WO2024032534A1 - Compression mechanism and scroll compressor - Google Patents

Compression mechanism and scroll compressor Download PDF

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Publication number
WO2024032534A1
WO2024032534A1 PCT/CN2023/111415 CN2023111415W WO2024032534A1 WO 2024032534 A1 WO2024032534 A1 WO 2024032534A1 CN 2023111415 W CN2023111415 W CN 2023111415W WO 2024032534 A1 WO2024032534 A1 WO 2024032534A1
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WO
WIPO (PCT)
Prior art keywords
fixed scroll
back pressure
end plate
section
scroll
Prior art date
Application number
PCT/CN2023/111415
Other languages
French (fr)
Chinese (zh)
Inventor
刘轩
刘鑫娴
邹宏伟
Original Assignee
谷轮环境科技（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 CN202222076401.8U external-priority patent/CN218030611U/en
Priority claimed from CN202210944867.7A external-priority patent/CN117570019A/en
Application filed by 谷轮环境科技（苏州）有限公司 filed Critical 谷轮环境科技（苏州）有限公司
Publication of WO2024032534A1 publication Critical patent/WO2024032534A1/en

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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

Definitions

  • the present disclosure relates to a compression mechanism and a scroll compressor having the compression mechanism.
  • Scroll compressors can be used in refrigeration systems, air conditioning systems and heat pump systems, for example.
  • the compression mechanism of the scroll compressor is used to compress the working fluid (such as refrigerant).
  • the compression mechanism includes a fixed scroll and an orbiting scroll that rotates in translation relative to the fixed scroll.
  • Both the fixed scroll and the orbiting scroll include an end plate and spiral blades extending from one side of the end plate.
  • a series of moving compression cavities are formed between the fixed scroll and the spiral blades of the orbiting scroll, with the volume gradually decreasing from the radial outer side to the radial inner side, thus compressing the working fluid. .
  • a back pressure chamber is provided in the scroll compressor to provide back pressure for engaging the fixed scroll and the orbiting scroll in the axial direction.
  • the pressure in the back pressure chamber will fluctuate, resulting in a reduction in the working reliability of the compressor, and there is a risk that the working fluid will flow back into the compression chamber and cause repeated compression, resulting in energy loss of the scroll compressor. Risks of losses and wasted efficiency.
  • An object of one or more embodiments of the present disclosure is to provide a compression mechanism and a scroll compressor that have improved reliability and prevent energy loss and efficiency waste.
  • a compression mechanism including: a fixed scroll, which is an integral component and includes an integrally formed fixed scroll end plate and a fixed scroll blade, the fixed scroll blade is formed on the fixed scroll The first side of the movable scroll end plate; the movable scroll, the movable scroll includes the movable scroll end plate and the movable scroll blades formed on the first side of the movable scroll end plate, and the fixed scroll blades and the movable scroll blades interact with each other.
  • the back pressure passage includes an expansion section and a narrowing section formed on opposite sides of the expansion section, and the fluid flow cross-sectional area of the expansion section is greater than the fluid flow of each of the narrowing sections. Flow cross-sectional area.
  • the central axis of one of the narrowing sections is offset from the central axis of the other of the narrowing sections.
  • the back pressure channel includes two or more expansion sections, and each of the expansion sections is formed with constriction sections on opposite sides.
  • the back pressure passage is formed in the fixed scroll end plate and extends through the fixed scroll end plate.
  • the fixed scroll further includes a fixed scroll hub formed between the fixed scroll end plate and the fixed scroll end plate.
  • the fixed scroll hub On the second side opposite to the first side, the fixed scroll hub includes a first annular hub and a second annular hub, and the back pressure chamber is surrounded by the fixed scroll end plate, the first annular hub and the second annular hub. Space composition.
  • the back pressure passage includes a first narrowing section open to a compression chamber and a second narrowing section open to the back pressure chamber, and the opposite sides of the fixed scroll end plate are processed with connected first drills. hole and a second drilled hole, the second drilled hole having a hole diameter larger than the first drilled hole and having an end open to the back pressure chamber, the end being mounted with a divider, the divider including a part that allows fluid flow therethrough
  • the through hole and the blocking part that blocks the flow of fluid, the first narrowing section is formed by the first drilled hole, the second narrowed section is formed by the through hole, and the expansion section is formed by the part of the second drilled hole where the partition is not installed. form.
  • the divider is removably mounted to the end of the second bore, and the divider includes a plurality of spaced through holes.
  • a back pressure passage is formed in and extends through the orbiting scroll end plate, and the back pressure cavity is formed on a second side of the orbiting scroll end plate opposite to the first side.
  • the axial length of the expansion section is greater than the axial length of each of the narrowing sections.
  • each of the narrowing sections has the same flow cross-sectional area, and the fluid flow cross-sectional area of the expansion section is in the range of 1.1 to 1.5 times the flow cross-sectional area of the narrowing section, or,
  • the narrowing sections have different fluid flow cross-sectional areas respectively, and the fluid flow cross-sectional area of the expansion section is in the range of 1.1 to 1.5 times the maximum fluid flow cross-sectional area of the narrowing section.
  • FIG. 1 is a cross-sectional view showing a scroll compressor according to a comparative example
  • Figures 2a and 2b are schematic diagrams showing changes in the compression chamber connected to the back pressure channel during the operation of the scroll compressor
  • FIG. 3 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the first embodiment of the present disclosure
  • FIG. 4 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the second embodiment of the present disclosure.
  • FIG. 5 is a cross-sectional view showing a fixed scroll of a scroll compressor according to a third embodiment of the present disclosure.
  • Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those skilled in the art. Numerous specific details are set forth, such as examples of specific components, devices, and methods, in order to provide a thorough understanding of the various embodiments of the disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and should not be construed to limit the scope of the disclosure. In some exemplary embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.
  • the scroll compressor 1 includes a compression mechanism, a motor, a rotating shaft, a main bearing seat 50 and an interior defining accommodating the scroll compression mechanism. Space shell.
  • the compression mechanism includes a fixed scroll 20 and an orbiting scroll 30 .
  • the motor is configured to rotate the rotating shaft, and then the rotating shaft drives the movable scroll 30 to orbit relative to the fixed scroll 20 (that is, the central axis of the movable scroll moves around the central axis of the fixed scroll, but the movable scroll does not Rotate around its central axis) to compress the working fluid.
  • the fixed scroll 20 may be fixed relative to the housing body 10 in any suitable manner.
  • the fixed scroll 20 may include a fixed scroll end plate 22 , a fixed scroll blade 24 formed on one side of the fixed scroll end plate 22 , and a fixed scroll hub formed on the other side of the fixed scroll end plate 22 .
  • the non-orbiting scroll hub may include a first annular hub 26 and a second annular hub 28 .
  • the orbiting scroll 30 may include an orbiting scroll end plate 32 and an orbiting scroll blade 34 formed on one side of the orbiting scroll end plate 32 .
  • the fixed scroll blades 24 and the orbiting scroll blades 34 are capable of engaging each other such that a series of volumes are formed between the fixed scroll blades 24 and the orbiting scroll blades 34 from radially outward to radially inward when the scroll compressor is operating.
  • the gradually decreasing moving compression chamber achieves compression of the working fluid.
  • the main bearing seat 50 is adapted to support the orbiting scroll end plate 32 of the orbiting scroll 30 .
  • the orbiting scroll end plate 32 orbits on the supporting surface of the main bearing seat 50 .
  • the main bearing housing 50 may be fixed relative to the casing body 10 of the scroll compressor 1 by any suitable means.
  • a back pressure chamber is usually provided for one of the fixed scroll 20 and the movable scroll 30 , so that the fixed scroll 20
  • the orbiting scroll 30 can reliably engage with each other under the action of back pressure.
  • a first annular hub 26 is formed around the exhaust port 40 .
  • the back pressure chamber 70 is formed by the space surrounded by the fixed scroll end plate 22, the first annular hub 26 and the second annular hub 28 and is closed by a seal assembly disposed therein.
  • the back pressure chamber 70 is in fluid communication with one of a series of compression chambers between the orbiting scroll 30 and the fixed scroll 20 through the back pressure channel 60 formed in the fixed scroll end plate 22 , thereby exerting force on the orbiting scroll 30
  • the back pressure in the back pressure chamber 70 can effectively press the fixed scroll 20 and the orbiting scroll 30 together.
  • the volume of the compression chamber connected to the back pressure passage 60 and the corresponding pressure change dynamically.
  • the back pressure channel is connected to a smaller compression chamber (shaded area), and the pressure in the compression chamber is larger.
  • the fluid in the compression chamber flows into the back pressure chamber.
  • the back pressure channel will be connected to the larger compression chamber (the shaded area), and the pressure in the compression chamber will Small, at this time, the fluid in the back pressure chamber flows back into the compression chamber.
  • the fluid injected back into the compression chamber will be vortexed
  • the scroll compressor repeatedly compresses, which will lead to energy loss and efficiency waste of the scroll compressor.
  • the pressure in the back pressure chamber fluctuates with the compression process and cannot remain stable, the reliability of the scroll compressor is reduced.
  • the inventor of the present invention has conceived an improved compression mechanism and scroll compressor.
  • This compression mechanism can not only reduce or prevent the back pressure fluctuation of the scroll compressor, but also prevent the backflow of fluid from the back pressure chamber. Repeated compression occurs in the compression chamber.
  • FIGS. 3 to 5 wherein the same reference numerals in the drawings represent the same components and detailed descriptions of these components will be omitted.
  • the scroll compressor according to the first embodiment of the present disclosure is similar in structure to the scroll compressor according to the comparative example described above, in which only the fixed scroll 20A shown in FIG. 3 is used instead of the scroll compressor according to the comparative example.
  • Fixed scroll 20, other structures of the scroll compressor remain basically unchanged.
  • the fixed scroll 20A may be an integral component and include an integrally formed fixed scroll end plate 22 and a fixed scroll blade 24 , wherein the fixed scroll blade 24 may be formed on the fixed scroll end plate 22 the first side.
  • the integrated fixed scroll refers to the fixed scroll formed as a single piece processed in one piece, rather than the split fixed scroll formed by connecting multiple parts.
  • the non-orbiting scroll also includes a non-orbiting scroll hub 26, 28, which may be formed on a second side of the non-orbiting scroll end plate 22 opposite the first side. Obviously, the non-orbiting scroll hub portions 26, 28 are formed integrally with the non-orbiting scroll end plate 22, rather than being formed as two separate components that are mechanically connected or fixed to each other.
  • the fixed scroll end plate 22 may be provided with a back pressure passage 60A that fluidly communicates one compression chamber in a series of compression chambers with the back pressure chamber 70 .
  • the back pressure passage 60A may include an expansion section 62A and constriction sections formed on opposite sides of the expansion section (herein, the constriction section opening to the compression chamber will be referred to as the first constriction section 64A, and The narrowed section opening to the back pressure chamber 70 is called the second narrowed section 66A).
  • the fluid flow cross-sectional area of the expanded section 62A may be larger than the fluid flow cross-sectional area of either of the first narrowing section 64A and the second narrowing section 66A.
  • the cross-section perpendicular to the direction of fluid movement is called the fluid flow cross-section, and its area is called the fluid flow cross-section area.
  • the fluid When the fluid flows from the compression chamber to the back pressure chamber, the fluid first flows through the first narrowing section 64A, and the fluid undergoes a process of becoming thinner and narrower from the larger fluid flow cross-sectional area in the compression chamber, so that the flow velocity becomes larger and the dynamic movement becomes smaller.
  • the pressure increases and the static pressure decreases.
  • the fluid enters the expansion section 62A from the first narrowing section 64A.
  • the high-speed fluid sprayed from the first narrowing section 64A forms a high-speed main fluid in the middle of the expansion section 62A, and symmetrical vortices are formed on both sides of the main fluid.
  • the high-speed main fluid continuously interacts with the vortices on both sides.
  • the fluid is pulled forward by the high-speed main fluid in the middle, so that the speed of the high-speed main fluid in the middle decreases and the speed of the vortex fluid increases until the main flow in the middle is not enough to overcome the pressure difference, the vortex fluid flows back, and the middle fluid area is enlarged.
  • the fluid passes through the second narrowing section 66A, the fluid flow cross-sectional area is reduced again, and the kinetic energy is rapidly transformed into pressure potential energy. As a result, the fluid experiences a double throttling effect.
  • the fluid when fluid flows from the back pressure chamber to the compression chamber, the fluid first flows through the second constriction section 66A, then enters the expansion section 62A from the second constriction section 66A, and finally flows through the first constriction In section 64A, the fluid also undergoes double throttling.
  • the back pressure channel 60A can produce a secondary throttling effect. This enhanced throttling effect increases the flow resistance of the back pressure chamber and the compression chamber, allowing the back pressure in the back pressure chamber to remain stable and prevent the fluid from flowing. The flow back into the compression chamber causes repeated compression, thereby improving scroll compressor performance.
  • the axial length of the expansion section 62A may be greater than the axial length of each of the first constriction section 64A and the second constriction section 66A, which may be further enhanced by increasing the axial length of the expansion section 62A.
  • the throttling effect of the back pressure channel will further keep the back pressure stable and prevent repeated compression of the fluid.
  • the fluid flow cross-sectional area of the expansion section 62A may be in the range of 1.1 to 1.5 times the fluid flow cross-sectional area of the first narrowing section 66A or the second narrowing section 66A. It should be noted here that the first narrowing section 64A and the second narrowing section 66A may have the same fluid flow cross-sectional area.
  • the fluid flow cross-sectional area of the expansion section 62A may be in the first narrowing section.
  • the fluid flow cross-sectional area of the section 64A or the second narrow section 66A is within a range of 1.1 to 1.5 times.
  • the first narrowing section 64A may also have a different fluid flow cross-sectional area than the second narrowing section 66A.
  • the fluid flow cross-sectional area of the expansion section 62A may be between the first narrowing section 64A and the second narrowing section 64A. In the range of 1.1 to 1.5 times the larger fluid flow cross-sectional area in the narrow section 66A.
  • the throttling effect of the back pressure channel can be further enhanced, thereby maintaining The back pressure stabilizes and prevents repeated compression of the fluid.
  • the opposite sides of the fixed scroll end plate 22 may be processed with connected first boreholes and second boreholes.
  • the diameter of the second borehole is larger than the diameter of the first borehole and the second borehole has a diameter of Open to the end of the back pressure chamber 70, a partition 80A is installed in this end.
  • the partition 80A may include a through hole 82A that allows fluid flow therethrough and a barrier 84A that blocks the flow of fluid.
  • the first narrowing section 64A may be formed by the first drilled hole
  • the second narrowed section 66A may be formed by the through hole 82A
  • the expansion section 62A may be formed by a portion of the second drilled hole where the partition 80 is not installed. form.
  • the spacer may, for example, be a screw formed with an external thread for detachable mounting into the second bore. In this way, a fixed scroll with a secondary throttling effect can be easily machined.
  • the partition 80A includes a plurality of spaced apart A through hole, of course, the separator can also be formed with other forms of through holes. It should be understood that in the case where the partition 80A includes a plurality of through holes, the fluid flow cross-sectional area of the second narrowing section 66A is the sum of the fluid flow cross-sectional areas of the plurality of through holes.
  • FIG. 4 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the second embodiment of the present disclosure.
  • the fixed scroll 20B of the scroll compressor according to the second embodiment of the present disclosure is similar in structure to the fixed scroll 20A of the scroll compressor according to the first embodiment of the present disclosure described above, and the only difference is that The structure of the back pressure channel is different, and only the differences will be described in detail below.
  • the fixed scroll back pressure passage 60B may include an expansion section 62B and first and second constriction sections 64B and 66B disposed on opposite sides of the expansion section, wherein , the fluid flow cross-sectional area of the expansion section 62B may be larger than the fluid flow cross-sectional area of each of the first narrowing section 64B and the second narrowing section 66B. Moreover, the central axis of the first narrowing section 64B and the central axis of the second narrowing section 66B are staggered.
  • Figure 4 also shows an alternative embodiment of a divider 80B that may include a through hole 82B that allows fluid flow therethrough and a barrier 84B that blocks fluid flow.
  • the through hole 82B may be a single through hole formed in the center of the partition 80B.
  • FIG. 5 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the third embodiment of the present disclosure.
  • the fixed scroll 20C of the scroll compressor according to the third embodiment of the present disclosure is similar in structure to the fixed scroll 20A of the scroll compressor according to the first embodiment of the present disclosure described above, and the only difference is that The structure of the back pressure channel is different, and only the differences will be described in detail below.
  • the fixed scroll bias passage 60C may include a plurality of expansion sections and narrowing sections disposed on opposite sides of each expansion section, wherein a fluid flow cross-section of the expansion section The area may be greater than the fluid flow cross-sectional area of each of the narrowed sections.
  • the fluid undergoes multiple throttling in the back pressure channel 60C, causing the fluid to encounter greater flow resistance, thereby further improving the stability of the pressure in the back pressure chamber and further reducing the risk of fluid backflow into the compression chamber causing repeated compression. Improve scroll compressor performance.
  • a back-pressure channel with a secondary throttling effect can also be provided in the movable scroll end plate to achieve the same purpose, that is, the back-pressure channel can extend through the movable scroll.
  • the end plate communicates with the back pressure chamber formed on one side of the orbiting scroll.
  • a back pressure chamber may be formed in a space within the main bearing housing 50 and be in fluid communication with one of the series of compression chambers via a back pressure passage formed in the orbiting scroll end plate.
  • the narrowing section has a uniform cross-sectional shape
  • the narrowing section can also have any other suitable shape, such as a tapered shape. V-shaped shape, etc.

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

Abstract

A compression mechanism, comprising: a fixed scroll, the fixed scroll comprising a fixed scroll end plate and a fixed scroll blade; a movable scroll, the movable scroll comprising a movable scroll end plate and a movable scroll blade, and the fixed scroll blade and the movable scroll blade being mutually engaged to form a series of compression cavities; and a back pressure cavity, the back pressure cavity being in fluid communication with a compression cavity by means of a back pressure channel so as to apply back pressure, the back pressure channel comprising an expanded section and narrowed sections formed on two opposite sides of the expanded section, and the fluid flow cross-sectional area of the expanded section being larger than that of each narrowed section. A scroll compressor comprising the compression mechanism has high reliability.

Description

压缩机构和涡旋压缩机Compression mechanism and scroll compressor
本申请要求以下中国专利申请的优先权：于2022年8月8日提交中国专利局的申请号为202210944867.7、发明创造名称为“压缩机构和涡旋压缩机”的中国专利申请；于2022年8月8日提交中国专利局的申请号为202222076401.8、发明创造名称为“压缩机构和涡旋压缩机”的中国专利申请。这些专利申请的全部内容通过引用结合在本申请中。This application claims priority from the following Chinese patent applications: a Chinese patent application with application number 202210944867.7 and an invention title "Compression Mechanism and Scroll Compressor" submitted to the China Patent Office on August 8, 2022; The Chinese patent application with the application number 202222076401.8 and the invention name "Compression Mechanism and Scroll Compressor" was submitted to the China Patent Office on March 8. The entire contents of these patent applications are incorporated by reference into this application.
技术领域Technical field
本公开涉及压缩机构以及具有该压缩机构的涡旋压缩机。The present disclosure relates to a compression mechanism and a scroll compressor having the compression mechanism.
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 contents in this section only provide background information related to the present disclosure and may not constitute prior art.
涡旋压缩机可以应用于例如制冷***、空调***和热泵***中。涡旋压缩机的压缩机构作为其主要部件用于实现工作流体(例如制冷剂)的压缩。压缩机构包括定涡旋和相对于定涡旋平动绕动的动涡旋。定涡旋和动涡旋均包括端板和从端板的一侧延伸的螺旋叶片。当动涡旋相对于定涡旋绕动时，定涡旋和动涡旋的螺旋叶片之间形成体积从径向外侧向径向内侧逐渐减小的一系列移动的压缩腔，由此压缩工作流体。Scroll compressors can be used in refrigeration systems, air conditioning systems and heat pump systems, for example. As its main component, the compression mechanism of the scroll compressor is used to compress the working fluid (such as refrigerant). The compression mechanism includes a fixed scroll and an orbiting scroll that rotates in translation relative to the fixed scroll. Both the fixed scroll and the orbiting scroll include an end plate and spiral blades extending from one side of the end plate. When the orbiting scroll orbits relative to the fixed scroll, a series of moving compression cavities are formed between the fixed scroll and the spiral blades of the orbiting scroll, with the volume gradually decreasing from the radial outer side to the radial inner side, thus compressing the working fluid. .
背压腔设置在涡旋压缩机中从而提供使定涡旋与动涡旋在轴向方向上接合的背压力。然而，涡旋压缩机的实际操作中，存在背压腔内的压力发生波动导致压缩机的工作可靠性降低的风险，并且存在工作流体回灌到压缩腔中发生重复压缩导致涡旋压缩机能量损耗和效率浪费的风险。A back pressure chamber is provided in the scroll compressor to provide back pressure for engaging the fixed scroll and the orbiting scroll in the axial direction. However, in the actual operation of the scroll compressor, there is a risk that the pressure in the back pressure chamber will fluctuate, resulting in a reduction in the working reliability of the compressor, and there is a risk that the working fluid will flow back into the compression chamber and cause repeated compression, resulting in energy loss of the scroll compressor. Risks of losses and wasted efficiency.
因此，需要提供一种改进的压缩机构及涡旋压缩机。Therefore, there is a need to provide an improved compression mechanism and scroll compressor.
发明内容Contents of the invention
本公开的一个或多个实施方式的目的是提供一种具有提高的可靠性且防止能量损耗和效率浪费的压缩机构及涡旋压缩机。 An object of one or more embodiments of the present disclosure is to provide a compression mechanism and a scroll compressor that have improved reliability and prevent energy loss and efficiency waste.
根据本公开的一个方面，提供了一种压缩机构包括：定涡旋，定涡旋是一体式部件并且包括一体形成的定涡旋端板以及定涡旋叶片，定涡旋叶片形成在定涡旋端板的第一侧；动涡旋，动涡旋包括动涡旋端板和形成在动涡旋端板的第一侧的动涡旋叶片，并且定涡旋叶片与动涡旋叶片相互接合以在其间形成一系列能够对流体进行压缩的压缩腔；以及背压腔，背压腔通过背压通道与一系列压缩腔中的一个压缩腔流体连通以施加使得动涡旋与定涡旋接合的背压力；其特征在于，背压通道包括膨胀部段以及形成在膨胀部段相反两侧的缩窄部段，膨胀部段的流体流通截面面积大于缩窄部段的每一者的流体流通截面面积。According to one aspect of the present disclosure, there is provided a compression mechanism including: a fixed scroll, which is an integral component and includes an integrally formed fixed scroll end plate and a fixed scroll blade, the fixed scroll blade is formed on the fixed scroll The first side of the movable scroll end plate; the movable scroll, the movable scroll includes the movable scroll end plate and the movable scroll blades formed on the first side of the movable scroll end plate, and the fixed scroll blades and the movable scroll blades interact with each other. joined to form a series of compression chambers capable of compressing the fluid therebetween; and a back pressure chamber in fluid communication with one of the series of compression chambers through a back pressure passage to exert an orbiting scroll and a fixed scroll Joint back pressure; characterized in that the back pressure passage includes an expansion section and a narrowing section formed on opposite sides of the expansion section, and the fluid flow cross-sectional area of the expansion section is greater than the fluid flow of each of the narrowing sections. Flow cross-sectional area.
可选地，缩窄部段中的一个缩窄部段的中心轴线与缩窄部段中的另一个缩窄部段的中心轴线错开。Optionally, the central axis of one of the narrowing sections is offset from the central axis of the other of the narrowing sections.
可选地，背压通道包括两个或更多个膨胀部段，并且膨胀部段中的每一者的相反两侧均形成有缩窄部段。Optionally, the back pressure channel includes two or more expansion sections, and each of the expansion sections is formed with constriction sections on opposite sides.
可选地，背压通道形成在定涡旋端板中且延伸穿过定涡旋端板，定涡旋还包括定涡旋毂部，定涡旋毂部形成在定涡旋端板的与第一侧相反的第二侧，定涡旋毂部包括第一环形毂部和第二环形毂部，背压腔由定涡旋端板、第一环形毂部和第二环形毂部围绕的空间构成。Optionally, the back pressure passage is formed in the fixed scroll end plate and extends through the fixed scroll end plate. The fixed scroll further includes a fixed scroll hub formed between the fixed scroll end plate and the fixed scroll end plate. On the second side opposite to the first side, the fixed scroll hub includes a first annular hub and a second annular hub, and the back pressure chamber is surrounded by the fixed scroll end plate, the first annular hub and the second annular hub. Space composition.
可选地，背压通道包括敞开至一个压缩腔的第一缩窄部段以及敞开至背压腔的第二缩窄部段，定涡旋端板的相反两侧加工有连通的第一钻孔和第二钻孔，第二钻孔的孔径大于第一钻孔的孔径并且第二钻孔具有敞开至背压腔的端部，端部安装有分隔件，分隔件包括允许流体流动穿过的通孔以及阻挡流体流动的阻挡部，第一缩窄部段由第一钻孔形成，第二缩窄部段由通孔形成，膨胀部段由第二钻孔的未安装分隔件的部分形成。Optionally, the back pressure passage includes a first narrowing section open to a compression chamber and a second narrowing section open to the back pressure chamber, and the opposite sides of the fixed scroll end plate are processed with connected first drills. hole and a second drilled hole, the second drilled hole having a hole diameter larger than the first drilled hole and having an end open to the back pressure chamber, the end being mounted with a divider, the divider including a part that allows fluid flow therethrough The through hole and the blocking part that blocks the flow of fluid, the first narrowing section is formed by the first drilled hole, the second narrowed section is formed by the through hole, and the expansion section is formed by the part of the second drilled hole where the partition is not installed. form.
可选地，分隔件可拆卸地安装至第二钻孔的端部，并且分隔件包括间隔开的多个通孔。Optionally, the divider is removably mounted to the end of the second bore, and the divider includes a plurality of spaced through holes.
可选地，背压通道形成在动涡旋端板中且延伸穿过动涡旋端板，背压腔形成在动涡旋端板的与第一侧相反的第二侧。Optionally, a back pressure passage is formed in and extends through the orbiting scroll end plate, and the back pressure cavity is formed on a second side of the orbiting scroll end plate opposite to the first side.
可选地，膨胀部段的轴向长度大于缩窄部段的每一者的轴向长度。Optionally, the axial length of the expansion section is greater than the axial length of each of the narrowing sections.
可选地，缩窄部段中的每一者具有相同的流通截面面积，膨胀部段的流体流通截面面积处于缩窄部段的流通截面面积的1.1至1.5倍的范围内，或者， 缩窄部段分别具有不同的流体流通截面面积，膨胀部段的流体流通截面面积处于缩窄部段的最大流体流通截面面积的1.1至1.5倍的范围内。Optionally, each of the narrowing sections has the same flow cross-sectional area, and the fluid flow cross-sectional area of the expansion section is in the range of 1.1 to 1.5 times the flow cross-sectional area of the narrowing section, or, The narrowing sections have different fluid flow cross-sectional areas respectively, and the fluid flow cross-sectional area of the expansion section is in the range of 1.1 to 1.5 times the maximum fluid flow cross-sectional area of the narrowing section.
从下文的详细描述中，本公开的其它应用领域将变得更为明显。应该理解的是，这些详细描述和具体示例，虽然示出了本公开的优选实施例，但是它们旨在为了示例性说明的目的，而非试图限制本公开。Other areas of application of the present disclosure will become apparent from the detailed description below. It should be understood that the detailed description and specific examples, while indicating preferred embodiments of the disclosure, are intended for purposes of illustration and are not intended to limit the disclosure.
附图说明Description of drawings
通过以下参照附图的描述，本公开的一个或多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 more embodiments of the present disclosure will become more apparent from the following description with reference to the accompanying drawings, in which:
图1为示出了根据比较示例的涡旋压缩机的剖视图；1 is a cross-sectional view showing a scroll compressor according to a comparative example;
图2a和图2b为示出了在涡旋压缩机的工作过程中背压通道所连通的压缩腔的变化的示意图；Figures 2a and 2b are schematic diagrams showing changes in the compression chamber connected to the back pressure channel during the operation of the scroll compressor;
图3为示出了根据本公开的第一实施方式的涡旋压缩机的定涡旋的剖视图；3 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the first embodiment of the present disclosure;
图4为示出了根据本公开的第二实施方式的涡旋压缩机的定涡旋的剖视图；以及4 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the second embodiment of the present disclosure; and
图5为示出了根据本公开的第三实施方式的涡旋压缩机的定涡旋的剖视图。5 is a cross-sectional view showing a fixed scroll of a scroll compressor according to a third embodiment of the present disclosure.
具体实施方式Detailed ways
现在将参照附图更全面地描述示例性实施方式。Example embodiments will now be described more fully with reference to the accompanying drawings.
提供示例性实施方式以使得本公开将是详尽的并且将向本领域技术人员更全面地传达范围。阐述了许多具体细节比如具体部件、装置和方法的示例，以提供对本公开的各实施方式的透彻理解。对本领域技术人员而言将清楚的是，不需要采用具体细节，示例性实施方式可以以许多不同的形式实施，并且也不应当理解为限制本公开的范围。在一些示例性实施方式中，不对公知的过程、公知的装置结构和公知的技术进行详细的描述。Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those skilled in the art. Numerous specific details are set forth, such as examples of specific components, devices, and methods, in order to provide a thorough understanding of the various embodiments of the disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and should not be construed to limit the scope of the disclosure. In some exemplary embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.
下面参照图1来描述涡旋压缩机1的总体结构。如图所示，涡旋压缩机1包括压缩机构、马达、旋转轴、主轴承座50及限定容纳涡旋压缩机构的内部 空间的壳体。The overall structure of the scroll compressor 1 will be described below with reference to FIG. 1 . As shown in the figure, the scroll compressor 1 includes a compression mechanism, a motor, a rotating shaft, a main bearing seat 50 and an interior defining accommodating the scroll compression mechanism. Space shell.
压缩机构包括定涡旋20和动涡旋30。马达构造成使旋转轴旋转，接着，旋转轴驱动动涡旋30相对于定涡旋20绕动运动(即，动涡旋的中心轴线绕定涡旋的中心轴线运动，但是动涡旋不会绕其中心轴线旋转)以压缩工作流体。The compression mechanism includes a fixed scroll 20 and an orbiting scroll 30 . The motor is configured to rotate the rotating shaft, and then the rotating shaft drives the movable scroll 30 to orbit relative to the fixed scroll 20 (that is, the central axis of the movable scroll moves around the central axis of the fixed scroll, but the movable scroll does not Rotate around its central axis) to compress the working fluid.
定涡旋20可以以任何合适的方式相对于壳体本体10固定。定涡旋20可以包括定涡旋端板22、形成在定涡旋端板22一侧的定涡旋叶片24以及形成在定涡旋端板22的另一侧的定涡旋毂部。定涡旋毂部可以包括第一环形毂部26和第二环形毂部28。The fixed scroll 20 may be fixed relative to the housing body 10 in any suitable manner. The fixed scroll 20 may include a fixed scroll end plate 22 , a fixed scroll blade 24 formed on one side of the fixed scroll end plate 22 , and a fixed scroll hub formed on the other side of the fixed scroll end plate 22 . The non-orbiting scroll hub may include a first annular hub 26 and a second annular hub 28 .
动涡旋30可以包括动涡旋端板32以及形成在动涡旋端板32一侧的动涡旋叶片34。定涡旋叶片24与动涡旋叶片34能够彼此接合，使得当涡旋压缩机运行时在定涡旋叶片24和动涡旋叶片34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移动的压缩腔，从而实现对工作流体的压缩。The orbiting scroll 30 may include an orbiting scroll end plate 32 and an orbiting scroll blade 34 formed on one side of the orbiting scroll end plate 32 . The fixed scroll blades 24 and the orbiting scroll blades 34 are capable of engaging each other such that a series of volumes are formed between the fixed scroll blades 24 and the orbiting scroll blades 34 from radially outward to radially inward when the scroll compressor is operating. The gradually decreasing moving compression chamber achieves compression of the working fluid.
主轴承座50适于支承动涡旋30的动涡旋端板32。动涡旋端板32在主轴承座50的支承面上绕动。主轴承座50可以通过任何合适的方式相对于涡旋压缩机1的壳体本体10固定。The main bearing seat 50 is adapted to support the orbiting scroll end plate 32 of the orbiting scroll 30 . The orbiting scroll end plate 32 orbits on the supporting surface of the main bearing seat 50 . The main bearing housing 50 may be fixed relative to the casing body 10 of the scroll compressor 1 by any suitable means.
在压缩机1的正常工作中，定涡旋20和动涡旋30必须在轴向方向上彼此接合才能对工作流体进行压缩。另外，为了给涡旋组件提供一定的轴向柔性以增加压缩机的可靠性和安全性，通常为定涡旋20和动涡旋30中的一者设置背压腔，从而使得定涡旋20和动涡旋30能够在背压力的作用下彼此可靠接合。如图1所示，第一环形毂部26围绕排气口40形成。背压腔70由定涡旋端板22、第一环形毂部26和第二环形毂部28围绕的空间构成并且由设置在其内的密封组件封闭。背压腔70通过定涡旋端板22中形成的背压通道60与动涡旋30和定涡旋20之间的一系列压缩腔中的一个压缩腔流体连通，从而施加使得动涡旋30与定涡旋20接合的背压力，利用背压腔70中的背压力可以有效地将定涡旋20和动涡旋30压在一起。In normal operation of the compressor 1, the fixed scroll 20 and the orbiting scroll 30 must engage each other in the axial direction to compress the working fluid. In addition, in order to provide a certain axial flexibility to the scroll assembly to increase the reliability and safety of the compressor, a back pressure chamber is usually provided for one of the fixed scroll 20 and the movable scroll 30 , so that the fixed scroll 20 The orbiting scroll 30 can reliably engage with each other under the action of back pressure. As shown in FIG. 1 , a first annular hub 26 is formed around the exhaust port 40 . The back pressure chamber 70 is formed by the space surrounded by the fixed scroll end plate 22, the first annular hub 26 and the second annular hub 28 and is closed by a seal assembly disposed therein. The back pressure chamber 70 is in fluid communication with one of a series of compression chambers between the orbiting scroll 30 and the fixed scroll 20 through the back pressure channel 60 formed in the fixed scroll end plate 22 , thereby exerting force on the orbiting scroll 30 The back pressure in the back pressure chamber 70 can effectively press the fixed scroll 20 and the orbiting scroll 30 together.
然而，在涡旋压缩机的工作过程中，背压通道60所连通的压缩腔的体积以及相应的压力是动态变化的。具体地，如图2(a)所示，背压通道与体积较小的压缩腔(阴影覆盖的区域)连通，压缩腔内的压力较大，此时，压缩腔内的流体流入背压腔中；随着动涡旋30绕定涡旋20发生绕动，如图2(b)所示，背压通道将与体积较大的压缩腔(阴影覆盖的区域)连通，压缩腔内的压力较小，此时，背压腔中的流体回灌至压缩腔。流体回灌到压缩腔中将被涡 旋压缩机重复压缩，这会导致涡旋压缩机的能量损耗和效率浪费，并且，由于背压腔内的压力随压缩过程发生波动而不能保持稳定，使得涡旋压缩机的可靠性降低。However, during the operation of the scroll compressor, the volume of the compression chamber connected to the back pressure passage 60 and the corresponding pressure change dynamically. Specifically, as shown in Figure 2(a), the back pressure channel is connected to a smaller compression chamber (shaded area), and the pressure in the compression chamber is larger. At this time, the fluid in the compression chamber flows into the back pressure chamber. middle; as the movable scroll 30 revolves around the fixed scroll 20, as shown in Figure 2(b), the back pressure channel will be connected to the larger compression chamber (the shaded area), and the pressure in the compression chamber will Small, at this time, the fluid in the back pressure chamber flows back into the compression chamber. The fluid injected back into the compression chamber will be vortexed The scroll compressor repeatedly compresses, which will lead to energy loss and efficiency waste of the scroll compressor. Moreover, because the pressure in the back pressure chamber fluctuates with the compression process and cannot remain stable, the reliability of the scroll compressor is reduced.
为了解决上述问题，本发明人构想出了一种改进的压缩机构及涡旋压缩机，该压缩机构不仅能够减小或防止涡旋压缩机的背压发生波动并且防止流体从背压腔回灌至压缩腔发生重复压缩。In order to solve the above problems, the inventor of the present invention has conceived an improved compression mechanism and scroll compressor. This compression mechanism can not only reduce or prevent the back pressure fluctuation of the scroll compressor, but also prevent the backflow of fluid from the back pressure chamber. Repeated compression occurs in the compression chamber.
下面就结合图3至图5对根据本公开的涡旋压缩机做进一步详细的说明，其中，附图中相同的附图标记表示相同的部件并将省略对这些部件的具体描述。The scroll compressor according to the present disclosure will be described in further detail below with reference to FIGS. 3 to 5 , wherein the same reference numerals in the drawings represent the same components and detailed descriptions of these components will be omitted.
根据本公开的第一实施方式的涡旋压缩机与上文描述的根据比较示例的涡旋压缩机的结构类似，其中，仅用图3所示的定涡旋20A代替了根据比较示例中的定涡旋20，涡旋压缩机的其他构造基本不变。The scroll compressor according to the first embodiment of the present disclosure is similar in structure to the scroll compressor according to the comparative example described above, in which only the fixed scroll 20A shown in FIG. 3 is used instead of the scroll compressor according to the comparative example. Fixed scroll 20, other structures of the scroll compressor remain basically unchanged.
如图3所示，定涡旋20A可以是一体式部件并且包括一体形成的定涡旋端板22、以及定涡旋叶片24，其中，定涡旋叶片24可以形成在定涡旋端板22的第一侧。一体式的定涡旋指的是定涡旋形成为一体加工的单件形式，而非由多个部件连接形成的分体式定涡旋。定涡旋还包括定涡旋毂部26、28，其可以形成在定涡旋端板22与第一侧相反的第二侧。显然，定涡旋毂部26、28与定涡旋端板22一体形成，而不是形成为机械上相互连接或固定的两个单独的部件。As shown in FIG. 3 , the fixed scroll 20A may be an integral component and include an integrally formed fixed scroll end plate 22 and a fixed scroll blade 24 , wherein the fixed scroll blade 24 may be formed on the fixed scroll end plate 22 the first side. The integrated fixed scroll refers to the fixed scroll formed as a single piece processed in one piece, rather than the split fixed scroll formed by connecting multiple parts. The non-orbiting scroll also includes a non-orbiting scroll hub 26, 28, which may be formed on a second side of the non-orbiting scroll end plate 22 opposite the first side. Obviously, the non-orbiting scroll hub portions 26, 28 are formed integrally with the non-orbiting scroll end plate 22, rather than being formed as two separate components that are mechanically connected or fixed to each other.
定涡旋端板22中可以设置有将一系列压缩腔中的一个压缩腔与背压腔70流体连通的背压通道60A。背压通道60A可以包括膨胀部段62A以及形成在膨胀部段相反两侧的缩窄部段(在此，将敞开至压缩腔的缩窄部段称为第一缩窄部段64A，并将敞开至背压腔70的缩窄部段称为第二缩窄部段66A)。膨胀部段62A的流体流通截面面积可以大于第一缩窄部段64A和第二缩窄部段66A中的任一者的流体流通截面面积。本文中，将垂直于流体运动方向的截面称为流体流通截面,其面积大小称为流体流通截面面积。The fixed scroll end plate 22 may be provided with a back pressure passage 60A that fluidly communicates one compression chamber in a series of compression chambers with the back pressure chamber 70 . The back pressure passage 60A may include an expansion section 62A and constriction sections formed on opposite sides of the expansion section (herein, the constriction section opening to the compression chamber will be referred to as the first constriction section 64A, and The narrowed section opening to the back pressure chamber 70 is called the second narrowed section 66A). The fluid flow cross-sectional area of the expanded section 62A may be larger than the fluid flow cross-sectional area of either of the first narrowing section 64A and the second narrowing section 66A. In this article, the cross-section perpendicular to the direction of fluid movement is called the fluid flow cross-section, and its area is called the fluid flow cross-section area.
当流体从压缩腔向背压腔流动时，流体首先流动通过第一缩窄部段64A，流体经历从压缩腔中较大的流体流通截面面积变细变窄的过程，由此流速变大，动压提高，静压降低。随后流体从第一缩窄部段64A进入膨胀部段62A，从第一缩窄部段64A喷出的高速流体在膨胀部段62A的中间形成高速主流体，主流体两侧形成有对称漩涡，高速主流体不断与两侧涡旋相互作用，漩涡内的 流体被中间的高速主流体向前拉动，从而中间的高速主流体速度降低，漩涡流体速度提升，直至中间主流体不足以克服压差，漩涡流体回流，中间流体区域被拉大。此时流体经过第二缩窄部段66A，流体流通截面面积再次缩小，动能迅速向压力势能转变。由此，流体经历了双重节流作用。类似地，当流体从背压腔向压缩腔流动时，流体首先流动通过第二缩窄部段66A，随后从第二缩窄部段66A进入膨胀部段62A，并且最后流动通过第一缩窄部段64A，流体同样经受双重节流作用。由此，背压通道60A能够产生二次节流的效果，这种增强的节流效果增大了背压腔和压缩腔的流动阻力，使得背压腔内的背压力能够保持稳定并且防止流体回灌至压缩腔发生重复压缩，从而提高涡旋压缩机性能。When the fluid flows from the compression chamber to the back pressure chamber, the fluid first flows through the first narrowing section 64A, and the fluid undergoes a process of becoming thinner and narrower from the larger fluid flow cross-sectional area in the compression chamber, so that the flow velocity becomes larger and the dynamic movement becomes smaller. The pressure increases and the static pressure decreases. Then the fluid enters the expansion section 62A from the first narrowing section 64A. The high-speed fluid sprayed from the first narrowing section 64A forms a high-speed main fluid in the middle of the expansion section 62A, and symmetrical vortices are formed on both sides of the main fluid. The high-speed main fluid continuously interacts with the vortices on both sides. The fluid is pulled forward by the high-speed main fluid in the middle, so that the speed of the high-speed main fluid in the middle decreases and the speed of the vortex fluid increases until the main flow in the middle is not enough to overcome the pressure difference, the vortex fluid flows back, and the middle fluid area is enlarged. At this time, the fluid passes through the second narrowing section 66A, the fluid flow cross-sectional area is reduced again, and the kinetic energy is rapidly transformed into pressure potential energy. As a result, the fluid experiences a double throttling effect. Similarly, when fluid flows from the back pressure chamber to the compression chamber, the fluid first flows through the second constriction section 66A, then enters the expansion section 62A from the second constriction section 66A, and finally flows through the first constriction In section 64A, the fluid also undergoes double throttling. As a result, the back pressure channel 60A can produce a secondary throttling effect. This enhanced throttling effect increases the flow resistance of the back pressure chamber and the compression chamber, allowing the back pressure in the back pressure chamber to remain stable and prevent the fluid from flowing. The flow back into the compression chamber causes repeated compression, thereby improving scroll compressor performance.
优选地，膨胀部段62A的轴向长度可以大于第一缩窄部段64A以及第二缩窄部段66A的每一者的轴向长度，通过增加膨胀部段62A的轴向长度可以进一步增强背压通道的节流效果，从而将进一步保持背压力稳定并且防止流体重复压缩。并且优选地，膨胀部段62A的流体流通截面面积可以处于第一缩窄部段66A或第二缩窄部段66A的流体流通截面面积的1.1至1.5倍的范围内。在此需要说明的是，第一缩窄部段64A与第二缩窄部段66A可以具有相同的流体流通截面面积，此时，膨胀部段62A的流体流通截面面积可以处于第一缩窄部段64A或第二缩窄部段66A的流体流通截面面积的1.1至1.5倍的范围内。第一缩窄部段64A也可以具有与第二缩窄部段66A不同的流体流通截面面积，此时，膨胀部段62A的流体流通截面面积可以处于第一缩窄部段64A以及第二缩窄部段66A中较大的流体流通截面面积的1.1至1.5倍的范围内。通过使得膨胀部段62A的流体流通截面面积仅略大于第一缩窄部段64A以及第二缩窄部段66A的流体流通横截面面，还可以进一步增强背压通道的节流效果，从而保持背压力稳定并且防止流体重复压缩。Preferably, the axial length of the expansion section 62A may be greater than the axial length of each of the first constriction section 64A and the second constriction section 66A, which may be further enhanced by increasing the axial length of the expansion section 62A. The throttling effect of the back pressure channel will further keep the back pressure stable and prevent repeated compression of the fluid. And preferably, the fluid flow cross-sectional area of the expansion section 62A may be in the range of 1.1 to 1.5 times the fluid flow cross-sectional area of the first narrowing section 66A or the second narrowing section 66A. It should be noted here that the first narrowing section 64A and the second narrowing section 66A may have the same fluid flow cross-sectional area. At this time, the fluid flow cross-sectional area of the expansion section 62A may be in the first narrowing section. The fluid flow cross-sectional area of the section 64A or the second narrow section 66A is within a range of 1.1 to 1.5 times. The first narrowing section 64A may also have a different fluid flow cross-sectional area than the second narrowing section 66A. In this case, the fluid flow cross-sectional area of the expansion section 62A may be between the first narrowing section 64A and the second narrowing section 64A. In the range of 1.1 to 1.5 times the larger fluid flow cross-sectional area in the narrow section 66A. By making the fluid flow cross-sectional area of the expansion section 62A only slightly larger than the fluid flow cross-sections of the first narrowing section 64A and the second narrowing section 66A, the throttling effect of the back pressure channel can be further enhanced, thereby maintaining The back pressure stabilizes and prevents repeated compression of the fluid.
示例性地，定涡旋端板22的相反两侧可以加工有连通的第一钻孔和第二钻孔，第二钻孔的孔径大于第一钻孔的孔径并且所述第二钻孔具有敞开至背压腔70的端部，该端部中安装有分隔件80A。分隔件80A可以包括允许流体流动穿过的通孔82A以及阻挡流体流动的阻挡部84A。此时，第一缩窄部段64A可以由第一钻孔形成，第二缩窄部段66A可以由通孔82A形成，膨胀部段62A可以由第二钻孔的未安装分隔件80的部分形成。分隔件例如可以为形成有外螺纹的螺钉以可拆卸地安装至第二钻孔中。以此方式，能够简单地加工出具有二次节流效应的定涡旋。图3中示例性地示出了分隔件80A包括间隔开的多 个通孔，当然分隔件也可以形成有其他形式的通孔。应当理解的是，在分隔件80A包括多个通孔的情况下，第二缩窄部段66A的流体流通截面面积为多个通孔的流体流通截面面积之和。For example, the opposite sides of the fixed scroll end plate 22 may be processed with connected first boreholes and second boreholes. The diameter of the second borehole is larger than the diameter of the first borehole and the second borehole has a diameter of Open to the end of the back pressure chamber 70, a partition 80A is installed in this end. The partition 80A may include a through hole 82A that allows fluid flow therethrough and a barrier 84A that blocks the flow of fluid. At this time, the first narrowing section 64A may be formed by the first drilled hole, the second narrowed section 66A may be formed by the through hole 82A, and the expansion section 62A may be formed by a portion of the second drilled hole where the partition 80 is not installed. form. The spacer may, for example, be a screw formed with an external thread for detachable mounting into the second bore. In this way, a fixed scroll with a secondary throttling effect can be easily machined. It is schematically shown in FIG. 3 that the partition 80A includes a plurality of spaced apart A through hole, of course, the separator can also be formed with other forms of through holes. It should be understood that in the case where the partition 80A includes a plurality of through holes, the fluid flow cross-sectional area of the second narrowing section 66A is the sum of the fluid flow cross-sectional areas of the plurality of through holes.
图4为示出了根据本公开的第二实施方式的涡旋压缩机定涡旋的剖视图。根据本公开的第二实施方式的涡旋压缩机的定涡旋20B与上文描述的根据本公开的第一实施方式的涡旋压缩机的定涡旋20A的结构类似，其不同之处仅在于背压通道的结构不同，以下将仅对其不同之处进行详细描述。4 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the second embodiment of the present disclosure. The fixed scroll 20B of the scroll compressor according to the second embodiment of the present disclosure is similar in structure to the fixed scroll 20A of the scroll compressor according to the first embodiment of the present disclosure described above, and the only difference is that The structure of the back pressure channel is different, and only the differences will be described in detail below.
根据本公开的第二实施方式的定涡旋的背压通道60B可以包括膨胀部段62B以及设置在膨胀部段相反两侧的第一缩窄部段64B和第二缩窄部段66B，其中,膨胀部段62B的流体流通截面面积可以大于第一缩窄部段64B和第二缩窄部段66B中的每一者的流体流通截面面积。并且，第一缩窄部段64B的中心轴线与第二缩窄部段66B的中心轴线是错开的。在根据本公开的第二实施方式的定涡旋中，由于第一缩窄部段64B的中心轴线与第二缩窄部段66B的中心轴线错开，因此，流体在背压通道60B中将会产生更多的绕流，使得流体受到的流动阻力更大，从而进一步提高背压腔压力的稳定性，并且进一步减小流体回灌压缩腔导致重复压缩的风险，由此提高涡旋压缩机性能。图4还示出了分隔件的替选的实施方式，分隔件80B可以包括允许流体流动穿过的通孔82B以及阻挡流体流动的阻挡部84B。通孔82B可以为形成在分隔件80B中心的单个通孔。The fixed scroll back pressure passage 60B according to the second embodiment of the present disclosure may include an expansion section 62B and first and second constriction sections 64B and 66B disposed on opposite sides of the expansion section, wherein , the fluid flow cross-sectional area of the expansion section 62B may be larger than the fluid flow cross-sectional area of each of the first narrowing section 64B and the second narrowing section 66B. Moreover, the central axis of the first narrowing section 64B and the central axis of the second narrowing section 66B are staggered. In the fixed scroll according to the second embodiment of the present disclosure, since the central axis of the first narrowing section 64B is offset from the central axis of the second narrowing section 66B, the fluid in the back pressure passage 60B will Generating more flow around the fluid causes greater flow resistance, thereby further improving the stability of the pressure in the back pressure chamber and further reducing the risk of fluid backflow into the compression chamber causing repeated compression, thus improving scroll compressor performance. . Figure 4 also shows an alternative embodiment of a divider 80B that may include a through hole 82B that allows fluid flow therethrough and a barrier 84B that blocks fluid flow. The through hole 82B may be a single through hole formed in the center of the partition 80B.
图5为示出了根据本公开的第三实施方式的涡旋压缩机定涡旋的剖视图。根据本公开的第三实施方式的涡旋压缩机的定涡旋20C与上文描述的根据本公开的第一实施方式的涡旋压缩机的定涡旋20A的结构类似，其不同之处仅在于背压通道的结构不同，以下将仅对其不同之处进行详细描述。5 is a cross-sectional view showing a fixed scroll of the scroll compressor according to the third embodiment of the present disclosure. The fixed scroll 20C of the scroll compressor according to the third embodiment of the present disclosure is similar in structure to the fixed scroll 20A of the scroll compressor according to the first embodiment of the present disclosure described above, and the only difference is that The structure of the back pressure channel is different, and only the differences will be described in detail below.
根据本公开的第三实施方式的定涡旋的偏压通道60C可以包括多个膨胀部段以及设置在每个膨胀部段相反两侧的缩窄部段，其中,膨胀部段的流体流通截面面积可以大于缩窄部段中的每一者的流体流通截面面积。流体在背压通道60C中经过多次节流，使得流体受到的流动阻力更大，从而进一步提高背压腔压力的稳定性，并且进一步减小流体回灌压缩腔导致重复压缩的风险，由此提高涡旋压缩机性能。The fixed scroll bias passage 60C according to the third embodiment of the present disclosure may include a plurality of expansion sections and narrowing sections disposed on opposite sides of each expansion section, wherein a fluid flow cross-section of the expansion section The area may be greater than the fluid flow cross-sectional area of each of the narrowed sections. The fluid undergoes multiple throttling in the back pressure channel 60C, causing the fluid to encounter greater flow resistance, thereby further improving the stability of the pressure in the back pressure chamber and further reducing the risk of fluid backflow into the compression chamber causing repeated compression. Improve scroll compressor performance.
在以上描述的实施方式中，通过利用设置在定涡旋中的背压通道来提高背压腔压力的稳定性并且减小由于流体回灌压缩腔而导致流体重复压缩的风险， 从而提高了涡旋压缩机的性能。然而，本领域技术人员可以想到的是，也可以将具有二次节流效应的背压通道设置在动涡旋端板中来实现同样的目的，即，背压通道可以延伸穿过动涡旋端板以与形成在动涡旋一侧的背压腔连通。具体地，背压腔可以形成在主轴承座50内的空间中并且经由形成在动涡旋端板中的背压通道与一系列压缩腔中的一个压缩腔流体连通。另外，虽然本申请的示例性实施方式中示出了缩窄部段具有均匀的截面形状，但是本领域技术人员可以理解的是，缩窄部段也可以具有任何其他合适的形状，例如渐缩的V形形状等。In the above-described embodiment, by utilizing the back-pressure channel provided in the fixed scroll to improve the stability of the back-pressure chamber pressure and reduce the risk of repeated compression of the fluid due to fluid backflow into the compression chamber, This improves the performance of the scroll compressor. However, those skilled in the art can imagine that a back-pressure channel with a secondary throttling effect can also be provided in the movable scroll end plate to achieve the same purpose, that is, the back-pressure channel can extend through the movable scroll. The end plate communicates with the back pressure chamber formed on one side of the orbiting scroll. Specifically, a back pressure chamber may be formed in a space within the main bearing housing 50 and be in fluid communication with one of the series of compression chambers via a back pressure passage formed in the orbiting scroll end plate. In addition, although the exemplary embodiments of the present application show that the narrowing section has a uniform cross-sectional shape, those skilled in the art will understand that the narrowing section can also have any other suitable shape, such as a tapered shape. V-shaped shape, etc.
虽然已经参照示例性实施方式对本公开进行了描述，但是应当理解，本公开并不局限于文中详细描述和示出的具体实施方式，在不偏离权利要求书所限定的范围的情况下，本领域技术人员可以对示例性实施方式做出各种改变。还应理解的是，在技术方案不矛盾的情况下，各个实施方式的特征可以相互结合或者可以省去。 While the present disclosure has been described with reference to exemplary embodiments, it is to be understood that the present disclosure is not limited to the specific embodiments described and illustrated in detail herein, without departing from the scope defined by the claims. Various changes may be made to the exemplary embodiments by skilled artisans. It should also be understood that, provided that the technical solutions are not inconsistent, features of various embodiments may be combined with each other or may be omitted.

Claims (10)

  1. 一种压缩机构，包括：A compression mechanism including:
    定涡旋(20A，20B，20C)，所述定涡旋是一体式部件并且包括一体形成的定涡旋端板(22)以及定涡旋叶片(24)，所述定涡旋叶片形成在所述定涡旋端板的第一侧；Fixed scroll (20A, 20B, 20C), the fixed scroll is an integral component and includes an integrally formed fixed scroll end plate (22) and a fixed scroll blade (24), which is formed on The first side of the fixed scroll end plate;
    动涡旋(30)，所述动涡旋(30)包括动涡旋端板(32)和形成在所述动涡旋端板(32)的第一侧的动涡旋叶片(34)，并且所述定涡旋叶片(24)与所述动涡旋叶片(34)相互接合以在其间形成一系列能够对流体进行压缩的压缩腔；以及An orbiting scroll (30), which includes an orbiting scroll end plate (32) and an orbiting scroll blade (34) formed on a first side of the orbiting scroll end plate (32), And the fixed scroll blade (24) and the orbiting scroll blade (34) are engaged with each other to form a series of compression chambers capable of compressing fluid; and
    背压腔(70)，所述背压腔(70)通过背压通道(60A，60B，60C)与所述一系列压缩腔中的一个压缩腔流体连通以施加使得所述动涡旋(30)与所述定涡旋(20A，20B，20C)接合的背压力；A back pressure chamber (70) is in fluid communication with one of the series of compression chambers through a back pressure passage (60A, 60B, 60C) to exert the movable scroll (30) ) The back pressure that engages the fixed scroll (20A, 20B, 20C);
    其特征在于，所述背压通道(60A，60B，60C)包括膨胀部段(62A，62B)以及形成在所述膨胀部段(62A，62B)相反两侧的缩窄部段(64A，66A；64B，66B)，所述膨胀部段的流体流通截面面积大于所述缩窄部段的每一者的流体流通截面面积。It is characterized in that the back pressure channel (60A, 60B, 60C) includes an expansion section (62A, 62B) and a narrowing section (64A, 66A) formed on opposite sides of the expansion section (62A, 62B). ; 64B, 66B), the fluid flow cross-sectional area of the expansion section is greater than the fluid flow cross-sectional area of each of the narrowing sections.
  2. 根据权利要求1所述的压缩机构，其中，所述缩窄部段(64B，66B)中的一个缩窄部段的中心轴线与所述缩窄部段(64B，66B)中的另一个缩窄部段的中心轴线错开。The compression mechanism of claim 1, wherein a central axis of one of the narrowed sections (64B, 66B) is aligned with the other of the narrowed sections (64B, 66B). The central axes of the narrow sections are staggered.
  3. 根据权利要求1所述的压缩机构，其中，所述背压通道(60C)包括两个或更多个所述膨胀部段，并且所述膨胀部段中的每一者的相反两侧均形成有缩窄部段。The compression mechanism of claim 1, wherein the back pressure passage (60C) includes two or more expansion sections, and opposite sides of each of the expansion sections are formed There is a narrowing section.
  4. 根据权利要求1-3中的任一项所述的压缩机构，其中，所述背压通道(60A，60B，60C)形成在所述定涡旋端板(22)中且延伸穿过所述定涡旋端板，所述定涡旋还包括定涡旋毂部，所述定涡旋毂部形成在所述定涡旋端板的与所述第一侧相反的第二侧，所述定涡旋毂部包括第一环形毂部(26)和第二环形毂部(28)，所述背压腔(70)由所述定涡旋端板(22)、所述第一环形毂 部(26)和所述第二环形毂部(28)围绕的空间构成。The compression mechanism according to any one of claims 1-3, wherein the back pressure passage (60A, 60B, 60C) is formed in the fixed scroll end plate (22) and extends through the a fixed scroll end plate, the fixed scroll further comprising a fixed scroll hub formed on a second side of the fixed scroll end plate opposite to the first side, the The fixed scroll hub includes a first annular hub (26) and a second annular hub (28). The back pressure chamber (70) is composed of the fixed scroll end plate (22), the first annular hub (26) and the space surrounded by the second annular hub (28).
  5. 根据权利要求4所述的压缩机构，其中，所述背压通道(60A，60B，60C)包括敞开至所述一个压缩腔的第一缩窄部段(64A，64B)以及敞开至所述背压腔的第二缩窄部段(66A，66B)，所述定涡旋端板的相反两侧加工有连通的第一钻孔和第二钻孔，所述第二钻孔的孔径大于所述第一钻孔的孔径并且所述第二钻孔具有敞开至所述背压腔的端部，所述端部安装有分隔件(80A，80B)，所述分隔件包括允许流体流动穿过的通孔(82A，82B)以及阻挡流体流动的阻挡部(84A，84B)，所述第一缩窄部段(64A，64B)由所述第一钻孔形成，所述第二缩窄部段(66A，66B)由所述通孔形成，所述膨胀部段(62A，62B)由所述第二钻孔的未安装所述分隔件的部分形成。The compression mechanism of claim 4, wherein the back pressure passage (60A, 60B, 60C) includes a first constriction section (64A, 64B) opening to the one compression chamber and a first constriction section (64A, 64B) opening to the back pressure passage. In the second narrowed section (66A, 66B) of the pressure chamber, connected first boreholes and second boreholes are processed on opposite sides of the fixed scroll end plate, and the aperture of the second borehole is larger than that of the fixed scroll end plate. The first borehole has an aperture and the second borehole has an end open to the back pressure chamber, the end is mounted with a divider (80A, 80B), the divider includes a structure that allows fluid flow therethrough through holes (82A, 82B) and blocking portions (84A, 84B) that block fluid flow, the first narrowing section (64A, 64B) is formed by the first drilled hole, and the second narrowing portion Segments (66A, 66B) are formed by said through-holes and said expansion sections (62A, 62B) are formed by portions of said second boreholes where said partitions are not mounted.
  6. 根据权利要求5所述的压缩机构，其中，所述分隔件(80A，80B)可拆卸地安装至所述第二钻孔的所述端部，并且所述分隔件(80A)包括间隔开的多个通孔(82A)或者所述分隔件(80B)包括位于其中心的单个通孔(82B)。The compression mechanism of claim 5, wherein said dividers (80A, 80B) are removably mounted to said ends of said second boreholes, and said dividers (80A) include spaced apart The plurality of through holes (82A) or the partition (80B) includes a single through hole (82B) at its center.
  7. 根据权利要求1至3的任一项所述的压缩机构，其中，所述背压通道形成在所述动涡旋端板中且延伸穿过所述动涡旋端板，所述背压腔形成在所述动涡旋端板的与所述第一侧相反的第二侧。The compression mechanism according to any one of claims 1 to 3, wherein the back pressure passage is formed in the orbiting scroll end plate and extends through the orbiting scroll end plate, and the back pressure chamber formed on a second side of the orbiting scroll end plate opposite to the first side.
  8. 根据权利要求1至3中的任一项所述的压缩机构，其中，所述膨胀部段的轴向长度大于所述缩窄部段的每一者的轴向长度。The compression mechanism of any one of claims 1 to 3, wherein the axial length of the expansion section is greater than the axial length of each of the narrowing sections.
  9. 根据权利要求1至3中的任一项所述的压缩机构，其中，所述缩窄部段中的每一者具有相同的流通截面面积，所述膨胀部段的流体流通截面面积处于所述缩窄部段的流通截面面积的1.1至1.5倍的范围内，或者，The compression mechanism according to any one of claims 1 to 3, wherein each of the narrowing sections has the same flow cross-sectional area, and the fluid flow cross-sectional area of the expansion section is between the Within the range of 1.1 to 1.5 times the flow cross-sectional area of the narrowing section, or,
    所述缩窄部段分别具有不同的流体流通截面面积，所述膨胀部段的流体流通截面面积处于所述缩窄部段的最大流体流通截面面积的1.1至1.5倍的范围内。 The narrowed sections respectively have different fluid flow cross-sectional areas, and the fluid flow cross-sectional area of the expansion section is in a range of 1.1 to 1.5 times the maximum fluid flow cross-sectional area of the narrowed section.
  10. 一种涡旋压缩机，其特征在于，所述涡旋压缩机包括根据权利要求1至9中的任一项所述的压缩机构。 A scroll compressor, characterized in that the scroll compressor includes the compression mechanism according to any one of claims 1 to 9.
PCT/CN2023/111415 2022-08-08 2023-08-07 Compression mechanism and scroll compressor WO2024032534A1 (en)

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CN202210944867.7 2022-08-08
CN202222076401.8U CN218030611U (en) 2022-08-08 2022-08-08 Compression mechanism and scroll compressor
CN202222076401.8 2022-08-08
CN202210944867.7A CN117570019A (en) 2022-08-08 2022-08-08 Compression mechanism and scroll compressor

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0526179A (en) * 1991-07-19 1993-02-02 Mitsubishi Heavy Ind Ltd Scroll type fluid machine
JPH05157063A (en) * 1991-12-03 1993-06-22 Mitsubishi Heavy Ind Ltd Scroll type fluid machine
CN109306959A (en) * 2018-11-26 2019-02-05 珠海格力节能环保制冷技术研究中心有限公司 A kind of back pressure cavity structure of voltage regulation and the screw compressor with it
CN110541821A (en) * 2019-09-11 2019-12-06 珠海格力电器股份有限公司 Compressor and refrigerating unit with effect of reducing air supply pressure drop
CN113931842A (en) * 2020-06-29 2022-01-14 艾默生环境优化技术(苏州)有限公司 Scroll compression mechanism and scroll compressor
CN218030611U (en) * 2022-08-08 2022-12-13 艾默生环境优化技术(苏州)有限公司 Compression mechanism and scroll compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0526179A (en) * 1991-07-19 1993-02-02 Mitsubishi Heavy Ind Ltd Scroll type fluid machine
JPH05157063A (en) * 1991-12-03 1993-06-22 Mitsubishi Heavy Ind Ltd Scroll type fluid machine
CN109306959A (en) * 2018-11-26 2019-02-05 珠海格力节能环保制冷技术研究中心有限公司 A kind of back pressure cavity structure of voltage regulation and the screw compressor with it
CN110541821A (en) * 2019-09-11 2019-12-06 珠海格力电器股份有限公司 Compressor and refrigerating unit with effect of reducing air supply pressure drop
CN113931842A (en) * 2020-06-29 2022-01-14 艾默生环境优化技术(苏州)有限公司 Scroll compression mechanism and scroll compressor
CN218030611U (en) * 2022-08-08 2022-12-13 艾默生环境优化技术(苏州)有限公司 Compression mechanism and scroll compressor

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