WO2021077935A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

Info

Publication number
WO2021077935A1
WO2021077935A1 PCT/CN2020/114687 CN2020114687W WO2021077935A1 WO 2021077935 A1 WO2021077935 A1 WO 2021077935A1 CN 2020114687 W CN2020114687 W CN 2020114687W WO 2021077935 A1 WO2021077935 A1 WO 2021077935A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
fixed scroll
main bearing
fixed
bearing seat
Prior art date
Application number
PCT/CN2020/114687
Other languages
English (en)
French (fr)
Inventor
陈静
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
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 WO2021077935A1 publication Critical patent/WO2021077935A1/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
    • 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
    • F04C29/06—Silencing

Definitions

  • the present disclosure relates to a compressor, in particular to a scroll compressor.
  • a scroll compressor includes a casing and a compression mechanism.
  • the fixed scroll and the movable scroll constituting the compression mechanism are arranged in the casing of the scroll compressor.
  • Figures 1-3 show the main structural components in the casing of the scroll compressor of the prior art, such as: main bearing housing 102, support ring 104, fixed scroll 106, movable scroll 108, Oldham slip ring 110 and positioning PIN 112.
  • the main bearing housing 102 has a hub that accommodates the movable scroll and supports a lower portion of the movable scroll end plate and a plurality of legs 121 extending upward from the lower portion.
  • the support ring 104 is supported on the top of the leg of the main bearing seat and is fixed on the main bearing seat by a bearing screw 103.
  • the support ring 104 is provided to meet the requirement of miniaturization of the compressor.
  • the support ring helps to realize the radial positioning of the fixed scroll when the internal space of the miniaturized compressor is small.
  • a positioning pin 112 extending in the axial direction is arranged in a positioning pin hole on the fixed scroll to prevent the fixed scroll from rotating in the circumferential direction.
  • the Oldham slip ring 110 has an upwardly extending positioning key slidably arranged in the slip ring groove 1062 of the fixed scroll and an upwardly extending positioning key slidably arranged in the slip ring groove 1082 of the movable scroll, so that the movable scroll The swirl can rotate in translation relative to the fixed scroll, but cannot rotate around the center axis of the movable scroll itself.
  • the main body of the Oldham slip ring 110 is arranged between the movable scroll and the main bearing seat.
  • the axial flexibility of the compressor is controlled by the gap S between the support ring 104 and the ear 1064 of the fixed scroll (as shown in FIG. 2).
  • the support ring fits with the leg 121 on the main bearing housing and is supported by the leg.
  • This kind of outrigger has poor rigidity and is prone to stress concentration or even breakage at the root of the outrigger.
  • the space for the load-bearing screw is still limited, and the required load-bearing screw length is longer, and the stress at the root of the load-bearing thread is large.
  • the rigidity of the main bearing seat varies greatly in one cycle, resulting in a large difference in the deformation of the main bearing seat in various angular directions under the action of radial rotation load, which makes the support ring
  • the roundness of the inner diameter is poor, and a lot of noise is generated during the vortex movement.
  • the present disclosure provides a new type of scroll compressor.
  • the scroll compressor includes: a fixed scroll having a fixed scroll end plate and a fixed scroll extending from one side of the fixed scroll end plate; a movable scroll having a movable scroll
  • the orbiting scroll end plate, the orbiting scroll extending from one side of the orbiting scroll end plate, the hub extending from the opposite side of the orbiting scroll end plate, the fixed scroll and the orbiting scroll cooperate to form a series of compression tasks Compression chamber of fluid; Oldham slip ring, Oldham slip ring is configured to enable the movable scroll to rotate in translation relative to the fixed scroll, but cannot rotate around the center axis of the movable scroll;
  • the main bearing housing includes The supporting portion for slidingly supporting the end plate of the movable scroll and the circumferential wall located on the radially outer side of the fixed scroll and the movable scroll.
  • the circumferential wall has a circumferential portion continuously extending 360 degrees in the circumferential direction on the radially outer side of the fixed scroll.
  • a plurality of openings are provided on the circumferential wall of the main bearing seat to provide movement space for the Oldham slip ring and/or the movable scroll.
  • the supporting portion of the main bearing seat is an independent thrust disk, and the thrust disk is connected to or supported by the radially extending portion of the main bearing seat.
  • the fixed scroll is configured to be able to float a predetermined distance in the axial direction of the scroll compressor.
  • a pressure plate is provided on the end surface of the circumferential wall, and the pressure plate has a portion extending radially inwardly beyond the circumferential wall to stop the axial floating of the fixed scroll, thereby limiting the predetermined distance that the fixed scroll can float in the axial direction.
  • the pressing plate is an annular plate, or the pressing plate includes a plurality of arc-shaped sections uniformly arranged on the end surface of the circumferential wall along the circumferential direction.
  • the pressure plate is fixed on the end surface of the circumferential wall in a screw fixing manner.
  • the scroll compressor further includes a sound-absorbing cover that separates the space in the casing of the scroll compressor into a high-pressure area and a low-pressure area.
  • the scroll compression mechanism causes the sound-absorbing cover to define a predetermined distance within which the fixed scroll can float in the axial direction. .
  • the fixed scroll further includes an upper end portion extending from the side of the fixed scroll end plate opposite to the fixed scroll, and the predetermined distance is defined by the maximum gap formed between the upper end portion and the sound-absorbing cover.
  • the muffler cover further includes a flange portion extending from its outer periphery toward the fixed scroll, and the predetermined distance is defined by the maximum gap formed between the flange portion and the end plate of the fixed scroll.
  • the scroll compressor further includes an anti-rotation structure for preventing the fixed scroll from rotating relative to the main bearing housing.
  • the anti-rotation structure includes: a positioning pin hole extending in the radial direction provided on the fixed scroll, a positioning groove provided on the main bearing seat, and a positioning pin inserted into the positioning pin hole and the positioning groove in the radial direction.
  • one end of the positioning pin fits with the positioning pin hole of the fixed scroll in a clearance fit or interference fit, and the other end of the positioning pin fits with the positioning groove of the main bearing seat in a slidable manner.
  • a convex portion protruding upward in the axial direction is provided on the top surface of the circumferential wall of the main bearing seat, and the positioning groove is provided on the convex portion.
  • the anti-rotation structure includes: a positioning key protruding radially outwards or a positioning groove recessed inward provided on the fixed scroll, and a positioning key provided on the main bearing seat for interacting with the fixed scroll Or a positioning groove that is concave inward in the radial direction or a positioning key that protrudes outward that is matched with the positioning groove.
  • the Oldham slip ring is configured to cooperate with the movable scroll and the main bearing seat.
  • the Oldham slip ring has an upwardly protruding upper key which is matched with the movable scroll and a downwardly protruding key which is matched with the main bearing seat.
  • the movable scroll is provided with a movable scroll-slip ring keyway that is matched with the upper protruding key;
  • the main bearing seat is provided with a main bearing seat-slip ring keyway that is matched with the lower protruding key.
  • the fixed scroll includes an outer peripheral wall located on the radially outer side of the fixed scroll extending from the end plate of the fixed scroll.
  • the fixed scroll may not include an outer peripheral wall extending from the end plate of the fixed scroll and located on the radially outer side of the fixed scroll.
  • the main bearing housing has higher rigidity; the fixed scroll is directly arranged on On the main bearing seat, the support ring and load-bearing bolts in the prior art are omitted, so that the structure is simplified; and the size chain is reduced due to the omission of the support ring, the fixed scroll and the movable scroll and the main bearing seat The neutrality is improved; and the noise generated during the vortex movement is improved.
  • Fig. 1 is a perspective view showing main internal structural components of a scroll compressor of the prior art
  • Figure 2 is a cross-sectional view of the main internal structural components of the scroll compressor of Figure 1;
  • Figure 3 is a perspective view of the main bearing housing of Figure 1;
  • FIGS. 4a-4c are respectively a perspective view, a cross-sectional view, and an exploded state view showing the internal main structural components of the scroll compressor according to the present disclosure
  • Fig. 5 is a perspective view of the main bearing seat of the scroll compressor of Fig. 4a;
  • Figure 6 is a perspective view of the fixed scroll of Figure 4a;
  • Figure 7a is a partial enlarged view showing the circumferential positioning structure of the fixed scroll
  • Figures 7b and 7c are respectively perspective views of two embodiments of the positioning pins of the circumferential positioning structure of Figure 7a;
  • Figure 8 is a perspective view showing another circumferential positioning structure of the fixed scroll
  • Fig. 9a is a perspective view showing the internal main structural components of the scroll compressor according to the present disclosure.
  • Figure 9b is a partial enlarged cross-sectional view of the scroll compressor of Figure 9a;
  • FIGS. 10a and 10b are partial cross-sectional views of the scroll compressor according to the present disclosure.
  • 11a and 11b are a cross-sectional view and an exploded state view showing the internal main structural components of a scroll compressor according to another embodiment of the present disclosure
  • Figure 11c is a perspective view of the main bearing housing of the scroll compressor of Figure 11a;
  • Figure 11d is a perspective view of the thrust plate of the scroll compressor of Figure 11a;
  • Figure 12a is a cross-sectional view showing internal main structural components of a scroll compressor according to yet another embodiment of the present disclosure
  • Figure 12b is a perspective view of the main bearing housing of the scroll compressor of Figure 12a;
  • FIG. 13a and 13b are respectively an exploded state view and a cross-sectional view showing the main internal structural components of the scroll compressor according to the present disclosure
  • Figure 13c is a perspective view of the main bearing housing in Figures 13a and 13b;
  • Figure 13d is a cross-sectional view with a different fixed scroll compared to Figure 13b;
  • Figure 14a is a perspective view of the fixed scroll of Figure 13b;
  • Fig. 14b is a perspective view of the fixed scroll of Fig. 13d.
  • the scroll compressor 100 includes a main bearing housing 2, a fixed scroll 4, a movable scroll 6, and an Oldham slip ring 8.
  • the main bearing housing 2 is usually fixedly mounted to the casing of the scroll compressor 100.
  • the fixed scroll 4 and the movable scroll 6 constitute a compression mechanism that compresses the working fluid.
  • the Oldham slip ring 8 is configured such that the movable scroll 6 can orbit relative to the fixed scroll 4 to compress the working fluid, but cannot rotate around the central axis of the orbiting scroll 6.
  • the movable scroll 6 is slidably supported on the main bearing housing 2.
  • the movable scroll 6 has a movable scroll end plate 62, a movable scroll 63 extending axially on one side of the driven scroll end plate 62, and the other side edge of the driven scroll end plate 62. Axially extending hub 61.
  • the movable scroll 6 is disposed in the main bearing housing 2, and the movable scroll end plate 62 is supported on the supporting portion 25 of the main bearing housing 2.
  • the fixed scroll 4 is arranged above the movable scroll 6.
  • the fixed scroll 4 has a fixed scroll end plate 42, a fixed scroll 45 extending from one side of the fixed scroll end plate, and an upper end 43 extending from the other side of the fixed scroll end plate.
  • a protrusion 46 protruding radially outward is provided above the fixed scroll end plate 42 on the outer side of the upper end 43, and a positioning pin hole 41 extending in the radial direction is provided in the protrusion 46.
  • the upper end 43 of the fixed scroll forms a back pressure cavity.
  • the outer peripheral surface of the fixed scroll end plate 42 is matched with the inner side of the circumferential wall 21 of the main bearing housing to realize the relative positioning of the fixed scroll and the main bearing housing 2.
  • Fig. 6 is a perspective view of a fixed scroll of the scroll compressor of Figs. 4a-4c.
  • the fixed scroll may be provided with a radially outer upper end 431 and a radially inner upper end 432 extending upward from the end plate, forming a back pressure cavity between the radially inner upper end and the radial outer upper end.
  • Fig. 4c is an exploded view of the main internal structural components of the scroll compressor according to the present disclosure.
  • the Oldham slip ring 8 is arranged on the main bearing seat, is arranged on the radially outer side of the support part 25, is located between the movable scroll and the main bearing seat, and cooperates with the fixed scroll and the movable scroll respectively, so that the movable scroll is relative to the fixed scroll.
  • the scroll can only orbit in translation, and cannot rotate around the center axis of the orbiting scroll.
  • FIG. 5 shows the specific structure of the main bearing housing 2 according to the present disclosure.
  • the main bearing housing 2 has a substantially cylindrical shape.
  • the main bearing housing 2 includes a circumferentially continuous circumferential wall 21 extending in the axial direction, a shaft portion 23, a leg portion 24, a supporting portion 25 and a central through hole 26.
  • the supporting portion 25 and the upper circumferential wall 21 form an upper chamber 29.
  • Below the upper chamber 29 are the middle chamber 28 and the spindle hole 27 in sequence (see Fig. 4b).
  • Oldham slip rings, fixed scrolls, movable scrolls, and movable scroll end plates are arranged in the upper chamber 29.
  • the hub 61 of the movable scroll is provided in the middle chamber 28.
  • the main bearing housing 2 has a continuous circumferential wall 21 instead of separate legs, the main bearing housing has higher rigidity and higher reliability, reducing the stress at the root of the supporting structure concentrated.
  • the fixed scroll is directly arranged in the main bearing housing, so the structure omits the support ring and the load-bearing bolt, making the overall structure simpler. And because the support ring is omitted and the size chain is reduced, the centering of the fixed scroll and the main bearing is better. Due to the circumferentially continuous structure of the main bearing housing, the noise during the operation of the scroll compressor is reduced.
  • a positioning pin 9 extending in the radial direction is provided between the main bearing housing 2 and the fixed scroll 4 to prevent the fixed scroll from rotating relative to the main bearing housing in the circumferential direction.
  • the circumferential wall 21 of the main bearing housing 2 has a top surface 211.
  • a protrusion 210 protruding upward in the axial direction is provided on the top surface of the circumferential wall 21, and a positioning groove 212 is provided on the protrusion 210.
  • the illustrated positioning groove 212 is substantially rectangular.
  • positioning grooves can be envisaged, such as semicircular, elliptical, trapezoidal, etc., as long as it can cooperate with positioning pins or positioning components to define the circumferential position of the fixed scroll relative to the main bearing housing.
  • the positioning pin 9 is radially arranged in the positioning groove 212 of the main bearing housing 2 and the positioning pin hole 41 extending in the radial direction of the fixed scroll 4 to restrict the circumferential rotation of the fixed scroll.
  • One end of the positioning pin 9 is matched with the positioning pin hole 41 in a clearance fit or interference fit.
  • the other end of the positioning pin 9 is slidably fitted with the positioning groove 212.
  • Figures 7b and 7c show two embodiments of positioning pins.
  • the positioning pin 9' has a substantially cylindrical shape, and the middle of the outer peripheral surface of the positioning pin 9'has a groove 91.
  • the end 92 of the positioning pin that is matched with the positioning groove 212 of the main bearing housing 2 has a drum-shaped or spherical outer peripheral surface that protrudes outward.
  • the outwardly protruding drum or spherical portion 92 helps to clarify the load-bearing area and avoid rapid wear caused by the corner contact between the positioning pin and the positioning groove 212.
  • Fig. 7c shows a cylindrical positioning pin 9" in another embodiment. This positioning pin can be a standard part with a simple structure and low cost.
  • FIG. 8 shows another circumferential positioning structure of the fixed scroll 4.
  • the positioning key 44 can cooperate with the corresponding positioning groove 212 ′ of the main bearing housing 2 to realize the circumferential positioning of the fixed scroll 4.
  • the positioning key can also be arranged on the outer peripheral wall of the fixed scroll. Those skilled in the art can imagine that a positioning groove can be provided on the fixed scroll and a positioning key can be provided on the main bearing seat.
  • FIGS. 9a, 9b, 10a, and 10b As shown in Figs. 9a and 9b, two symmetrically arranged arc-shaped pressing plates 271, 272 are provided on the top surface 211 of the main bearing housing 2.
  • the pressure plate may also be an annular pressure plate continuous in the circumferential direction.
  • the pressing plates 271, 272 are fixed on the top surface 211 of the main bearing housing by screws.
  • the widths of the pressure plates 271 and 272 in the radial direction are greater than the radial thickness of the circumferential wall 21 of the main bearing housing 2.
  • the fixed scroll 4 When the fixed scroll 4 is installed in the main bearing housing 2, a part of the pressure plates 271 and 272 are located above the fixed scroll end plate 42 of the fixed scroll 4 so as to be able to stop the fixed scroll from floating in the axial direction. There is a certain gap S1 between the top surface 421 of the fixed scroll end plate 42 of the fixed scroll 4 and the lower surface of the pressure plate.
  • the gap S1 defines a predetermined distance in which the fixed scroll 4 can float upward.
  • Fig. 10a shows a structure for realizing the axial flexibility of the scroll compressor according to another embodiment.
  • a silencer cover 13 is provided between the top cover 11 of the scroll compressor and the top of the casing 12.
  • the fixed scroll, the movable scroll and the main bearing seat are arranged in the casing 12 of the scroll compressor.
  • the muffler cover 13 divides the space in the scroll compressor housing into a high-pressure area and a low-pressure area.
  • the silencer cover 13 is arranged above the fixed scroll 4. There is a gap S2 between the muffler cover 13 and the radially outer upper end 431 of the fixed scroll 4.
  • the existing sound-absorbing cover is used to limit the floating distance of the fixed scroll 4 in the axial direction, so as to realize the axial flexibility of the scroll compressor during operation.
  • Fig. 10b shows a structure for realizing the axial flexibility of the scroll compressor according to another embodiment.
  • the muffler cover 13' further includes a flange portion 131' extending from its outer periphery toward the fixed scroll.
  • the gap S3 between the flange portion of the muffler cover and the fixed scroll end plate 42' defines the distance that the fixed scroll can float upward in the axial direction.
  • FIG. 11a-11b show the main structural components such as the fixed scroll 204, the movable scroll 206, the Oldham slip ring 208, and the main bearing housing 202 of the scroll compressor 200 according to another embodiment of the present disclosure.
  • the main bearing housing 202 is also substantially cylindrical in shape.
  • the main bearing housing 202 includes a continuous circumferential wall 2021 extending in the axial direction, a radial extending portion 2022, a shaft portion 2023, a leg portion 2024, and a central through hole 2026.
  • the circumferential wall 2021 is connected to the radial extension 2022.
  • the main bearing housing 202 has a thrust plate 207.
  • the thrust plate 207 serves as a support portion that supports the movable scroll.
  • the thrust plate 207 is provided on the radially extending portion 2022.
  • the thrust plate 207 is fixed on the radial extension portion 2022 by means of screw fixing.
  • the thrust plate includes a bottom 227 and a thrust bearing 217 extending in the axial direction perpendicular to the bottom 227.
  • the top surface of the thrust bearing portion 217 is used to support the movable scroll 206.
  • the Oldham slip ring 208 is arranged on the radially outer side of the thrust bearing portion 217 of the thrust plate, is arranged between the bottom 227 and the end plate of the movable scroll 206 and cooperates with the fixed scroll and the movable scroll 206 to restrict the movable scroll, respectively. Rotational movement of spin 206.
  • the middle cavity 2028 of the main bearing housing 202 can be designed to be larger.
  • a balance member 203 i.e., a counterweight, may be provided in the middle chamber 2028.
  • the central hole 257 of the thrust plate 207 has a larger diameter at the bottom. The diameter of the upper part of the central hole 257 of the thrust plate 207 may be smaller to support the movable scroll.
  • Fig. 12a shows the structure of the fixed scroll, the movable scroll, the Oldham ring and the main bearing housing of the scroll compressor 300 according to another embodiment of the present disclosure.
  • the structure of the fixed scroll 304, the movable scroll 306, the Oldham ring 308, and the thrust plate 307 of this embodiment is basically the same as the structure of the above-mentioned fixed scroll 204, the movable scroll 206, the Oldham slip ring 208 and the thrust plate 207, respectively. The same, so I won't repeat them here.
  • FIG. 12a shows the structure of the fixed scroll, the movable scroll, the Oldham ring and the main bearing housing of the scroll compressor 300 according to another embodiment of the present disclosure.
  • the structure of the fixed scroll 304, the movable scroll 306, the Oldham ring 308, and the thrust plate 307 of this embodiment is basically the same as the structure of the above-mentioned fixed scroll 204, the movable scroll 206, the Oldham slip ring 208 and the thrust plate 207
  • the difference between the main bearing housing 302 and the above-mentioned main bearing housing 202 is that a plurality of openings 3026 are provided on the lower side of the circumferential wall 3021 along the circumferential direction.
  • a plurality of openings 3026 are provided on the lower side of the circumferential wall 3021 along the circumferential direction.
  • four openings 3026 are provided.
  • the upper part of the circumferential wall is still circumferentially continuous.
  • the opening 3026 provides a larger movement space for the movable scroll and the Oldham slip ring.
  • the Oldham slip ring is arranged to cooperate with the fixed scroll and the movable scroll. According to another embodiment of the present disclosure, the Oldham slip ring is arranged to cooperate with the movable scroll and the main bearing seat.
  • Figures 13a and 13b respectively show an exploded view and a cross-sectional view of the main structural components of the scroll compressor with an Oldham slip ring that cooperates with the movable scroll and the main bearing housing.
  • Figure 13c shows the main bearing housing of this embodiment.
  • the Oldham slip ring 408 has an annular body portion 4081, orbiting scroll-slip ring keys 4082, 4084 protruding upward from the annular body portion 4081, and downward protruding from the annular body portion 4081 Spindle seat-slip ring keys 4086, 4088.
  • the structure of the main bearing housing 402 in this embodiment is similar to the structure of the main bearing housing 2 described above, the difference is that the main bearing housing 402 is provided with a spindle seat-slip ring key 4086, 4088 on the cross slip ring 408. Mating main bearing seat-slip ring keyway 4024 and 4026.
  • the movable scroll 406 is provided with movable scroll-slip ring key grooves 4064, 4066 for cooperating with the movable scroll-slip ring keys 4082, 4084.
  • a key groove for mating with the key of the Oldham slip ring 408 is omitted.
  • the scroll of the fixed scroll can be designed to be closer to the radially outer side. Then, in the case of the same outer dimensions of the fixed scroll, the fixed scroll can be designed to have a larger displacement. As shown in FIGS.
  • the fixed scroll 404 is provided with an outer peripheral wall 4049 located on the radially outer side of the fixed scroll 4044.
  • the fixed scroll scroll refers to the part that cooperates with the scroll scroll of the movable scroll.
  • the scroll portion usually has a uniform wall thickness.
  • Fig. 13d shows a structure similar to that in Fig. 13b, except that the fixed scroll 404' does not have the aforementioned outer peripheral wall.
  • the fixed scroll may have an outer peripheral wall 4049 located around the scroll as shown in FIG. 14a, or may not have a peripheral wall 4049 located around the scroll as shown in FIG. 14b. Peripheral wall.
  • the axial direction herein refers to the direction in which the main shaft of the scroll compressor extends. Radial refers to the direction extending perpendicular to the axial direction.

Landscapes

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

Abstract

一种涡旋压缩机（100），包括：定涡旋（4），定涡旋（4）具有定涡旋端板（42）、从定涡旋端板（42）的一侧延伸的定涡卷（45）；动涡旋（6），动涡旋（6）具有动涡旋端板（62）、从动涡旋端板（62）的一侧延伸的动涡卷（63）、从动涡旋端板（62）的相反一侧延伸的毂部（61），定涡卷（45）与动涡卷（63）配合以形成一系列压缩工作流体的压缩腔；十字滑环（8），十字滑环（8）构造成用于使动涡旋（6）相对于定涡旋（4）能够平动转动，但不能围绕动涡旋（6）的中心轴线旋转；以及主轴承座（2），主轴承座（2）包括用于滑动支承动涡旋端板（62）的支承部（25）以及位于定涡旋（4）和动涡旋（6）径向外侧的周向壁（21），周向壁（21）在定涡旋（4）的径向外侧具有沿圆周方向连续延伸360度的圆周部。具有这种结构的涡旋压缩机（100）结构更简化、运转时噪音更小并且主轴承座（2）具有更高的刚度。

Description

涡旋压缩机
本申请要求以下中国专利申请的优先权：于2019年10月24日提交中国专利局的申请号为201921800576.0、发明创造名称为“涡旋压缩机”的中国专利申请。该专利申请的全部内容通过引用结合在本申请中。
技术领域
本公开涉及一种压缩机，具体地涉及一种涡旋压缩机。
背景技术
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。
通常，涡旋压缩机包括壳体和压缩机构。构成压缩机构的定涡旋和动涡旋设置在涡旋压缩机的壳体内。图1-3示出了现有技术的涡旋压缩机的壳体内的主要结构部件，例如：主轴承座102、支撑环104、定涡旋106、动涡旋108、十字滑环110和定位销112。主轴承座102具有容纳动涡旋的毂部并且支承动涡旋端板的下部部分和从下部部分向上延伸的多个支腿121。支撑环104支撑在主轴承座的支腿的顶部上并且通过承载螺钉103固定在主轴承座上。支撑环104是为了满足压缩机小型化的需求而设置的。支撑环有助于在小型化压缩机内部空间较小的情况下实现定涡旋的径向定位。沿轴向延伸的定位销112设置在定涡旋上的定位销孔中，用来防止定涡旋沿周向的旋转。十字滑环110具有可滑动设置在定涡旋的滑环凹槽1062中的向上延伸的定位键和可滑动设置在动涡旋的滑环凹槽1082中的向上延伸的定位键，使得动涡旋能够相对于定涡旋平动转动，而不能围绕动涡旋自身的中心轴线旋转。十字滑环110的主体设置在动涡旋与主轴承座之间。在这种结构中，通过支撑环104与定涡旋的耳部1064(如图2所示)之间的间隙S来控制压缩机的轴向柔性。
然而，在这种结构中，支撑环与主轴承座上的支腿121配合并且由支腿支撑。这种支腿刚性较差，容易在支腿的根部产生应力集中，甚至断裂。在这种结构中，承载螺钉的空间仍然受到限制，并且所需的承载螺钉长度较长，承载螺纹根部应力大。此外，由于主轴承座上的支腿结构，使得主轴承座在一周 上的刚度变化大，导致在径向旋转载荷作用下，主轴承座的各个角度方向的变形差异大，从而使得支撑环的内径圆度差，在涡旋运动期间产生很大的噪音。
发明内容
为了解决现有技术中的上述问题中的至少一部分，本公开提供了一种新型的涡旋压缩机。
根据本公开的实施方式的涡旋压缩机包括：定涡旋，定涡旋具有定涡旋端板、从定涡旋端板的一侧延伸的定涡卷；动涡旋，动涡旋具有动涡旋端板、从动涡旋端板的一侧延伸的动涡卷、从动涡旋端板的相反一侧延伸的毂部，定涡卷与动涡卷配合以形成一系列压缩工作流体的压缩腔；十字滑环，十字滑环构造成用于使动涡旋相对于定涡旋能够平动转动，但不能围绕动涡旋的中心轴线旋转；以及主轴承座，主轴承座包括用于滑动支承动涡旋端板的支承部以及位于定涡旋和动涡旋径向外侧的周向壁，周向壁在定涡旋的径向外侧具有沿圆周方向连续延伸360度的圆周部。
其中，在主轴承座的周向壁上设置有为十字滑环和/或动涡旋的运动提供运动空间的多个开口。
其中，主轴承座的支承部为独立的止推盘，止推盘连接至主轴承座的径向延伸部或者由主轴承座的径向延伸部支承。
其中，定涡旋构造成能够沿涡旋压缩机的轴向浮动预定距离。
其中，周向壁的端面上设置有压板，压板具有沿径向向内延伸超出周向壁的部分以能够止挡定涡旋的轴向浮动，从而限定定涡旋沿轴向能够浮动的预定距离。
其中，压板为环形板，或者压板包括沿周向均匀地设置在周向壁的端面上的多个弧形部段。
其中，压板以螺纹固定的方式固定在周向壁的端面上。
其中，涡旋压缩机还包括将涡旋压缩机的壳体内的空间分隔成高压区域和低压区域的消音盖，涡旋压缩机构造成由消音盖限定定涡旋能够在轴向上浮动的预定距离。
其中，定涡旋还包括从定涡旋端板的与定涡卷相反的一侧延伸的上端部，预定距离由上端部与消音盖之间形成的最大间隙来限定。
其中，消音盖还包括从其外周朝向定涡旋延伸的凸缘部，预定距离由凸缘部与定涡旋端板之间形成的最大间隙来限定。
其中，涡旋压缩机还包括用于防止定涡旋相对于主轴承座旋转的防旋转结构。
其中，防旋转结构包括：在定涡旋上设置的沿径向延伸的定位销孔、在主轴承座上设置的定位凹槽以及沿径向插入定位销孔和定位凹槽中的定位销。
其中，定位销的一端与定涡旋的定位销孔以间隙配合或过盈配合的方式配合，定位销的另一端与主轴承座的定位凹槽以能够滑动的方式配合。
其中，在主轴承座的周向壁的顶部表面上设置有沿轴向向上凸起的凸起部，定位凹槽设置在凸起部上。
其中，防旋转结构包括：在定涡旋上设置的沿径向向外突出的定位键或向内凹入的定位凹槽、以及在主轴承座上设置的用于与定涡旋的定位键或定位凹槽配合的沿径向向内凹入的定位凹槽或向外突出的定位键。
其中，十字滑环构造成与动涡旋和主轴承座配合。十字滑环具有与动涡旋配合的向上凸出的上凸出键以及与主轴承座配合的向下凸出的下凸出键。其中，动涡旋上设置有与上凸出键配合的动涡旋-滑环键槽；主轴承座上设置有与下凸出键配合的主轴承座-滑环键槽。
其中，定涡旋包括从定涡旋端板延伸的位于定涡卷径向外侧的外周壁。定涡旋可以不包括从定涡旋端板延伸的位于定涡卷径向外侧的外周壁。
由于该涡旋压缩机的周向壁在定涡旋的径向外侧具有沿圆周方向连续延伸360度的圆周部，在这种结构中，主轴承座具有更高的刚度；使定涡旋直接设置在主轴承座上，省去了现有技术中的支撑环和承载螺栓，从而使结构更简化；并且由于省去了支撑环而减少了尺寸链，定涡旋和动涡旋与主轴承座的对中性得到改善；并且改善了涡旋运动期间产生的噪音。
附图说明
本文中所描述的附图仅出于对示例性的结构的说明性目的而并非意在限制本公开的范围，其中：
图1是示出现有技术的涡旋压缩机的内部主要结构部件的立体图；
图2是图1的涡旋压缩机的内部主要结构部件的剖视图；
图3是图1的主轴承座的立体图；
图4a-4c分别是示出根据本公开的涡旋压缩机的内部主要结构部件的立体图、剖视图和分解状态图；
图5是图4a的涡旋压缩机的主轴承座的立体图；
图6是图4a的定涡旋的立体图；
图7a是示出定涡旋的周向定位结构的局部放大图；
图7b和图7c分别是图7a的周向定位结构的定位销的两种实施方式的立体图；
图8是示出了定涡旋的另一周向定位结构的立体图；
图9a是示出根据本公开的涡旋压缩机的内部主要结构部件的立体图；
图9b是图9a的涡旋压缩机的局部放大剖视图；
图10a和图10b是根据本公开的涡旋压缩机的局部剖视图；
图11a和图11b是示出根据本公开的另一实施方式的涡旋压缩机的内部主要结构部件的剖视图和分解状态图；
图11c是图11a的涡旋压缩机的主轴承座的立体图；
图11d是图11a的涡旋压缩机的止推盘的立体图；
图12a是示出根据本公开的又一实施方式的涡旋压缩机的内部主要结构部件的剖视图；
图12b是图12a的涡旋压缩机的主轴承座的立体图；
图13a和图13b分别是示出根据本公开的涡旋压缩机的内部主要结构部件的分解状态图和剖视图；
图13c是图13a和13b中的主轴承座的立体图；
图13d是与图13b相比具有不同的定涡旋的剖视图；
图14a是图13b的定涡旋的立体图；
图14b是图13d的定涡旋的立体图。
具体实施方式
下面将结合附图中所示的具体实施例对本公开进行详细地介绍。
图4a、图4b和图4c示出了根据本公开的实施方式的涡旋压缩机的内部主要结构部件。如图4a、图4b和图4c所示，该涡旋压缩机100包括主轴承 座2、定涡旋4、动涡旋6和十字滑环8。主轴承座2通常固定地安装至涡旋压缩机100的壳体。定涡旋4和动涡旋6构成对工作流体进行压缩的压缩机构。十字滑环8构造成使得动涡旋6相对于定涡旋4能够绕动以压缩工作流体，而不能绕动涡旋6的中心轴线旋转。动涡旋6以能够滑动的方式支承在主轴承座2上。
如图4b所示，动涡旋6具有动涡旋端板62、从动涡旋端板62的一侧沿轴向延伸的动涡卷63以及从动涡旋端板62的另一侧沿轴向延伸的毂部61。动涡旋6设置在主轴承座2中，并且动涡旋端板62支撑在主轴承座2的支撑部25上。
如图4b所示，定涡旋4设置在动涡旋6的上方。定涡旋4具有定涡旋端板42、从定涡旋端板的一侧延伸的定涡卷45和从定涡旋端板的另一侧延伸的上端部43。在定涡旋端板42上方于上端部43的外侧设置有沿径向向外突出的突起部46，突起部46中设置有沿径向延伸的定位销孔41。定涡旋的上端部43形成背压腔。定涡旋端板42的外周面与主轴承座的周向壁21的内侧配合，以实现定涡旋与主轴承座2的相对定位。定涡卷与动涡卷配合以形成一系列压缩工作流体的压缩腔。图6是图4a-4c的涡旋压缩机的定涡旋的立体图。定涡旋可以设置有从端板向上延伸的径向外侧上端部431和径向内侧上端部432，在径向内侧上端部和径向外侧上端部之间形成背压腔。
图4c是根据本公开的涡旋压缩机的主要内部结构部件的分解状态图。十字滑环8设置在主轴承座上，设置在支撑部25的径向外侧，位于动涡旋与主轴承座之间，分别与定涡旋和动涡旋配合，使得动涡旋相对于定涡旋只能平动绕动，不能围绕动涡旋的中心轴线旋转。
图5示出了根据本公开的主轴承座2的具体结构。如图5所示，该主轴承座2为大致圆筒形形状。该主轴承座2包括沿轴向延伸的周向连续的周向壁21、轴部23、腿部24、支撑部25以及中央通孔26。支撑部25与上部周向壁21形成上部腔室29。上部腔室29的下方依次和为中部腔室28和主轴孔27(参见图4b)。十字滑环、定涡卷、动涡卷和动涡旋端板设置在上部腔室29中。动涡旋的毂部61设置在中部腔室28中。
在这种结构中，由于主轴承座2具有连续的周向壁21，而不是具有分离的支腿，因此主轴承座具有较高的刚度以及较高的可靠性，减小了支撑结构根 部处的应力集中。在该结构中，定涡旋直接设置在主轴承座中，因此该结构省去了支撑环和承载螺栓，使得整体结构更简单。并且由于省去了支撑环而减少了尺寸链，使得定涡旋与主轴承的对中性更好。由于主轴承座的周向连续的结构，进而减少了涡旋压缩机运行期间的噪音。
下面结合图7a至图8介绍该涡旋压缩机的定涡旋的周向定位结构。如图7a所示，在主轴承座2与定涡旋4之间设置有沿径向延伸的定位销9，用于防止定涡旋相对于主轴承座沿周向的旋转。主轴承座2的周向壁21具有顶部表面211。在周向壁21的顶部表面上设置有沿轴向向上凸起的凸起部210，在该凸起部210上设置有定位凹槽212。所示出的定位凹槽212是大致矩形的。显而易见的是，能够设想其他形状的定位凹槽，例如半圆形、椭圆形、梯形等，只要能够与定位销或定位部件配合能够限定定涡旋相对主轴承座的周向位置即可。定位销9沿径向设置在主轴承座2的定位凹槽212和定涡旋4的径向延伸的定位销孔41中用以限制定涡旋的周向旋转。定位销9的一端与定位销孔41以间隙配合或过盈配合的方式配合。定位销9的另一端与定位凹槽212以可滑动的方式配合。
图7b和7c示出了定位销的两种实施方式。如图7b所示，定位销9’为大致圆柱形形状，该定位销9’的外周面的中部具有凹槽91。定位销的与主轴承座2的定位凹槽212配合的端部92具有向外凸出的鼓状或球面外周面。向外凸出的鼓状或球面部92有助于将承载区域明确化，并且避免定位销和定位凹槽212之间的边角接触引起的快速磨损。图7c示出了另一实施方式的圆柱形的定位销9”。这种定位销可以是标准件，结构简单，成本低。
图8示出了定涡旋4的另一种周向定位结构。在定涡旋4上没有设置定位销孔41，而是在定涡旋端板上设置有沿径向向外突出的至少一个定位键44。定位键44能够与主轴承座2的相应的定位凹槽212'配合从而实现定涡旋4的周向定位。定位键也可以设置在定涡旋的外周壁上。本领域的技术人员能够设想的是，能够在定涡旋上设置定位凹槽并且在主轴承座上设置定位键。
对于涡旋压缩机而言，需要具有一定的轴向柔性。下面将结合图9a、图9b和图10a、图10b介绍根据本公开的实现涡旋压缩机的轴向柔性的结构。如图9a和9b所示，在主轴承座2的顶部表面211上设置有两个对称地设置的弧形压板271、272。该压板也可以是周向连续的环状压板。该压板271、272通 过螺钉固定在主轴承座的顶部表面211上。压板271、272的沿径向的宽度大于主轴承座2的周向壁21的径向厚度。在定涡旋4设置在主轴承座2中时，压板271、272的一部分位于定涡旋4的定涡旋端板42的上方，以能够止挡定涡旋的轴向浮动。定涡旋4的定涡旋端板42的顶表面421与压板的下表面之间存在一定的间隙S1。该间隙S1限定定涡旋4能够向上浮动的预定距离。
图10a示出了另一实施方式的实现涡旋压缩机的轴向柔性的结构。如图10a所示，在涡旋压缩机的顶盖11与壳体12的顶部之间设置有消音盖13。定涡旋、动涡旋和主轴承座设置在涡旋压缩机的壳体12中。消音盖13将涡旋压缩机壳体内的空间分成高压区域和低压区。消音盖13设置在定涡旋4的上方。在消音盖13与定涡旋4的径向外侧上端部431之间具有间隙S2。在该结构中，利用已有的消音盖限制定涡旋4沿轴向浮动的距离，从而实现涡旋压缩机运行时的轴向柔性。在图10a所示的结构中不需要在主轴承座2的顶部表面211上额外设置压板。
图10b示出了又一实施方式的实现涡旋压缩机的轴向柔性的结构。如图10b所示，消音盖13’还包括从其外周朝向定涡旋延伸的凸缘部131’。消音盖的凸缘部与定涡旋端板42’之间的间隙S3限定定涡旋沿轴向能够向上浮动的距离。
图11a-11b示出了根据本公开的另一实施方式的涡旋压缩机200的定涡旋204、动涡旋206、十字滑环208和主轴承座202等主要结构部件。如图11c所示，该主轴承座202也是大致圆筒形形状。该主轴承座202包括沿轴向延伸的连续的周向壁2021、径向延伸部2022、轴部2023、腿部2024以及中央通孔2026。周向壁2021与径向延伸部2022连接。在该结构中，该主轴承座202与上述主轴承座2的区别在于该主轴承座202具有止推盘207。止推盘207用作支撑动涡旋的支撑部。止推盘207设置在径向延伸部2022上。该止推盘207通过螺纹固定的方式固定在径向延伸部2022上。如图11d所示，该止推盘包括底部227和垂直于底部227沿轴向延伸的止推轴承部217。止推轴承部217的顶表面用于支撑动涡旋206。十字滑环208设置在止推盘的止推轴承部217的径向外侧，设置在底部227与动涡旋206的端板之间并且分别与定涡旋和动涡旋206配合以限制动涡旋206的旋转运动。
在这种结构中，主轴承座202的中部腔室2028可以设计的更大。在这种 较大的中部腔室的情况下，可以在中部腔室2028内设置平衡构件203，即配重。为了与该较大的中部腔室2028配合，止推盘207的中央孔257在底部具有较大的直径。止推盘207的中央孔257的上部的直径可以较小，以支撑动涡旋。
图12a示出了根据本公开的又一实施方式的涡旋压缩机300的定涡旋、动涡旋、十字滑环和主轴承座的结构。该实施方式的定涡旋304、动涡旋306、十字滑环308和止推盘307的结构分别与上述定涡旋204、动涡旋206、十字滑环208和止推盘207的结构基本相同，在此不再赘述。如图12b所示，该主轴承座302与上述主轴承座202的区别在于在其周向壁3021的下侧部沿周向设置有多个开口3026。在所示出的实施方式中设置有4个开口3026。本领域的技术人员应当理解的是，能够设置其他数量的开口。在该结构中，周向壁的上部仍然是周向连续的。该开口3026为动涡旋和十字滑环提供了更大的运动空间。
前述实施方式中，十字滑环设置成与定涡旋和动涡旋配合。根据本公开的另外的实施方式，十字滑环设置成与动涡旋和主轴承座配合。图13a和13b分别示出了具有与动涡旋和主轴承座配合的十字滑环的涡旋压缩机的主要结构部件的分解状态图和剖视图。图13c示出了这一实施方式的主轴承座。在这一实施方式中，十字滑环408具有环状主体部4081、从环状主体部4081向上凸起的动涡旋-滑环键4082、4084以及从环状主体部4081向下凸起的主轴座-滑环键4086、4088。该实施方式中的主轴承座402的结构与上述主轴承座2的结构相似，其区别在于，该主轴承座402上设置有用于与十字滑环408上的主轴座-滑环键4086、4088配合的主轴承座-滑环键槽4024和4026。动涡旋406上设置有用于与动涡旋-滑环键4082、4084配合的动涡旋-滑环键槽4064、4066。定涡旋404上省去了用于与十字滑环408的键配合的键槽。在这种结构中，由于设计定涡旋时不必留有用于与十字滑环配合的键槽所需的空间，所以定涡旋的涡卷能够设计成更靠近径向外侧。那么，在定涡旋的相同的外部尺寸的情况下，定涡旋能够设计成具有更大的排量。如图13a和13b所示，定涡旋404上设置有位于定涡旋涡卷4044的径向外侧的外周壁4049。通常，定涡旋涡卷指的是与动涡旋的涡卷配合的部分。涡卷部分通常具有均匀的壁厚。图13d示出了与图13b中相似的结构，其区别在于，定涡旋404’不具有上述外 周壁。
图14a和图14b是分别示出了上述实施方式的定涡旋404和404’的立体图。在定涡旋不具有用于十字滑环的键槽的情况下，定涡旋可以如图14a所示具有位于涡卷周围的外周壁4049，也可以如图14b所示不具有位于涡卷周围的外周壁。
本文中的轴向指的是涡旋压缩机的主轴延伸的方向。径向指的是与轴向垂直延伸的方向。
虽然已经具体描述了本公开的一些实施方式和变型，但是本领域技术人员应该理解，本公开并不局限于上面描述和附图所示的实施方式和变型而是可以包括其他各种可能的变型和组合。在不偏离本公开的实质和范围的情况下可由本领域的技术人员实现其它的变型和变体。所有这些变型和变体都落入本公开的范围内。而且，所有在此描述的构件都可以由其他技术性上等同的构件来代替。

Claims (16)

  1. 一种涡旋压缩机，其特征在于，包括：
    定涡旋，所述定涡旋具有定涡旋端板、从所述定涡旋端板的一侧延伸的定涡卷；
    动涡旋，所述动涡旋具有动涡旋端板、从所述动涡旋端板的一侧延伸的动涡卷、从所述动涡旋端板的相反一侧延伸的毂部，所述定涡卷与所述动涡卷配合以形成一系列压缩工作流体的压缩腔；
    十字滑环，所述十字滑环构造成用于使所述动涡旋相对于所述定涡旋能够平动转动，但不能围绕所述动涡旋的中心轴线旋转；以及
    主轴承座，所述主轴承座包括用于滑动支承所述动涡旋端板的支承部以及位于所述定涡旋和所述动涡旋径向外侧的周向壁，所述周向壁在所述定涡旋的径向外侧具有沿圆周方向连续延伸360度的圆周部。
  2. 根据权利要求1所述的涡旋压缩机，其特征在于，
    在所述主轴承座的周向壁上设置有为所述十字滑环和/或所述动涡旋的运动提供运动空间的多个开口。
  3. 根据权利要求1所述的涡旋压缩机，其特征在于，
    所述主轴承座的支承部为独立的止推盘，所述止推盘连接至所述主轴承座的径向延伸部或者由所述主轴承座的所述径向延伸部支承。
  4. 根据权利要求1-3中任一项所述的涡旋压缩机，其特征在于，
    所述定涡旋构造成能够沿所述涡旋压缩机的轴向浮动预定距离。
  5. 根据权利要求4所述的涡旋压缩机，其特征在于，
    所述周向壁的顶部表面上设置有压板，所述压板具有沿径向向内延伸超出所述周向壁的部分以能够止挡所述定涡旋的轴向浮动，从而限定所述定涡旋沿轴向能够浮动的所述预定距离。
  6. 根据权利要求5所述的涡旋压缩机，其特征在于，
    所述压板为环形板，或者所述压板包括沿周向均匀地设置在所述周向壁的顶部表面上的多个弧形部段。
  7. 根据权利要求4所述的涡旋压缩机，其特征在于，
    所述涡旋压缩机还包括将所述涡旋压缩机的壳体内的空间分隔成高压区域和低压区域的消音盖，所述涡旋压缩机构造成由所述消音盖限定所述定涡旋能够在轴向上浮动的所述预定距离。
  8. 根据权利要求7所述的涡旋压缩机，其特征在于，
    所述定涡旋还包括从所述定涡旋端板的与所述定涡卷相反的一侧延伸的上端部，所述预定距离由所述上端部与所述消音盖之间形成的最大间隙来限定。
  9. 根据权利要求7所述的涡旋压缩机，其特征在于，
    所述消音盖还包括从其外周朝向所述定涡旋延伸的凸缘部，所述预定距离由所述凸缘部与所述定涡旋端板之间形成的最大间隙来限定。
  10. 根据权利要求1-3中任一项所述的涡旋压缩机，其特征在于，
    所述涡旋压缩机还包括用于防止所述定涡旋相对于所述主轴承座旋转的防旋转结构。
  11. 根据权利要求10所述的涡旋压缩机，其特征在于，
    所述防旋转结构包括：在所述定涡旋上设置的沿径向延伸的定位销孔、在所述主轴承座上设置的定位凹槽以及沿所述径向插入所述定位销孔和所述定位凹槽中的定位销。
  12. 根据权利要求11所述的涡旋压缩机，其特征在于，
    所述定位销的一端与所述定涡旋的所述定位销孔以间隙配合或过盈配合的方式配合，所述定位销的另一端与所述主轴承座的所述定位凹槽以能够滑动 的方式配合。
  13. 根据权利要求12所述的涡旋压缩机，其特征在于，
    在所述主轴承座的所述周向壁的顶部表面上设置有沿轴向向上凸起的凸起部，所述定位凹槽设置在所述凸起部上。
  14. 根据权利要求10所述的涡旋压缩机，其特征在于，
    所述防旋转结构包括：在所述定涡旋上设置的沿径向向外突出的定位键或向内凹入的定位凹槽、以及在所述主轴承座上设置的用于与所述定涡旋的所述定位键或定位凹槽配合的沿径向向内凹入的定位凹槽或向外突出的定位键。
  15. 根据权利要求1-3中任一项所述的涡旋压缩机，其特征在于，
    所述十字滑环构造成与所述动涡旋和所述主轴承座配合，
    所述十字滑环具有与所述动涡旋配合的向上凸出的上凸出键以及与所述主轴承座配合的向下凸出的下凸出键，
    所述动涡旋上设置有与所述上凸出键配合的动涡旋-滑环键槽；所述主轴承座上设置有与所述下凸出键配合的主轴承座-滑环键槽。
  16. 根据权利要求15所述的涡旋压缩机，其特征在于，
    所述定涡旋不包括或者包括从所述定涡旋端板延伸的位于所述定涡卷径向外侧的外周壁。
PCT/CN2020/114687 2019-10-24 2020-09-11 涡旋压缩机 WO2021077935A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201921800576.0 2019-10-24
CN201921800576.0U CN211144798U (zh) 2019-10-24 2019-10-24 涡旋压缩机

Publications (1)

Publication Number Publication Date
WO2021077935A1 true WO2021077935A1 (zh) 2021-04-29

Family

ID=71770373

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2020/114687 WO2021077935A1 (zh) 2019-10-24 2020-09-11 涡旋压缩机

Country Status (2)

Country Link
CN (1) CN211144798U (zh)
WO (1) WO2021077935A1 (zh)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN211144798U (zh) * 2019-10-24 2020-07-31 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
CN115306711A (zh) * 2022-08-12 2022-11-08 深圳昂湃技术有限公司 一种二氧化碳涡旋压缩机的压力平衡结构

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101158351A (zh) * 2007-11-16 2008-04-09 美的集团有限公司 涡旋式压缩机及其控制方法
CN101303018A (zh) * 2008-06-06 2008-11-12 西安交通大学 涡旋压缩机
JP2017002804A (ja) * 2015-06-10 2017-01-05 富士電機株式会社 スクロール圧縮機
CN209053784U (zh) * 2018-11-06 2019-07-02 苏州英华特涡旋技术有限公司 一种涡旋压缩机的防抽真空装置
CN209164082U (zh) * 2018-11-29 2019-07-26 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
CN211144798U (zh) * 2019-10-24 2020-07-31 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101158351A (zh) * 2007-11-16 2008-04-09 美的集团有限公司 涡旋式压缩机及其控制方法
CN101303018A (zh) * 2008-06-06 2008-11-12 西安交通大学 涡旋压缩机
JP2017002804A (ja) * 2015-06-10 2017-01-05 富士電機株式会社 スクロール圧縮機
CN209053784U (zh) * 2018-11-06 2019-07-02 苏州英华特涡旋技术有限公司 一种涡旋压缩机的防抽真空装置
CN209164082U (zh) * 2018-11-29 2019-07-26 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
CN211144798U (zh) * 2019-10-24 2020-07-31 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

Also Published As

Publication number Publication date
CN211144798U (zh) 2020-07-31

Similar Documents

Publication Publication Date Title
WO2021077935A1 (zh) 涡旋压缩机
JP6371087B2 (ja) 分離された背圧室を有するスクロール圧縮機
JP5812693B2 (ja) スクロール式流体機械
CN107002676A (zh) 电动涡旋压缩机
JP2013144940A (ja) スクロール圧縮機
JP6066801B2 (ja) 密閉型回転圧縮機
CN110319003B (zh) 动涡盘驱动组件和涡旋式压缩机
JPH07253094A (ja) スクロール圧縮機の軸方向漏泄防止装置
CN208900360U (zh) 涡旋压缩机
EP1850006A2 (en) Scroll compressor
US20100021328A1 (en) Scroll compressor
CN111237188A (zh) 涡旋压缩机及用于涡旋压缩机的静涡旋部件的定位方法
JP6757898B2 (ja) スクロール圧縮機
JP2005351117A (ja) ベーンポンプ
KR20020084968A (ko) 스크롤 압축기의 자전 방지 장치
CN202187915U (zh) 涡旋压缩机
JP5155942B2 (ja) スクロール型流体機械
WO2024094209A1 (zh) 涡旋压缩机
JPH021995B2 (zh)
KR20200037964A (ko) 유체압축기
WO2020108232A1 (zh) 涡旋压缩机及用于涡旋压缩机的静涡旋部件的定位方法
JP3274814B2 (ja) スクロール流体機械
JPH0330681B2 (zh)
CN110206728B (zh) 一种涡旋压缩机和空调器
CN110017276A (zh) 涡旋压缩机

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: 20879480

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: 20879480

Country of ref document: EP

Kind code of ref document: A1