WO2022021644A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

Info

Publication number
WO2022021644A1
WO2022021644A1 PCT/CN2020/124647 CN2020124647W WO2022021644A1 WO 2022021644 A1 WO2022021644 A1 WO 2022021644A1 CN 2020124647 W CN2020124647 W CN 2020124647W WO 2022021644 A1 WO2022021644 A1 WO 2022021644A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
oil
end plate
oil supply
scroll compressor
Prior art date
Application number
PCT/CN2020/124647
Other languages
English (en)
French (fr)
Inventor
刘轩
秦岩
张琼宇
刘畅
Original Assignee
艾默生环境优化技术(苏州)有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN202010732802.7A external-priority patent/CN114001031A/zh
Priority claimed from CN202021511823.8U external-priority patent/CN212536075U/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 WO2022021644A1 publication Critical patent/WO2022021644A1/zh

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the present disclosure relates to a scroll compressor.
  • the rotation of the orbiting scroll is used to make the hub of the orbiting scroll alone, or the hub of the orbiting scroll. Agitates the lubricating oil formed in the oil pool at the bottom of the main bearing housing with other additional components, so that it splashes and lubricates the thrust surface between the scroll and the main bearing, or between the scroll and the thrust assembly thrust surface.
  • the aforementioned oil sump can flow back to the base of the scroll compressor. Therefore, when the scroll compressor starts up again, it takes a certain amount of time to raise the oil level in the oil pool to the height where the hub of the movable scroll or the balance weight can stir the oil. During this time, the thrust surface is lubricated. Poor conditions can easily lead to early wear failure of the thrust surface.
  • An object of the present disclosure is to provide a scroll compressor that overcomes the above-mentioned drawbacks in the prior art.
  • the present disclosure relates to a scroll compressor including a fixed scroll including a fixed scroll end plate, a fixed helical wrap extending from a side of the fixed scroll end plate, and The discharge port arranged in the fixed scroll end plate; the movable scroll member, the movable scroll member includes the movable scroll end plate, the orbiting spiral wrap extending from one side of the driven scroll end plate and the driven scroll end plate
  • the hub protruding from the opposite side of the orbiting helical scroll, the orbiting helical scroll engages with the fixed helical scroll in a meshing manner, thereby creating a fluid cavity for compressing the working fluid
  • the supporting assembly, the orbiting scroll end plate slides supported on a bearing assembly, the bearing assembly and the orbiting scroll end plate each having thrust surfaces in sliding contact with each other; and a drive assembly including a shaft for driving the hub, wherein the hub is provided with an oil supply passage , so that the lubricating oil in the hub is sprayed to the thrust surface through the oil supply channel.
  • oil passages are provided in the shaft for supplying lubricating oil into the hub.
  • the oil supply passage is positioned adjacent the orbiting scroll end plate.
  • a throttling device is provided in the oil supply channel, and a through oil passage hole is provided in the throttling device, and the lubricating oil is sprayed to the thrust surface through the oil passage hole.
  • the throttling device is a throttling screw
  • the oil supply passage is provided with a threaded hole that engages with the throttling screw.
  • the oil supply passage includes a sloped section that directs lubricating oil to the thrust surface.
  • the scroll compressor further includes an oil slinger disposed between the hub portion and the bearing assembly, the oil slinger ring positioned axially below the oil supply passage and secured to the hub portion, the oil slinger ring having the ability to transport lubricating oil Inclined guide surface leading towards the thrust surface.
  • the scroll compressor further includes an intermediate member disposed between the hub portion and the bearing assembly, wherein the intermediate member has a top portion proximate the orbiting scroll end plate, and the oil supply passage is disposed to correspond to the top portion of the intermediate member and the area between the orbiting scroll end plate.
  • the top of the intermediate member has a sloped surface that directs lubricating oil toward the thrust surface, and/or the top of the intermediate member is provided with a plurality of involute oil grooves that direct lubricating oil toward the thrust surface.
  • the scroll compressor further includes: a drive bushing that fits radially outboard of the eccentric crankpin of the shaft; and a counterweight member including a drive bushing connected to the drive bushing or the shaft A mounting base and a counterweight portion extending axially from the mounting base; wherein the counterweight portion constitutes an intermediate member.
  • the scroll compressor according to the present disclosure uses the oil supply channel to perform forced splash lubrication on the thrust surface, which can effectively reduce the early wear failure of the thrust surface caused by a short oil shortage when the scroll compressor starts up; When the scroll compressor is running at a low speed, the splash lubrication of the oil is insufficient.
  • the present disclosure is especially suitable for a high-speed variable frequency compressor with a balance weight component, and the lubrication state of its thrust surface can be significantly improved through splash lubrication.
  • the axial position of the oil supply passage of the present disclosure needs to be as close to the thrust surface as possible.
  • FIG. 1 is a cross-sectional view of a prior art scroll compressor
  • FIG. 2 shows a partial cross-sectional view of a hub of an orbiting scroll provided with oil supply passages and its peripheral components of a scroll compressor according to the present disclosure
  • Figure 3 shows a top sectional view taken along the axis of the oil supply channel shown in Figure 2;
  • Fig. 4 shows a partial cross-sectional view of the hub portion of the orbiting scroll shown in Fig. 2 with a throttle screw disposed in the oil supply passage;
  • FIG. 5 shows a partial enlarged cross-sectional view of the oil supply channel shown in FIG. 4 provided with the throttle screw;
  • FIG. 6 shows an assembled perspective view of an oil slinger mounted on the hub of the orbiting scroll of the scroll compressor according to the present disclosure
  • Figure 7 shows an exploded perspective view of the oil slinger of Figure 6
  • FIG. 8 shows a partial cross-sectional view of the oil slinger of FIG. 6 mounted on the hub of the orbiting scroll shown in FIG. 2;
  • Fig. 9 shows a partial enlarged cross-sectional view of the hub portion shown in Fig. 8 with the oil slinger installed;
  • Figure 10 shows a perspective view of a balance weight member provided with an inclined surface on top
  • Figure 11 is a partial cross-sectional view of the balance weight member shown in Figure 10 installed around the hub;
  • Figure 12 shows a perspective view of a balance weight component provided with an involute oil groove at the top
  • Figure 13 shows a top view of a balance weight component provided with an involute oil groove at the top;
  • Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods in order to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and should not be construed to limit the scope of the disclosure. In some example embodiments, well-known methods, well-known device structures, and well-known technologies are not described in detail.
  • first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by These terms are restricted. These terms may only be used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as “first,” “second,” and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.
  • scroll compressor 10 is shown as a low-pressure side-type hermetic scroll refrigeration compressor (ie, a compressor in which the motor is positioned in the suction pressure region of the compressor), as shown in FIG. 1 .
  • low-pressure side-type hermetic scroll refrigeration compressor ie, a compressor in which the motor is positioned in the suction pressure region of the compressor
  • high side compressors ie, compressors in which the motor is positioned in the discharge pressure region of the compressor.
  • FIG. 1 shows a prior art scroll compressor 10 .
  • the scroll compressor 10 may include a sealed housing assembly 12, a bearing block assembly 14, a drive assembly 16, a compression mechanism 18, and the like.
  • Bearing block assembly 14 , drive assembly 16 and compression mechanism 18 may be housed in housing assembly 12 .
  • the casing assembly 12 may generally form a compressor casing and may include a cylindrical casing 26 , an end cap 28 at an upper end of the cylindrical casing 26 , a transversely extending divider 30 , and a lower end of the cylindrical casing 26 to A bottom cover (not shown) forms the base of the vertical scroll compressor 10 .
  • End cap 28 and divider 30 may generally define discharge chamber 34 .
  • the housing 26 , the divider 30 and the bottom cover may generally define a suction chamber 40 .
  • Suction inlet fitting 38 may be attached to barrel housing 26 of housing assembly 12 and may communicate with suction chamber 40 .
  • Divider 30 may include a discharge passage 42 via which compression mechanism 18 communicates with discharge chamber 34 .
  • the bearing adapter assembly 14 may be attached to the housing assembly 12 (specifically the housing 26 in the figures) and may include a main bearing adapter 44 and a bearing 46 housed in the main bearing adapter 44 .
  • the drive assembly 16 may include a stator (not shown), a rotor (not shown), and a shaft 54 .
  • the stator may be press fit into the housing assembly 12 (specifically housing 26 in the figures).
  • the rotor can be attached to the shaft 54 and can rotatably drive the shaft 54 .
  • the shaft 54 may be rotatably supported by the main bearing block 44 via the bearing 46 near the upper end. Lubricating oil is accommodated in the bottom cover.
  • a through oil passage 52 (as shown in FIG. 2 ) is provided in the shaft 54 for sucking the lubricating oil contained in the base from the lower end of the shaft 54 to the upper end of the shaft 54 through the oil passage 52 .
  • the compression mechanism 18 may generally include an orbiting scroll 58 and a fixed scroll 60 .
  • the orbiting scroll 58 may include an orbiting scroll end plate 62 , an orbiting spiral wrap 64 extending upwardly from the orbiting scroll end plate 62 .
  • the fixed scroll 60 may include a fixed scroll end plate 74 and a fixed spiral wrap 76 protruding downward from one side of the fixed scroll end plate 74 .
  • the orbiting wrap 76 of the fixed scroll 60 may meshingly engage the orbiting wrap 64 of the orbiting scroll 58 to create a series of moving fluid chambers.
  • the fixed wrap 76 may follow from the radially outer position (suction pressure) through the radially intermediate position (intermediate pressure) Moving to the radially inward position (at the discharge pressure) reduces the volume thereby compressing the working fluid.
  • the fixed scroll 60 includes a discharge port 77 located at the center of the fixed spiral wrap 76 for discharging the compressed working fluid.
  • the orbiting scroll end plate 62 of the orbiting scroll 58 may have a cylindrical hub 68 protruding downward.
  • the cylindrical hub 68 may have a drive bushing 70 rotatably disposed therein.
  • the shaft 54 may include an eccentric crank pin 56 (also referred to as an eccentric).
  • the crankpin 56 is drivingly engaged in the drive bush 70 . That is, the drive bush 70 is fitted on the radially outer side of the eccentric crank pin 56 of the shaft 54 .
  • Crank pin 56 may drivingly engage drive bushing 70 to provide radially flexible transmission.
  • the driving force generated by the driving assembly 16 is transmitted to the driving bushing 70 via the crank pin 56 of the shaft 54, and then transmitted to the cylindrical hub 68 of the orbiting scroll 58 by the driving bushing 70, thereby driving the orbiting scroll Piece 58 orbits.
  • the thrust assembly 48 is separately formed and disposed between the main bearing block 44 and the orbiting scroll 58 .
  • Thrust assembly 48 and main bearing block 44 constitute the bearing assembly described in this application. It should be understood that the thrust assembly 48 may be formed in one piece with the main bearing block 44, ie, the support assembly is one piece. In the absence of the thrust assembly 48, the main bearing block 44 constitutes the support assembly (FIG. 1).
  • the orbiting scroll 58 orbits relative to the fixed scroll 60 driven by the shaft 54 . Simultaneously, the orbiting scroll end plate 62 of the orbiting scroll 58 slides on the thrust assembly 48 . Accordingly, the orbiting scroll end plate 62 and the thrust assembly 48 respectively include thrust surfaces 63, 49 in sliding contact with each other.
  • a balance weight member 72 is also provided between the hub portion 68 of the orbiting scroll 58 and the thrust assembly 48 .
  • the lubricating oil flows up to the top surface of the eccentric crank pin 56 through the oil passage 52 in the shaft 54 under the action of centrifugal force, and then flows down along the outer peripheral surface of the eccentric crank pin 56 to irrigate the drive bushing
  • the sleeve 70 is lubricated and then accumulates in the bottom of the main bearing housing 44 to form the oil sump 47 (FIG. 1).
  • the hub 68 of the orbiting scroll 58 (along with the counterweight member 72 in this example) agitates the lubricating oil in the sump, splashing the lubricating oil onto the thrust assembly 48 and the orbiting scroll end of the orbiting scroll 58 between the plates 62 to lubricate the thrust assembly 48 and the thrust surfaces of the orbiting scroll end plate 62 .
  • the oil level in the oil sump 47 needs to reach a height at which the hub 68 or the balance weight member 72 can agitate.
  • the scroll compressor After the scroll compressor is started, it takes a period of time to accumulate lubricating oil so that the oil level in the oil sump 47 reaches a sufficient height to be agitated by the hub 68 or the balance weight member 72 and to allow the agitated lubricating oil to splash To the orbiting scroll end plate 62 and the thrust surface of the thrust assembly 48 .
  • At least one oil supply passage 66 is provided on the hub portion 68 of the orbiting scroll 58.
  • two or more oil supply passages 66 are provided.
  • the oil supply passage 66 is provided on the side of the hub portion 68 of the orbiting scroll 58 close to the orbiting scroll end plate 62 of the orbiting scroll 58 . As shown by the arrows in FIGS.
  • the lubricating oil is pumped from the base of the scroll compressor 10 to the top of the shaft 54 via the oil passage 52 of the shaft 54 (the end face of the shaft 54 and the orbiting scroll of the orbiting scroll 58 ) between the end plates 62), under the action of the oil pressure and the centrifugal force generated by the rotation of each component, the lubricating oil inside the hub 68 is thrown out to the outside of the hub 68 through the oil supply passage 66, and splashes onto the orbiting scroll 58 at the orbiting scroll end plate 62 and the thrust surface of the thrust assembly 48 .
  • the lubricating oil can be sprayed onto the thrust surfaces significantly faster than by the hub 68 and/or the balance weight member 72 which agitates the oil sump of a predetermined height at the bottom of the main bearing housing . This is because there is no need to wait for the scroll compressor 10 to operate for a period of time so that the liquid level in the oil pool formed at the bottom of the main bearing seat 44 reaches a certain height before the thrust surface can be lubricated by splashing lubricating oil. Therefore, the lubricating oil is supplied to the thrust surface as soon as possible through the oil supply passage 66, thereby preventing the early wear failure of the thrust surface.
  • the lubricating oil can be supplied to the thrust surface as quickly as possible through the oil supply passage 66, thereby improving the agitation of the lubricating oil by the hub portion 68 and/or the balance weight member 72 that is too low to When enough lubricant is sprayed onto the thrust surface.
  • the lubricating oil splashed through the oil supply channel 66 will still flow back to the oil pool 47, and after the oil level reaches a certain height, it can still be stirred by the hub 68 and/or the balance weight member 72 and splashed to the thrust surface and lubricate the thrust surfaces. Therefore, this arrangement does not interfere with the original system of agitating the oil through the hub 68 and/or the counterweight member 72 so that it splashes onto and lubricates the thrust surfaces.
  • the oil supply passage 66 may be adjacent to the orbiting scroll end plate 62 of the orbiting scroll 58 . Disposed, ie, disposed adjacent to the orbiting scroll end plate 62 of the orbiting scroll 58 and the thrust surface of the thrust assembly 48 . Also, as shown in FIG. 3 , the oil supply passage 66 extends in the radial direction. Alternatively, those skilled in the art may contemplate that the oil supply passage 66 may extend in other directions, such as deflected in a rotational direction or inclined in an axial direction, to facilitate centrifugal forces to throw oil against the thrust surface.
  • the axial position of the oil supply passage 66 may be set higher than the top of the balance weight member 72 .
  • the amount of fuel sprayed through the fuel supply passage 66 can be varied by the size of the diameter of the fuel supply passage 66 .
  • a throttle device may be provided in the fuel supply passage 66 , and a through oil passage hole may be provided in the throttle device.
  • the throttle device is a throttle screw 80
  • a threaded hole 78 is provided in the oil supply passage 66 .
  • the threaded hole 78 is matched with the throttle screw 80 .
  • An oil passage hole 82 penetrating in the axial direction is provided in the center of the throttle screw 80 .
  • the fuel injection amount can be adjusted by changing the diameter of the oil passage hole 82 of the throttle screw 80 .
  • Using the throttle screw 80 can simplify the processing of the oil supply passage 66 and further simplify the processing of the movable scroll member 58 . According to different types of compressors, only the corresponding throttle screw 80 needs to be replaced. In addition, when the oil supply passage 66 is machined on the hub portion 68, if the diameter of the oil supply passage 66 is too small, it is difficult to machine. By using the throttle screw 80 , the problem of machining the oil supply passage 66 with a small diameter on the hub portion 68 can be better resolved.
  • the structure of the oil supply passage 66 itself can be improved.
  • the oil supply passage 66 may include a sloped section that sprays lubricating oil toward the orbiting scroll end plate 62 and the thrust surface of the thrust assembly 48 .
  • a radial direction of the oil supply channel 66 around the hub 68 may be provided.
  • An oil slinger 84 is disposed between the hub portion 68 and the thrust assembly 48 and is secured to the hub portion 68 below the oil supply passage 66 .
  • the slinger 84 may have sloped guide surfaces 85 (ie, within the tapered truncated) that direct oil toward the orbiting scroll end plate 62 and the thrust surfaces of the thrust assembly 48 . conical surface).
  • the lubricating oil is directed to be sprayed onto the thrust surface by the inclined (or tapered) guide surface 85 .
  • the oil slinger 84 may be a circular ring formed by hinged or snap-connected two semi-circular rings. The two half-circles of the slinger 84 are connected together by, for example, pinning or snapping together after being mounted on the hub 68 of the orbiting scroll 58 .
  • the oil sprayed from the oil supply passage 66 is guided by the inclined (or tapered) guide surface 85 of the oil slinger 84 to spray the oil onto the thrust surface.
  • the generally bowl-shaped oil throwing ring 84 can function as a small oil pool, which is beneficial to throw the oil onto the thrust surface more evenly.
  • the balance weight member 72 includes a mounting base 73 connected to the drive bushing 70 (which may also be connected to the shaft 54 ) and a weight portion 75 extending axially from the mounting base 73 .
  • the weight portion extends in the axial direction between the hub portion 68 and the thrust assembly 48 , and constitutes an intermediate member disposed between the hub portion 68 of the orbiting scroll 58 and the thrust assembly 48 .
  • the balance weight member 72 also has a top portion 79 proximate the orbiting scroll end plate 62 .
  • the general configuration of the balance weight member 72 is generally known in the art.
  • the top portion 79 of the counterweight member 72 may have a sloped surface 86 for better oil splashing onto the thrust surfaces.
  • This inclined surface 86 is located radially outside of the oil supply passage 66 around the hub 68 .
  • the oil supply passage 66 is positioned to correspond to the area between the top portion 79 of the balance weight member 72 and the orbiting scroll end plate 62 so that the oil supply passage 66 will be sprayed from the oil supply passage 66 using the inclined surface 86 of the top portion 79 of the balance weight member 72 . Spilled oil is directed to the thrust surface.
  • the inclined surface 86 can also prevent the oil supply passage 66 from being blocked due to the up-and-down movement of the balance weight member 72 .
  • a plurality of involute oil grooves 88 may be provided on the top portion 79 of the balance weight member 72 . Utilizing the involute oil grooves 88 can more effectively direct lubricating oil toward the end plate 68 and the thrust surfaces of the thrust assembly 48 .
  • the present disclosure uses the oil supply channel to perform forced splash lubrication on the thrust surface, which can effectively reduce the early wear failure of the thrust surface caused by a short oil shortage when the scroll compressor is started; When the machine is running at low speed, the oil splashing and lubrication are insufficient.
  • the present disclosure is especially suitable for a high-speed variable frequency compressor with a balanced counterweight component, and its thrust surface lubrication state can be significantly improved through splash lubrication.

Abstract

一种涡旋压缩机，包括：定涡旋件（60），定涡旋件（60）包括定涡旋端板（74）、从定涡旋端板（74）的一侧延伸的定螺旋涡卷（76）以及设置在定涡旋端板（74）中的排出口（77）；动涡旋件（58），动涡旋件（58）包括动涡旋端板（62）、从动涡旋端板（62）的一侧延伸的动螺旋涡卷（64）以及从动涡旋端板（62）的与动螺旋涡卷（64）相反的一侧突出的毂部（68），动螺旋涡卷（64）与定螺旋涡旋（76）以啮合的方式接合，从而产生用于压缩工作流体的流体腔；支承组件，动涡旋端板（62）滑动支承在支承组件上，支承组件和动涡旋端板（62）各自具有彼此滑动接触的止推面（63、49）；以及驱动组件（16），驱动组件（16）包括用以驱动毂部（68）的轴（54），其中，在毂部（68）上设置有供油通道（66），使得毂部（68）内的润滑油经由供油通道（66）喷溅至止推面（63、49）。这种涡旋压缩机能够有效降低压缩机启动时，短暂缺油造成的止推面早期磨损失效并显著改善止推面润滑状态。

Description

涡旋压缩机
本申请要求以下中国专利申请的优先权：于2020年07月27日提交国家知识产权局的申请号为202010732802.7、发明创造名称为“涡旋压缩机”的中国专利申请；于2020年07月27日提交国家知识产权局的申请号为202021511823.8、发明创造名称为“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。
技术领域
本公开涉及一种涡旋压缩机。
背景技术
本部分提供与本公开相关的背景信息，而本部分不一定是现有技术。
在涡旋压缩机的运行过程中，为了确保流体腔密封从而对工作流体进行有效压缩，需要在轴向上施加较大的载荷。作用在涡旋件上的轴向载荷最终由主轴承座、或者设置于涡旋件与主轴承座之间的止推组件承受。所以涡旋件与主轴承座或者止推组件之间的止推面需要良好的润滑。
无论是设置有主轴承座还是附加地设置有止推组件的涡旋压缩机，都是利用动涡旋件的转动，使动涡旋件的毂部单独地、或者动涡旋件的毂部与其他附加部件一起搅动形成于主轴承座底部的油池中的润滑油，使其飞溅至并润滑涡旋件与主轴承座之间的止推面、或者涡旋件和止推组件之间的止推面。
在利用上述方式进行飞溅润滑的情况下，当涡旋压缩机的转速较低时，搅起的油量比较少，而造成止推面润滑不足。在设置有止推组件的情况下，止推组件的径向延伸面会将飞溅的部分油挡住，进一步降低了止推面润滑量。另外，在设置于涡旋压缩机的驱动组件的轴的顶端处的偏心曲柄销外侧设置有驱动衬套并且在驱动衬套上设置有例如平衡配重部件的情况下，该平衡配重部件也可能会遮挡部分溅油区域，更不利于飞溅润滑。此外，在压缩机停机后，上述油池会流回涡旋压缩机的基部。所以，当涡旋压缩机再次启动时，需要一定时间才能把油池液位提升到动涡旋件的毂部或平衡配重部件能够搅油的高度，在这段时间内，止推面润滑条件较差，容易造成止推面早期磨损失效。
发明内容
本部分提供本公开的总体概述，而不是本公开的全部范围或其所有特征的全面公开。
本公开的目的在于提供一种涡旋压缩机，该涡旋压缩机克服了现有技术中的上述缺陷。
在一种形式中，本公开涉及一种涡旋压缩机，包括：定涡旋件，定涡旋件包括定涡旋端板、从定涡旋端板的一侧延伸的定螺旋涡卷以及设置在定涡旋端板中的排出口；动涡旋件，动涡旋件包括动涡旋端板、从动涡旋端板的一侧延伸的动螺旋涡卷以及从动涡旋端板的与动螺旋涡卷相反的一侧突出的毂部，动螺旋涡卷与定螺旋涡旋以啮合的方式接合，从而产生用于压缩工作流体的流体腔；支承组件，动涡旋端板滑动支承在支承组件上，支承组件和动涡旋端板各自具有彼此滑动接触的止推面；以及驱动组件，驱动组件包括用以驱动毂部的轴，其中，在毂部上设置有供油通道，使得毂部内的润滑油经由供油通道喷溅至止推面。
在一些形式中，在轴中设置有用于将润滑油供给至毂部内的油道。
在一些形式中，供油通道邻近动涡旋端板设置。
在一些形式中，供油通道有多个并且沿周向方向设置在毂部上，多个供油通道具有彼此相同的直径或者不同的直径。
在一些形式中，供油通道中设置有节流装置，节流装置中设置有贯通的通油孔，润滑油经由通油孔喷溅至止推面。
在一些形式中，节流装置为节流螺钉，供油通道中设置有与节流螺钉接合的螺纹孔。
在一些形式中，供油通道包括将润滑油引导至止推面的倾斜部段。
在一些形式中，涡旋压缩机还包括设置在毂部与支承组件之间的甩油环，甩油环位于供油通道的轴向下方并且固定至毂部上，甩油环具有将润滑油朝向止推面引导的倾斜的引导面。
在一些形式中，涡旋压缩机还包括设置在毂部与支承组件之间的中间构件，其中，中间构件具有靠近动涡旋端板的顶部，并且供油通道设置成对应于中间构件的顶部与动涡旋端板之间的区域。
在一些形式中，中间构件的顶部具有将润滑油朝向止推面引导的倾斜表面，和/或，中间构件的顶部上设置有将润滑油朝向止推面引导的多个渐开线油槽。
在一些形式中，涡旋压缩机还包括：驱动衬套，驱动衬套配合在轴的偏心曲柄销的径向外侧；以及平衡配重部件，平衡配重部件包括连接至驱动衬套或轴的安装基部以及从安装基部沿轴向延伸的配重部；其中，配重部构成了中间构件。
根据本公开的涡旋压缩机利用供油通道对止推面进行强制喷溅润滑，可以有效降低在涡旋压缩机启动时，短暂缺油所造成的止推面早期磨损失效；也可以改善在涡旋压缩机低速运行时，搅油飞溅润滑不充分的情况。本公开尤其适合带平衡配重部件的高速变频压缩机，通过喷溅润滑可显著改善其止推面润滑状态。本公开的供油通道的轴向位置需尽量靠近止推面。
根据本文提供的描述，其他应用领域将变得明显。本概述中的描述和具体示例仅用于说明的目的，而不意在限制本公开的范围。
附图说明
本文中描述的附图仅出于说明选定实施方式而非所有可能的实施方案的目的，而不意在限制本公开的范围。
图1是现有技术的涡旋压缩机的横截面图；
图2示出了根据本公开的涡旋压缩机的设置有供油通道的动涡旋件的毂部及其周边部件的局部截面图；
图3示出了沿图2所示的供油通道的轴线截取的俯视截面图；
图4示出了图2所示动涡旋件的毂部在供油通道中设置节流螺钉的局部截面图；
图5示出了图4所示设置有节流螺钉的供油通道的局部放大截面图；
图6示出了安装于根据本公开的涡旋压缩机的动涡旋件的毂部的甩油环的组装立体图；
图7示出了图6的甩油环的分解立体图；
图8示出了图6的甩油环安装于图2所示的动涡旋件的毂部的局部截面图；
图9示出了图8所示安装有甩油环的毂部的局部放大截面图；
图10示出了顶部设置有倾斜表面的平衡配重部件的立体图；
图11是图10所示平衡配重部件安装于毂部周围的局部截面图；
图12示出了在顶部设置有渐开线油槽的平衡配重部件的立体图；
图13示出了在顶部设置有渐开线油槽的平衡配重部件的俯视图；
贯穿附图中的若干视图，对应的附图标记指示对应的部件。
具体实施方式
现在将参照附图更充分地描述示例性实施方式。
提供了示例性实施方式以使得本公开将是透彻的并且将向本领域技术人员充分地传达范围。阐述了许多具体细节例如特定部件、装置和方法的示例，以提供对本公开的实施方式的透彻理解。对于本领域技术人员而言将明显的是，不需要采用具体细节，示例性实施方式可以以许多不同的形式来实施并且不应被解释为限制本公开的范围。在一些示例性实施方式中，对公知的方法、公知的装置结构和公知的技术不再进行详细描述。
当元件或层被提及为“位于另一元件或层上”、“接合至”、“连接至”或“联接至”另一元件或层时，元件或层可以直接位于其他元件或层上、接合至、连接至或联接至其他元件或层，或者可以存在中间元件或层。相反，当元件被提及为“直接位于另一元件或层上”、“直接接合至”、“直接连接至”或“直接联接至”另一元件或层时，不会存在中间元件或层。用以描述元件之间的关系的其他用语(例如“位于……之间”与“直接位于……之间”、“相邻”与“直接相邻”等)应当以相似的方式来解释。如本文中使用的，术语“和/或”包括相关列举项目中的一个或更多个项目的任何组合和全部组合。
尽管在本文中可以使用术语第一、第二、第三等来描述各种元件、部件、区域、层和/或部段，但是这些元件、部件、区域、层和/或部段不应当受这些术语限制。这些术语可以仅用于区分一个元件、部件、区域、层或部段与另一区域、层或部段。除非上下文明确表明，否则诸如“第一”、“第二”和其他数字术语之类的术语在本文中使用时并不意味着顺序或次序。因此，下面论述的第一元件、部件、区域、层或部段在不脱离示例性实施方式的教示的情况下可以被称为第二元件、部件、区域、层或部段。
本公开的原理适于结合在许多不同类型的设备、例如涡旋压缩机和旋转压缩机中，包括密封式机器、开放式驱动机器和非密封式机器。出于例示的目的，涡旋压缩机10被示出为低压侧型密封式涡旋制冷压缩机(即，马达设置在压缩机的抽吸压力区域中的压缩机)，如图1中所示。将理解的是，本公开的原理还适用于高压侧压缩机(即，马达设置在压缩机的排放压力区域中的压缩机)。
图1示出了现有技术的涡旋压缩机10。涡旋压缩机10可以包括密封的外壳组件12、轴承座组件14、驱动组件16和压缩机构18等。轴承座组件14、驱动组件16和压缩机构18可以容置在外壳组件12中。
外壳组件12可以大体上形成压缩机壳体，并且可以包括筒形外壳26、位于筒形外壳26的上端部处的端盖28、横向延伸的分隔部30以及位于筒形外壳26的下端部处以形成立式的涡旋压缩机10的基部的底盖(未示出)。端盖28和分隔部30可以大体上限定排放室34。外壳26、分隔部30和底盖可以大体上限定抽吸室40。吸气入口配件38可以附接至外壳组件12的筒形外壳26并且可以与抽吸室40连通。分隔部30可以包括排放通道42，压缩机构18经由排放通道42与排放室34连通。
轴承座组件14可以附接至外壳组件12(图中具体为外壳26)并且可以包括主轴承座44和容置在主轴承座44中的轴承46。
驱动组件16可以包括定子(未示出)、转子(未示出)和轴54。定子可以压配合到外壳组件12(图中具体为外壳26)中。转子可以附接在轴54上并且可以以可旋转的方式驱动轴54。轴54在靠近上端处可以经由轴承46由主轴承座44以可旋转的方式支承。在底盖中容纳有润滑油。在轴54中设置有贯通的油道52(如图2所示)，用以将容纳在基部中的润滑油从轴54的下端经由该油道52抽吸到轴54的上端。
压缩机构18可以大体上包括动涡旋件58和定涡旋件60。动涡旋件58可以包括动涡旋端板62、从动涡旋端板62向上延伸的动螺旋涡卷64。定涡旋件60可以包括定涡旋端板74和从定涡旋端板74的一侧向下突出的定螺旋涡卷76。定涡旋件60的定螺旋涡卷76可以以啮合的方式接合动涡旋件58的动螺旋涡卷64，从而产生一系列移动的流体腔。在压缩机构18的整个压缩周期中，由动螺旋涡卷64、定螺旋涡卷76限定的流体腔可以随着从径向外侧位置(抽 吸压力处)经过径向中间位置(中间压力处)向径向内侧位置(排放压力处)移动而减小体积由此压缩工作流体。定涡旋件60包括位于定螺旋涡卷76中央处用于排出压缩的工作流体的排出口77。
从动涡旋件58的动涡旋端板62可以向下突出有筒形毂部68。筒形毂部68可以具有以可旋转的方式设置在该筒形毂部68中的驱动衬套70。轴54可以包括偏心曲柄销56(也称为偏心部)。曲柄销56以传动的方式配合在驱动衬套70中。即，驱动衬套70配合在轴54的偏心曲柄销56的径向外侧。
曲柄销56可以以传动的方式接合驱动衬套70以提供径向柔性传动。由此，将驱动组件16产生的驱动力经由轴54的曲柄销56传递至驱动衬套70，再由驱动衬套70传递至动涡旋件58的筒形毂部68，从而带动动涡旋件58绕动。
如图2所示，止推组件48单独地形成并且设置在主轴承座44与动涡旋件58之间。止推组件48和主轴承座44构成了本申请中所述的支承组件。应理解的是，止推组件48可以与主轴承座44形成为一体件，即，支承组件为一体件。在未设置止推组件48的情况下，则主轴承座44构成支承组件(图1)。
当涡旋压缩机10运行时，动涡旋件58在轴54的驱动下相对于定涡旋件60绕动。同时，动涡旋件58的动涡旋端板62在止推组件48上滑动。因此，动涡旋端板62和止推组件48分别包括彼此滑动接触的止推面63、49。
在图示的示例中，在动涡旋件58的毂部68与止推组件48之间还设置有平衡配重部件72。在涡旋压缩机10运行时，润滑油在离心力作用下经由轴54中的油道52向上流动至偏心曲柄销56的顶面，然后顺着偏心曲柄销56的外周面向下流动以对驱动衬套70进行润滑，然后积聚在主轴承座44的底部中以形成油池47(图1)。动涡旋件58的毂部68(以及在本示例中的平衡配重部件72一起)搅动油池的润滑油，使润滑油飞溅至止推组件48与动涡旋件58的动涡旋端板62之间，从而对止推组件48和动涡旋端板62的止推面进行润滑。这种情况下，油池47的油位需要达到毂部68或平衡配重部件72能够搅动的高度。因此，在涡旋压缩机启动后，需要一段时间积攒润滑油，使得油池47的油位达到足够的高度，以便能够被毂部68或平衡配重部件72搅动并且使得搅动的润滑油能够飞溅到动涡旋端板62和止推组件48的止推面。
第一实施方式
如图2和图3所示，在动涡旋件58的毂部68上设置有至少一个供油通道 66。优选地，设置两个或者更多个供油通道66。例如，该供油通道66设置在动涡旋件58的毂部68的靠近动涡旋件58的动涡旋端板62的一侧。如图2和图3中的箭头所示，润滑油从涡旋压缩机10的基部经由轴54的油道52抽送到轴54的顶部(轴54的端面与动涡旋件58的动涡旋端板62之间)，在油的压力以及各部件旋转产生的离心力的作用下，将毂部68内侧的润滑油经由供油通道66甩出到毂部68外侧，喷溅到动涡旋件58的动涡旋端板62与止推组件48的止推面处。
与通过毂部68和/或平衡配重部件72搅动主轴承座底部的积攒预定高度的油池相比，通过设置供油通道66，能够显著更快地将润滑油喷溅到止推面处。这样是因为不需要等待涡旋压缩机10运行一段时间而使在主轴承座44的底部形成的油池中的液位到达一定高度后才能够通过润滑油的飞溅来润滑止推面。因此，通过供油通道66尽快地将润滑油供给至止推面，由此避免造成止推面早期磨损失效。即使涡旋压缩机10低速运行，通过供油通道66也能尽快地将润滑油供给至止推面，从而改善毂部68和/或平衡配重部件72对润滑油的搅动速度太低而不能将足够的润滑油喷溅至止推面的情况。
同时，经由供油通道66喷溅后的润滑油仍然会流回油池47，等油位达到一点高度后，仍然可以被毂部68和/或平衡配重部件72搅动而飞溅至止推面并润滑止推面。因此，该布置不会对原有的通过毂部68和/或平衡配重部件72搅动润滑油使其飞溅至止推面并润滑止推面的系统带来影响。
为了便于通过供油通道66将毂部内部的润滑油喷溅至毂部外部的端板和止推组件的止推面，供油通道66可以邻近动涡旋件58的动涡旋端板62设置，即邻近动涡旋件58的动涡旋端板62与止推组件48的止推面设置。并且，如图3所示，供油通道66在径向方向上延伸。替代性地，本领域技术人员可以设想，供油通道66可以在其他方向上延伸，例如在旋转方向偏转或者沿轴向倾斜，以有利于离心力将油甩至止推面。
此外，为了防止从供油通道66引出的润滑油被平衡配重部件72挡住而无法到达止推面，供油通道66的轴向位置可以设置成高于平衡配重部件72的顶部。
经由供油通道66喷溅的喷油量可以通过供油通道66的直径的大小来改变。供油通道66的直径越大，喷油量越多，反之亦然。
此外，如图4和图5所示，为了控制供油通道66的喷油量，也可以在供油通道66中设置节流装置，在节流装置中设置有贯通的通油孔。例如，该节流装置为节流螺钉80，在供油通道66中设置有螺纹孔78。该螺纹孔78与节流螺钉80相配合。在节流螺钉80的中央设置有轴向贯通的通油孔82。喷油量可以通过改变节流螺钉80的通油孔82的直径来调整。利用节流螺钉80，可以简化供油通道66的加工、进而简化动涡旋件58的加工，根据压缩机类型的不同，仅需要更换相应的节流螺钉80即可。此外，在毂部68上加工供油通道66时，如果供油通道66的直径过小，则难以进行加工。而通过使用节流螺钉80，则能够较好地解决在毂部68上的加工小直径的供油通道66的难题。
优选地，为了进一步改善润滑油的喷溅效果，可以对供油通道66自身的结构进行改进。例如，供油通道66可以包括将润滑油朝向动涡旋端板62和止推组件48的止推面喷溅的倾斜部段。
优选地，如图6至图9所示，为了更好的把油喷溅到止推面并且避免对供油通道66的过多加工，可以设置环绕毂部68位于供油通道66的径向外侧的甩油环84。甩油环84设置在毂部68与止推组件48之间，并且在供油通道66的下方固定至毂部68上。如图6和图7所示，甩油环84可以具有将润滑油朝向动涡旋端板62和止推组件48的止推面引导的倾斜的引导面85(即，渐缩的截头内锥形面)。通过倾斜(或渐缩)的引导面85将润滑油引导溅射至止推面。甩油环84可以是由两个半圆环铰接或卡扣连接在一起形成的圆环。甩油环84的两个半圆环在安装于动涡旋件58的毂部68上后通过例如销钉铰接或卡扣连接在一起。从供油通道66喷溅出来的油经由甩油环84的倾斜(或渐缩)的引导面85引导，将油溅射到止推面。而且，大体呈碗状的甩油环84可以起到小型油池的作用，有利于将油更均匀的甩到止推面上。
如图10和图11所示，平衡配重部件72包括连接至驱动衬套70(也可以连接至轴54)的安装基部73以及从安装基部73沿轴向延伸的配重部75。配重部在毂部68与止推组件48之间沿轴向延伸，构成设置在动涡旋件58的毂部68与止推组件48之间的中间构件。平衡配重部件72还具有靠近动涡旋端板62的顶部79。平衡配重部件72的大体构造在本领域中基本上是已知的。
替代性地，为了更好的把油喷溅到止推面，可以将平衡配重部件72的顶部79具有倾斜表面86。该倾斜表面86环绕毂部68位于供油通道66的径向 外侧。供油通道66设置成对应于平衡配重部件72的顶部79与动涡旋端板62之间的区域，从而利用平衡配重部件72的顶部79的倾斜表面86，将从供油通道66喷溅出来的油引导溅射到止推面。而且，该倾斜表面86也可以防止平衡配重部件72因为上下晃动而导致供油通道66被挡住。
替代性地，如图12和图13所示，可以在平衡配重部件72的顶部79上设置多个渐开线油槽88。利用渐开线油槽88能够更有效地将润滑油朝向端板68和止推组件48的止推面引导。
(1)本公开利用供油通道对止推面进行强制喷溅润滑，可以有效降低在涡旋压缩机启动时，短暂缺油所造成的止推面早期磨损失效；也可以改善在涡旋压缩机低速运行时，搅油飞溅润滑不充分的情况。
(2)本公开尤其适合带平衡配重部件的高速变频压缩机，通过喷溅润滑可显著改善其止推面润滑状态。
已出于说明和描述的目的提供了实施方式的前述描述。这些描述并不意在穷举或限制本公开。特定实施方式的各个元件或特征通常并不局限于该特定实施方式，而是在适用的情况下，即使没有具体地示出或描述，也是能够互换的并且能够在选定实施方式中使用。特定实施方式的各个元件或特征还可以以许多方式进行改变。这样的改变不应当被认为是与本公开相背离，并且所有这样的改型均意在被包括于本公开的范围内。

Claims (11)

  1. 一种涡旋压缩机，包括：
    定涡旋件，所述定涡旋件包括定涡旋端板、从所述定涡旋端板的一侧延伸的定螺旋涡卷以及设置在所述定涡旋端板中的排出口；
    动涡旋件，所述动涡旋件包括动涡旋端板、从所述动涡旋端板的一侧延伸的动螺旋涡卷以及从所述动涡旋端板的与所述动螺旋涡卷相反的一侧突出的毂部，所述动螺旋涡卷与所述定螺旋涡旋以啮合的方式接合，从而产生用于压缩工作流体的流体腔；
    支承组件，所述动涡旋端板滑动支承在所述支承组件上，所述支承组件和所述动涡旋端板各自具有彼此滑动接触的止推面；以及
    驱动组件，所述驱动组件包括用以驱动所述毂部的轴，
    其中，在所述毂部上设置有供油通道，所述毂部内的润滑油经由所述供油通道喷溅至所述止推面。
  2. 根据权利要求1所述的涡旋压缩机，其中，在所述轴中设置有用于将润滑油供给至所述毂部内的油道。
  3. 根据权利要求1所述的涡旋压缩机，其中，所述供油通道邻近所述动涡旋端板设置。
  4. 根据权利要求3所述的涡旋压缩机，其中，所述供油通道有多个并且沿周向方向设置在所述毂部上，多个所述供油通道具有彼此相同的直径或者不同的直径。
  5. 根据权利要求1所述的涡旋压缩机，其中，所述供油通道中设置有节流装置，所述节流装置中设置有贯通的通油孔，所述润滑油经由所述通油孔喷溅至所述止推面。
  6. 根据权利要求5所述的涡旋压缩机，其中，所述节流装置为节流螺钉， 所述供油通道中设置有与所述节流螺钉接合的螺纹孔。
  7. 根据权利要求1所述的涡旋压缩机，其中，所述供油通道包括将所述润滑油引导至所述止推面的倾斜部段。
  8. 根据权利要求1所述的涡旋压缩机，其中，所述涡旋压缩机还包括设置在所述毂部与所述支承组件之间的甩油环，所述甩油环位于所述供油通道的轴向下方并且固定至所述毂部上，所述甩油环具有将润滑油朝向所述止推面引导的倾斜的引导面。
  9. 根据权利要求1所述的涡旋压缩机，其中，所述涡旋压缩机还包括设置在所述毂部与所述支承组件之间的中间构件，其中，所述中间构件具有靠近所述动涡旋端板的顶部，并且所述供油通道设置成对应于所述中间构件的所述顶部与所述动涡旋端板之间的区域。
  10. 根据权利要求9所述的涡旋压缩机，其中，所述中间构件的所述顶部具有将润滑油朝向所述止推面引导的倾斜表面，和/或，所述中间构件的所述顶部上设置有将润滑油朝向所述止推面引导的多个渐开线油槽。
  11. 根据权利要求9或10所述的涡旋压缩机，还包括：
    驱动衬套，所述驱动衬套配合在所述轴的偏心曲柄销的径向外侧；以及
    平衡配重部件，所述平衡配重部件包括连接至所述驱动衬套或所述轴的安装基部以及从所述安装基部沿轴向延伸的配重部；
    其中，所述配重部构成了所述中间构件。
PCT/CN2020/124647 2020-07-27 2020-10-29 涡旋压缩机 WO2022021644A1 (zh)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CN202010732802.7A CN114001031A (zh) 2020-07-27 2020-07-27 涡旋压缩机
CN202021511823.8 2020-07-27
CN202010732802.7 2020-07-27
CN202021511823.8U CN212536075U (zh) 2020-07-27 2020-07-27 涡旋压缩机

Publications (1)

Publication Number Publication Date
WO2022021644A1 true WO2022021644A1 (zh) 2022-02-03

Family

ID=80037454

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2020/124647 WO2022021644A1 (zh) 2020-07-27 2020-10-29 涡旋压缩机

Country Status (1)

Country Link
WO (1) WO2022021644A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11933304B2 (en) 2021-09-02 2024-03-19 Bitzer Kuehlmaschinenbau Gmbh Scroll compressor including hub lubricant passage

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH045493A (ja) * 1990-04-23 1992-01-09 Daikin Ind Ltd スクロール型流体装置
JPH04279787A (ja) * 1991-03-07 1992-10-05 Hitachi Ltd 密閉形スクロール圧縮機
JP2001012370A (ja) * 1999-06-24 2001-01-16 Mitsubishi Heavy Ind Ltd スクロール型圧縮機
JP2003003972A (ja) * 2001-06-20 2003-01-08 Fujitsu General Ltd スクロール圧縮機
JP2003042080A (ja) * 2001-07-31 2003-02-13 Matsushita Electric Ind Co Ltd 密閉型スクロール圧縮機
CN1467378A (zh) * 2002-06-13 2004-01-14 松下电器产业株式会社 涡旋式压缩机
CN210371170U (zh) * 2019-07-19 2020-04-21 艾默生环境优化技术(苏州)有限公司 用于涡旋压缩机的平衡块及涡旋压缩机

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH045493A (ja) * 1990-04-23 1992-01-09 Daikin Ind Ltd スクロール型流体装置
JPH04279787A (ja) * 1991-03-07 1992-10-05 Hitachi Ltd 密閉形スクロール圧縮機
JP2001012370A (ja) * 1999-06-24 2001-01-16 Mitsubishi Heavy Ind Ltd スクロール型圧縮機
JP2003003972A (ja) * 2001-06-20 2003-01-08 Fujitsu General Ltd スクロール圧縮機
JP2003042080A (ja) * 2001-07-31 2003-02-13 Matsushita Electric Ind Co Ltd 密閉型スクロール圧縮機
CN1467378A (zh) * 2002-06-13 2004-01-14 松下电器产业株式会社 涡旋式压缩机
CN210371170U (zh) * 2019-07-19 2020-04-21 艾默生环境优化技术(苏州)有限公司 用于涡旋压缩机的平衡块及涡旋压缩机

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11933304B2 (en) 2021-09-02 2024-03-19 Bitzer Kuehlmaschinenbau Gmbh Scroll compressor including hub lubricant passage

Similar Documents

Publication Publication Date Title
KR100294429B1 (ko) 스크롤기계
US5533875A (en) Scroll compressor having a frame and open sleeve for controlling gas and lubricant flow
US5897306A (en) Partition and pilot ring for scroll machine
CN1112517C (zh) 涡旋式压缩机
JPH0893664A (ja) スクロール圧縮機
US4488855A (en) Main bearing lubrication system for scroll machine
KR19990044128A (ko) 스크롤 압축기
US6637550B2 (en) Displacement type fluid machine
CN212536075U (zh) 涡旋压缩机
JP2004100609A (ja) スクロール流体機械
WO2022021644A1 (zh) 涡旋压缩机
CN209340147U (zh) 用于涡旋压缩机的止推板和涡旋压缩机
US20130156623A1 (en) Variable-speed scroll refrigeration compressor
JPH06264876A (ja) スクロ−ル形圧縮機
US6338617B1 (en) Helical-blade fluid machine
CN112145412B (zh) 设置有轨道盘润滑系统的涡旋式压缩机
JP2522459B2 (ja) スクロ―ル形流体機械
CN114001031A (zh) 涡旋压缩机
WO2020143350A1 (zh) 用于涡旋压缩机的止推板和涡旋压缩机
CN113530827A (zh) 涡旋压缩机
JP2001271749A (ja) 密閉型電動圧縮機
CN204663894U (zh) 涡旋压缩机
JPH05231357A (ja) スクロール流体機械
JPH0727068A (ja) スクロ−ル形圧縮機
JP2616128B2 (ja) スクロール圧縮機

Legal Events

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

Ref document number: 20947505

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 20947505

Country of ref document: EP

Kind code of ref document: A1