡旋的环形凹部内并且与该环形凹部配合形成背压腔，环形凹部(即背压腔)可以与涡旋压缩结构的中间的压缩腔(通常称为中压腔)连通，因此，该浮动密封件在背压腔的流体中压压力的作用下浮动。隔板将涡旋压缩机的内部空间分隔成高压侧和低压侧，浮动密封件的上表面和隔板或隔板密封附接件(例如套环)的下表面接触并产生接触压力，形成端面密封效果，以将高压侧与低压侧隔绝。并且，在浮动密封件的内外侧分别设置唇形密封件，以分别与环形凹部(背压腔)的径向内环形壁和径向外侧环形壁接触密封，从而将背压腔与低压侧之间、背压腔与高压侧之间隔绝。
在上述构造中，一方面，定涡旋的环形凹部(环形凹部的径向内侧壁与径向外侧壁之间)的面积需要足够大，进而使设置在环形凹部内的密封组件上浮的压力足够大以接触隔板或隔板的密封附接件，以满足轴向密封压力，另一方面，环形凹部的径向内侧壁的内部的高压腔(与压缩机构的排气口流体连通的排气腔)的面积设置较小以减小轴向载荷。然而，该构 造导致设置在径向内侧壁内的排气组件受限于小的面积，降低了排气组件(排气孔和排气阀)的设计自由度，而无法满足更广泛的压缩比(特别是低压缩比)范围的需求。
发明内容
本公开的一个目的是通过将密封组件的密封部抵接于定涡旋以将高压空间与低压区域隔绝以取消背压腔使得排气构造空间最大化、实现单侧密封的涡旋压缩机。
本公开的另一个目的是通过将密封组件与隔板或隔板的密封附接件固定或一体形成以替代抵接接触密封使得消除由于密封组件不能及时上浮而不能启动的缺陷、减少接触磨损的涡旋压缩机。
本公开提供了一种涡旋压缩机，包括：壳体，在所述壳体内限定有处于吸气压力的低压区域；压缩机构，所述压缩机构设置在所述壳体内并且包括定涡旋和动涡旋，所述定涡旋包括定涡旋端板、形成在所述定涡旋端板中的排气口、形成在所述定涡旋端板一侧的螺旋状的定涡旋叶片以及形成在所述定涡旋端板另一侧的与所述排气口连通的处于排气压力的高压空间；以及密封组件，所述密封组件包括第一密封部，所述第一密封部构造成抵接于所述定涡旋以将所述高压空间与所述低压区域隔绝。
有利地，所述涡旋压缩机包括隔板，所述隔板将所述壳体内的内部空间分隔成第一区域和第二区域，所述第一区域包括所述低压区域并且容纳所述压缩机构，所述第二区域接纳来自所述高压空间的经过压缩的高压工作流体，所述隔板设置有孔口，以及所述密封组件包括用于将所述高压空间与所述低压区域隔绝的第二密封部，所述第二密封部构造成适于抵接于所述隔板或者抵接于附接至所述隔板的所述孔口处的附接件。
有利地，所述密封组件包括顶板和底板，所述第一密封部包括插置在所述顶板与所述底板之间的连接部和抵接于所述定涡旋的唇缘部，以及所述第二密封部形成在所述顶板处。
有利地，所述涡旋压缩机还包括适于将所述密封组件朝向所述隔板推压的启动弹簧。
有利地，所述涡旋压缩机包括隔板，所述隔板将所述壳体内的内部空间分 隔成第一区域和第二区域，所述第一区域包括所述低压区域并且容纳所述压缩机构，所述第二区域接纳来自所述高压空间的经过压缩的高压工作流体，所述隔板设置有孔口，在所述孔口处附接有附接件，以及所述密封组件包括顶板，所述顶板固定至所述附接件或者与所述附接件成一体。
有利地，所述密封组件包括底板，所述底板附接至所述顶板，以及所述第一密封部包括插置在所述顶板与所述底板之间的连接部和抵接于所述定涡旋的唇缘部。
有利地，所述定涡旋包括部分地限定所述高压空间的毂部，以及所述第一密封部与所述毂部的径向内侧壁抵接，或者，所述第一密封部与所述毂部的径向外侧壁抵接。
有利地，所述定涡旋包括定涡旋本体和定涡旋盖板，所述定涡旋本体包括所述定涡旋端板，所述定涡旋盖板附接至所述定涡旋端板，所述毂部形成在所述定涡旋盖板处。
有利地，所述第一密封部与所述毂部的径向外侧壁抵接，所述密封组件包括径向向内延伸超过所述毂部的径向内侧壁的延伸部，并且优选地，所述第二密封部形成在所述延伸部处。
有利地，在所述高压空间中设置有可变容积比阀。
与现有的涡旋压缩机相比，本公开提供了改进的密封和排气设计：1)通过将密封组件的密封部抵接于定涡旋以将高压空间与低压区域隔绝，在允许定涡旋轴向浮动的情况下，取消了背压腔，使得用于排气构造的空间最大化，从而提高了排气孔布置和排气阀组件的设计自由度，实现了涡旋压缩机以及应用涡旋压缩机的系统在更广的运行范围内保持高能效，简化了密封结构并且进而简化了定涡旋的结构；由于取消背压腔可以实现单侧(径向)密封，减少了密封件的数量；增加了启动弹性构件以在压缩机启动瞬间保证密封组件顶端(轴向)密封，以防止高压侧流体启动瞬间泄漏到低压侧。2)将密封组件设置在盖板的毂部上，使得减小密封组件的尺寸。3)将密封组件与隔板或隔板的密封附接件固定或一体形成以替代(轴向)抵接接触密封，取消了启动弹性构件，使得不存在现有技术的例如在低温工况下由于密封组件不能及时上浮(例如，PTFE密封件在低温时不宜变形而卡住，或者，低的环境温度下低的吸气压力和低的中压腔压力即背压腔压力)导 致高压侧和低压侧导通而不能工作的缺陷，同时也不存在密封组件的端面接触密封(例如在流体脉动的作用下微小错动)导致的磨损，减少了部件数量，降低了成本。
附图说明
通过以下参照附图而提供的对具体实施例的详细描述，将能够更加容易地理解本公开的特征和优点。附图中，相同的特征或部件采用相同的附图标记来表示且附图不一定按比例绘制，并且附图中：
图1是根据本公开的实施方式的一个方面的包括密封组件和定涡旋的涡旋压缩机的示意性剖视图。
图2是图1的涡旋压缩机的密封组件和定涡旋的放大示意性剖视图。
图3是图1的涡旋压缩机的密封组件和定涡旋的分解立体图。
图4是根据本公开的实施方式的另一方面的包括密封组件的涡旋压缩机的示意性剖视图，密封组件设置在定涡旋的盖板的毂部上。
图5是图4的涡旋压缩机的密封组件和定涡旋的分解立体图。
图6是根据本公开的实施方式的再一个方面的包括密封组件的涡旋压缩机的示意性剖视图。
图7是图4的包括密封组件的涡旋压缩机的变型，密封组件的顶板和隔板的附接件一体形成。
图8是图1的包括密封组件的涡旋压缩机的变型，密封组件的顶板和隔板的附接件一体形成。
图9是相关技术的包括设置在环形凹部内的密封组件和定涡旋的涡旋压缩机的示意性剖视图。
图10是图9的涡旋压缩机的密封组件构造和定涡旋的放大示意性剖视图。
具体实施方式
下面对本公开各种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。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。
首先将参照图9和图10描述涡旋压缩机的总体构造和运行原理。涡旋压缩机(下文中有时也会称为压缩机)一般包括壳体110。壳体110可以包括大致圆筒形的本体111、设置在本体111一端的顶盖112、设置在本体111另一端的底盖114以及设置在顶盖112和本体111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之间的空间构成高压侧，而隔板116、本体111和底盖114之间的空间构成低压侧。在低压侧设置有用于吸入流体的进气接头(未示出)，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构成的马达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和形成在端板另一侧的环形凹部158，该环形凹部包括径向外侧壁和径向内侧壁。在端板的大致中央位置处形成有排气口159。排气口159周围的空间也构成高压侧。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在从径向外侧向径向内侧逐渐减小的压缩腔C1、C2和C3。其中，径向最外侧的压缩腔C1处于吸气压力，径向最内侧的压缩腔C3处于排气压力。中间的压缩腔C2处于吸气压力和排气压力之间，从而也被称之为中压腔。
动涡旋160的一侧由主轴承座140的上部(即支撑部)支撑，驱动轴130的一端由设置在主轴承座140中的主轴承支撑。驱动轴130的一端设置有偏心曲柄销132，在偏心曲柄销132和动涡旋160的毂部162之间设置有卸载衬套。通过马达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的中心轴线旋转，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159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159回流到低压侧，可以在排气口159处设置单向阀或排气阀190，该阀可以是可变容积比阀，例如可以在对一些排气压力和吸气压力比比较低的低压缩比的工况进行提前排气，以免对制冷剂过压缩造成功耗的损失，使得涡旋压缩机在更广的运行范围内保持高能效。
定涡旋150设置有定位孔151，主轴承座140上设置有用于穿过定位孔151的螺栓141，该定位孔151和螺栓141构造成在它们之间形成轴向间隙和径向间隙，使得为定涡旋(相对于主轴承座)提供轴向柔性和径向柔性。
通常，在定涡旋150的环形凹部158中设置有密封组件S。即，密封组件S设置在隔板116和定涡旋150之间。环形凹部158经由形成在定涡旋端板154中的通孔155(也称之为中压通道)与一系列压缩腔C1、C2、C3中的一个流体连通。优选地，环形凹部158经由通孔155与中间的压缩腔C2流体连通。从而密封组件S与环形凹部158一起配合形成为动涡旋150提供背压的背压腔BC。密封组件S的轴向位移受到隔板116的限制。当各个压缩腔中的压力超过设定值时，这些压缩腔中的压力所产生的合力将超过背压腔BC中提供的下压力从而使得定涡旋150向上运动。此时，压缩腔中的流体将通过定涡旋150的螺旋叶片156的顶端与动涡旋160的端板164之间的间隙以及动涡旋160的螺旋叶片166的顶端与定涡旋150的端板154之间的间隙泄漏到低压侧以实现卸载，从而为涡旋压缩机提供了轴向柔性。因此，密封组件在来自中压通道的压缩腔流体的作用下轴向浮动以配合定涡旋的轴向浮动。
下面将更详细地描述密封组件S的构造和功能。如图10所示，密封组件S可以包括上板S1、下板S2和设置在上板S1与下板S2之间的第一密封件S3和第三密封件S5。密封组件S的形状与环形凹部158(背压腔BC)的形状基本对应，从而第一密封件S3可以抵靠环形凹部158的径向内侧壁实现密封，而第三密封件S5可以抵靠环形凹部158的径向外侧壁实现密封。此外，上板S1的上端可以抵靠隔板116或设置在隔板116上的套环117实现密封。
密封组件S在压缩机中实现了如下方式的密封：1)上板S1的上端抵靠隔板116上的套环117以实现高压侧和低压侧的隔开；2)第一密封件S3抵靠环形凹部158的径向内侧壁以实现高压侧与背压腔BC的隔开；3)第三密封件S5抵靠环形凹部158的径向外侧壁以实现背压腔BC与低压侧的隔开。
上述用于浮动密封件的背压腔需要在定涡旋的顶板上设置环形凹部，在环形凹部的径向内侧壁与径向外侧壁之间形成背压腔。根据该背压腔构造，一方面，环形凹部(背压腔)的面积需要足够大以保证密封组件(上板)的上端与隔板或隔板的套环之间具有足够的轴向密封压力；另一方面，径向内侧壁的内部的高压腔(排气腔)的面积通常设置较小以减小轴向载荷。然而，例如，排气孔通常布置成沿径向方向布置的多个排气孔以适用于多个压缩比，同时考虑与排气孔配合的排气阀组件的设置，这需要较大的空间，因此，现有技术的布置会导致设置在径向内侧壁内的排气阀组件和排气孔受限于小的面积，降低了排气组件的设计自由度，而无法满足更广泛的压缩比(特别是低压缩比)范围的需求，特别地导致压缩机在低压缩比工况下能效很低。
有鉴于此，本公开提供了一种具有改进的密封组件和排气构造的压缩机，并且结合图1至图8对密封组件和排气构造进行描述。
参见图1至图3，并且结合图9至图10，涡旋压缩机100，包括：壳体110，在壳体内限定有处于吸气压力的低压区域LR；压缩机构CM，压缩机构设置在壳体110内并且包括定涡旋150和动涡旋，定涡旋150包括定涡旋端板154、形成在定涡旋端板中的排气口159、形成在定涡旋端板一侧的螺旋状的定涡旋叶片156以及形成在定涡旋端板另一侧的与排气口连通的处于排气压力的高压空间DC；以及密封组件S100，密封组件可以包括第一密封部S140，第一密封部构造成抵接于定涡旋以将高压空间与低压区域隔绝。在高压空间DC中设置有单向阀或排气阀，该阀可以是可变容积比阀190。
借助于上述，使得允许定涡旋轴向浮动和满足高压侧与低压侧之间密封的情况下，取消了背压腔，使得用于排气构造的高压空间最大化，从而提高了排气孔布置和排气阀组件的设计自由度。特别地，高压空间可以沿径向向外扩展，从而允许可变容积比排气阀进而可变容积比孔口径向向外设置，这实现了涡旋 压缩机以及应用涡旋压缩机的系统在更广的运行范围内保持高能效。此外，由于取消背压腔可以实现单侧(径向)密封，减少了密封件的数量，并且定涡旋无需设置内外双毂部，这简化了密封组件的结构进而简化了定涡旋的结构。
具体地，涡旋压缩机可以包括隔板116，该隔板将壳体内的内部空间分隔成第一区域和第二区域，第一区域可以包括低压区域LR并且容纳压缩机构，第二区域接纳来自高压空间DC的经过压缩的高压工作流体。密封组件S100可以包括第二密封部S142，第二密封部适于在工作状态下抵接于附接至隔板116的附接件S120，当然，第二密封部也可以构造成适于抵接于隔板。密封组件S100可以包括顶板S110和底板S130，如图示，第一密封部S140有利地可以包括插置在顶板与底板之间的连接部(未示出)和抵接于定涡旋的唇缘部并且，第二密封部S142形成在顶板S110处。该唇缘部可以实施为柔性密封唇缘，该柔性密封唇缘允许定涡旋在轴向和径向上有一定柔性，用于调节空间，用于补偿制造误差和用于带液工况等的卸载，并且双板结构允许可靠及方便地固定第一密封部。当然，本领域技术人员可以想到其他方式实现第一密封部与定涡旋的密封，例如，在第一密封部与定涡旋之间设置环形密封圈等。
为了在压缩机启动瞬间保证密封组件顶端(轴向)密封，可以设置启动弹性构件，以防止高压侧流体启动瞬间泄漏到低压侧，使得压缩机能够正常启动。在附图中，涡旋压缩机还包括适于将密封组件S100朝向隔板116推压的启动弹簧S150。在实施方式的一个方面，该启动弹簧S150可以将密封组件S100的顶板S110和底板S130朝向隔板116推压。
隔板116设置有孔口，在孔口处附接有附接件S120，该附接件与孔口过盈配合并且可以用作对排气进行消音的消音密封件。有利地，如图7和图8所示，密封组件S100的顶板S110，顶板固定至附接件或者与附接件成一体。当然，顶板也可以固定至附接件。将密封组件与隔板或隔板的附接件固定或一体形成以替代(轴向)抵接接触密封(特别在金属对金属的抵接接触密封)，取消了启动弹性构件，使得不存在现有技术的例如在低温工况下由于密封组件不能及时上浮(例如，PTFE密封件在低温时不宜变形而卡住，或者，低的环境温度下低的吸气压力和低的中压腔压力)导致高压侧和低压侧导通而不能工作的缺陷，同时也不存在密封组件的端面接触密封(例如在流体脉动的作用下微小错动)导致的磨损，减少了部件数量，降低了成本。
如图所示，定涡旋可以包括部分地限定高压空间DC的毂部181，第一密封部S140可以与毂部181的径向内侧壁抵接(如图2和图8所示)，或者，第 一密封部S140可以与毂部181的径向外侧壁抵接(如图6所示)。第一密封部S140可以设置为单个密封部，以简化密封组件的结构。
在实施方式的另一个方面，定涡旋150可以包括定涡旋本体和定涡旋盖板170，定涡旋本体可以包括定涡旋端板154，定涡旋盖板170附接至定涡旋端板154，毂部171形成在定涡旋盖板170处。在分体式定涡旋中，借助于定涡旋盖板，允许密封组件附接至定涡旋盖板而无需附接至定涡旋本体，从而允许在定涡旋本体与定涡旋盖板之间形成具有更大容积的更适于安装各种阀的高压空间。并且，将密封组件设置在盖板的毂部上，使得可以减小密封组件的尺寸，降低成本。
有利地，参见图6，密封组件S100可以包括与毂部181的径向外侧壁抵接的单个第一密封部的情况下，图6中的单个第一密封部设置在定涡旋(不存在盖板的情况下)的毂部181上，密封组件S100可以包括径向向内延伸超过毂部181的径向外侧壁的延伸部S141，换句话说，延伸部的内径尺寸D1小于毂部181的外径尺寸D2。更优选地，延伸部S141可以延伸超过毂部181的径向内侧壁。类似地，在图4中，单个第一密封部设置在盖板170的毂部171上，密封组件S100也可以包括径向向内延伸超过毂部171的径向外侧壁的延伸部S141，即，延伸部的内径尺寸D3小于毂部171的外径尺寸D4。更优选地，延伸部S141可以延伸超过毂部171的径向内侧壁。该延伸部允许在其下方形成高压受压部，从而在压缩机运行期间利用高压区域中的高压将密封组件向上推压。进一步地，第二密封部S142可以形成在延伸部S141处。
尽管在此已详细描述了本公开的优选实施方式，但要理解的是本公开并不局限于在此详细描述和示出的具体结构，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要求保护的权利要求的范围内。

Claims (10)

  1. 一种涡旋压缩机(100)，包括：
    壳体(110)，在所述壳体内限定有处于吸气压力的低压区域(LR)；
    压缩机构(CM)，所述压缩机构设置在所述壳体(110)内并且包括定涡旋(150)和动涡旋，所述定涡旋(150)包括定涡旋端板(154)、形成在所述定涡旋端板中的排气口(159)、形成在所述定涡旋端板一侧的螺旋状的定涡旋叶片(156)以及形成在所述定涡旋端板另一侧的与所述排气口连通的处于排气压力的高压空间(DC)；以及
    密封组件(S100)，
    其特征在于，所述密封组件包括第一密封部(S140)，所述第一密封部构造成抵接于所述定涡旋以将所述高压空间与所述低压区域隔绝。
  2. 根据权利要求1所述的涡旋压缩机(100)，其中：
    所述涡旋压缩机包括隔板(116)，所述隔板将所述壳体内的内部空间分隔成第一区域和第二区域，所述第一区域包括所述低压区域(LR)并且容纳所述压缩机构，所述第二区域接纳来自所述高压空间(DC)的经过压缩的高压工作流体，
    所述隔板(116)设置有孔口，以及
    所述密封组件(S100)包括用于将所述高压空间与所述低压区域隔绝的第二密封部(S142)，所述第二密封部构造成适于抵接于所述隔板或者抵接于附接至所述隔板的所述孔口处的附接件(S120)。
  3. 根据权利要求2所述的涡旋压缩机(100)，其中：
    所述密封组件(S100)包括顶板(S110)和底板(S130)，
    所述第一密封部(S140)包括插置在所述顶板与所述底板之间的连接部和抵接于所述定涡旋的唇缘部，以及
    所述第二密封部(S142)形成在所述顶板(S110)处。
  4. 根据权利要求2所述的涡旋压缩机(100)，其中，所述涡旋压缩机包括适于将所述密封组件(S100)朝向所述隔板(116)推压的启动弹簧(S150)。
  5. 根据权利要求1所述的涡旋压缩机(100)，其中：
    所述涡旋压缩机包括隔板(116)，所述隔板将所述壳体内的内部空间分隔成第一区域和第二区域，所述第一区域包括所述低压区域(LR)并且容纳所述压缩机构，所述第二区域接纳来自所述高压空间(DC)的经过压缩的高压工作流体，
    所述隔板(116)设置有孔口，在所述孔口处附接有附接件(S120)，以及
    所述密封组件(S100)包括顶板(S110)，所述顶板固定至所述附接件或者与所述附接件成一体。
  6. 根据权利要求5所述的涡旋压缩机(100)，其中：
    所述密封组件(S100)包括底板(S130)，所述底板附接至所述顶板，以及
    所述第一密封部(S140)包括插置在所述顶板(S110)与所述底板(S130)之间的连接部和抵接于所述定涡旋的唇缘部。
  7. 根据权利要求1至6中任一项所述的涡旋压缩机(100)，其中：
    所述定涡旋(150)包括部分地限定所述高压空间(DC)的毂部(181、171)，以及
    所述第一密封部与所述毂部的径向内侧壁抵接，或者，所述第一密封部与所述毂部的径向外侧壁抵接。
  8. 根据权利要求7所述的涡旋压缩机(100)，其中，所述定涡旋(150) 包括定涡旋本体和定涡旋盖板(170)，所述定涡旋本体包括所述定涡旋端板(154)，所述定涡旋盖板(170)附接至所述定涡旋端板(154)，所述毂部(171)形成在所述定涡旋盖板(170)处。
  9. 根据权利要求2所述的涡旋压缩机(100)，其中，所述定涡旋(150)包括部分地限定所述高压空间(DC)的毂部(181、171)，所述第一密封部与所述毂部的径向外侧壁抵接，所述密封组件(S100)包括径向向内延伸超过所述毂部的径向内侧壁的延伸部(S141)，所述第二密封部(S142)形成在所述延伸部(S141)处。
  10. 根据权利要求1至6中任一项所述的涡旋压缩机(100)，其中，在所述高压空间(DC)中设置有可变容积比阀(190)。
PCT/CN2021/137743 2020-12-15 2021-12-14 涡旋压缩机 WO2022127768A1 (zh)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1177062A (zh) * 1996-06-12 1998-03-25 东芝株式会社 涡轮式压缩机
US6390792B1 (en) * 2001-01-23 2002-05-21 Rechi Precision Co., Ltd. Venting passage for isolation block of scroll compressor and check valve for the same
US20040126246A1 (en) * 2002-12-30 2004-07-01 Industrial Technology Research Institute Load-regulating device for scroll type compressors
CN101614205A (zh) * 2009-07-15 2009-12-30 大连三洋压缩机有限公司 一种涡旋式压缩机
CN103161728A (zh) * 2011-12-14 2013-06-19 丹佛斯商用压缩机有限公司 变速涡旋式制冷压缩机
CN214196666U (zh) * 2020-12-15 2021-09-14 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1177062A (zh) * 1996-06-12 1998-03-25 东芝株式会社 涡轮式压缩机
US6390792B1 (en) * 2001-01-23 2002-05-21 Rechi Precision Co., Ltd. Venting passage for isolation block of scroll compressor and check valve for the same
US20040126246A1 (en) * 2002-12-30 2004-07-01 Industrial Technology Research Institute Load-regulating device for scroll type compressors
CN101614205A (zh) * 2009-07-15 2009-12-30 大连三洋压缩机有限公司 一种涡旋式压缩机
CN103161728A (zh) * 2011-12-14 2013-06-19 丹佛斯商用压缩机有限公司 变速涡旋式制冷压缩机
CN214196666U (zh) * 2020-12-15 2021-09-14 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

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