WO2020228272A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

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Publication number
WO2020228272A1
WO2020228272A1 PCT/CN2019/116600 CN2019116600W WO2020228272A1 WO 2020228272 A1 WO2020228272 A1 WO 2020228272A1 CN 2019116600 W CN2019116600 W CN 2019116600W WO 2020228272 A1 WO2020228272 A1 WO 2020228272A1
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WO
WIPO (PCT)
Prior art keywords
peripheral wall
bearing seat
thrust
scroll compressor
inner peripheral
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Application number
PCT/CN2019/116600
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English (en)
French (fr)
Inventor
郭伟平
黄幼玲
Original Assignee
艾默生环境优化技术(苏州)有限公司
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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 WO2020228272A1 publication Critical patent/WO2020228272A1/zh

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

Definitions

  • the present disclosure relates to a scroll compressor.
  • the scroll compressor generally includes a casing and a compression mechanism composed of a fixed scroll and a movable scroll contained in the casing.
  • the fixed scroll is fixed to the casing of the scroll compressor.
  • the orbiting scroll can orbit relative to the fixed scroll to form a series of compression chambers for compressing the working fluid.
  • the orbiting of the orbiting scroll relative to the fixed scroll causes a change in the volume of the compression chamber, thereby compressing the working fluid in the compression chamber.
  • the compression mechanism is supported by a main bearing seat fixedly mounted to the housing.
  • the movable scroll is supported by the main bearing housing.
  • a split thrust bearing design In prior art scroll compressors, there is known a split thrust bearing design.
  • a thrust piece is provided between the main bearing housing and the movable scroll.
  • the thrust piece is a thrust plate.
  • the thrust piece is supported by the main shaft seat and is in contact with the movable scroll piece.
  • the lack of positioning between the thrust piece and the main bearing seat of the split thrust bearing is likely to cause failures and noise problems such as collision damage to parts.
  • the present disclosure provides a scroll compressor.
  • the scroll compressor includes: a housing; a compression mechanism, the compression mechanism including a fixed scroll and a movable scroll; a bearing seat component, the bearing seat component is fixedly mounted to the scroll compression The housing of the machine; the thrust piece, the thrust piece is supported by the bearing seat component, and the upper surface of the thrust piece supports the lower surface of the back plate of the movable scroll.
  • the scroll compressor has a positioning structure configured to restrict the movement of the thrust member relative to the bearing housing member in the radial direction and/or in the circumferential direction.
  • the bearing seat member and the thrust member each have a substantially annular base, and one of the bearing seat member and the thrust member is provided with the bearing seat member and the bearing seat member and the thrust member in the axial direction from the radially outer side of the base.
  • the other has a radially outer peripheral portion capable of radially abutting against the outer peripheral wall and/or a radially inner peripheral portion capable of radially contacting with the inner peripheral wall, wherein the positioning structure includes: an outer peripheral wall and a radially outer peripheral portion ; And/or the inner peripheral wall and the radial inner peripheral portion.
  • the outer peripheral wall and/or the inner peripheral wall are cylindrical.
  • the positioning structure further includes: a positioning pin and a positioning hole correspondingly provided on both the thrust member and the bearing housing member for receiving the positioning pin; or provided on the thrust member and the bearing housing member An axial key portion on one of them, and an axial recessed portion provided on the other of the thrust member and the bearing seat component to cooperate with the axial key portion.
  • the positioning structure includes: at least two positioning pins and at least two positioning holes provided on each of the thrust member and the bearing seat component for receiving the positioning pins; or provided on the thrust member and At least two axial keys and/or axial recesses on one of the bearing seat parts and the axial keys and/or axial recesses provided on the other of the thrust member and the bearing seat part At least two axial recessed portions and/or axial key portions matched by the recessed portion; or the shape fit of the bearing seat member and the thrust member to each other to restrict the movement of the thrust member relative to the bearing seat member in the radial direction and in the circumferential direction ⁇ radial circumference.
  • the outer peripheral wall includes a first outer peripheral wall and a second outer peripheral wall, the first outer peripheral wall and the second outer peripheral wall are symmetrically arranged with respect to the central axis of the substantially annular base; and/or the inner peripheral wall includes the first The inner peripheral wall and the second inner peripheral wall, the first inner peripheral wall and the second inner peripheral wall are symmetrically arranged with respect to the central axis of the substantially annular base.
  • the scroll compression mechanism is formed as an Oldham slip ring adapted to house the scroll compressor between the bearing housing part and the thrust piece.
  • the outer peripheral wall and/or the inner peripheral wall are provided with openings that provide space for the movement of the Oldham slip ring.
  • the base of the bearing seat component or the base of the thrust member is provided with an Oldham slip ring groove for guiding the Oldham slip ring to move in the first direction.
  • a notch is provided on the radially outer or radially inner peripheral portion of the thrust member, and the notch is configured as a part of the Oldham slip ring that cooperates with the movable scroll and/or the fixed scroll. Exercise provides space.
  • Figure 1 is a front sectional view of a turbo compressor according to the prior art
  • Figure 2 is a partial cross-sectional view of a scroll compressor according to the prior art, showing the movable scroll, Oldham slip ring and bearing seat components assembled together;
  • Figure 3 is a top perspective view of the movable scroll, Oldham slip ring and bearing seat components of the scroll compressor according to the prior art when assembled together;
  • Figure 4 is a bottom perspective view of a movable scroll of a scroll compressor according to the prior art
  • Fig. 5 is a top perspective view of the Oldham slip ring and bearing seat components of the scroll compressor according to the prior art when assembled together;
  • FIG. 6 is a top perspective view of the bearing seat component, thrust member and Oldham slip ring of the scroll compressor according to the first embodiment of the present disclosure in an assembled state;
  • Fig. 7 is an exploded perspective view of the bearing seat member, thrust member and Oldham slip ring of the scroll compressor according to the first embodiment of the present disclosure
  • Fig. 8 is an exploded perspective view of the bearing seat component, thrust piece and Oldham slip ring of the scroll compressor according to the second embodiment of the present disclosure
  • Fig. 9 is a bottom perspective view of the thrust member of the scroll compressor according to the second embodiment of the present disclosure.
  • Fig. 10 is an exploded perspective view of the bearing seat member, thrust member and Oldham slip ring of the scroll compressor according to the third embodiment of the present disclosure
  • Fig. 11 is a bottom perspective view of a thrust member of a scroll compressor according to a third embodiment of the present disclosure.
  • Fig. 12 is an exploded perspective view of a bearing housing component, a thrust piece, and an Oldham slip ring of a scroll compressor according to a fourth embodiment of the present disclosure
  • Fig. 13 is a bottom perspective view of a thrust member of a scroll compressor according to a fourth embodiment of the present disclosure.
  • Fig. 1 shows a scroll compressor 100 according to the prior art.
  • the scroll compressor 100 includes a housing 10, a compression mechanism 20 housed in the housing 10, a driving mechanism 30 for driving the compression mechanism 20 to move, and the like.
  • the compression mechanism 20 includes a fixed scroll 21 and a movable scroll 22.
  • the orbiting scroll 22 can orbit relative to the fixed scroll 21 to form a series of compression chambers for compressing the working fluid.
  • the compression mechanism 20 is supported on the main bearing housing 50.
  • the main bearing housing 50 can be fixed with respect to the housing 10 in any suitable manner.
  • the fixed scroll 21 may be fixed relative to the housing 10 in any suitable manner, for example, fixed relative to the main bearing housing 50 by bolts.
  • the driving mechanism 30 includes, for example, a motor, and the motor includes a stator 31 and a rotor 32.
  • the rotor 32 is provided in the stator 31 and can rotate relative to the stator 31.
  • the drive mechanism 30 drives the compression mechanism 20 via the rotating shaft 33.
  • the rotating shaft 33 is arranged in the rotor 32 and rotates together with the rotor 32.
  • the rotating shaft 33 is supported by the main bearing housing 50 via a main bearing, and an eccentric crank pin 34 is formed.
  • the eccentric crank pin 34 is fitted in the hub 222 of the movable scroll 22 to drive the movable scroll 22 to move.
  • a bearing seat member 41 and an Oldham slip ring 60 are provided between the movable scroll 22 and the main bearing seat 50.
  • the bearing housing part 41 and the main bearing housing 50 are formed separately and fixedly connected together.
  • the bearing housing part 41 is formed integrally with the main bearing housing 50.
  • the bearing seat component 41 provides axial support for the fixed scroll 21 and the movable scroll 22.
  • the bearing housing member 41 has a cylindrical inner peripheral wall 412 and a substantially annular base 413.
  • a center hole 414 having a substantially cylindrical shape is formed in the center of the inner peripheral wall 412. The central hole 414 allows the hub 222 of the movable scroll 22 to pass through, and allows the hub 222 to move in the central hole 414 when the movable scroll 22 moves.
  • An Oldham slip ring 60 is provided between the bearing seat member 41 and the movable scroll 22.
  • the Oldham slip ring 60 is generally a ring frame.
  • a pair of Oldham slip ring first keys 601 extending upward along the longitudinal axis of the scroll compressor are provided on opposite sides of the Oldham slip ring 60.
  • the Oldham Slip Ring first key 601 is mounted to the Oldham Slip Ring groove (not shown) of the turbo compressor, and the Oldham Slip Ring 60 can follow the first direction on the line of the pair of Oldham Slip Ring first keys 601 slide.
  • the other two sides of the Oldham slip ring 60 are provided with a pair of Oldham slip ring second keys 602 extending upward along the longitudinal axis of the scroll compressor.
  • the second key 602 of the Oldham slip ring is mounted to the orbiting scroll chute 224 of the movable scroll 22, so that the orbiting scroll 22 can be moved along the first line of the second key 602 of the pair of Oldham ring. Slide in two directions.
  • the above-mentioned first direction is substantially orthogonal to the second direction.
  • the movable scroll 22 performs a translational movement relative to the fixed scroll 21 through the Oldham slip ring 60.
  • the Oldham slip ring does not have to be provided with a raised key, and a pair of guide surfaces may be provided at positions corresponding to the above-mentioned keys to guide the movement of the Oldham slip ring.
  • the bearing seat member thrust surface 411 of the bearing seat member 41 at the top of the inner peripheral wall 412 supports the movable scroll member thrust surface 221 located on the lower side of the movable scroll member 22, wherein the movable scroll member thrust surface 221 serves as the movable scroll
  • the bottom surface of the back plate 223 of the rotating member 22 During the rotation of the movable scroll 22, end surface friction occurs between the thrust surface 411 of the bearing seat member and the thrust surface 221 of the movable scroll.
  • the area of the thrust surface 411 of the bearing seat member is limited by the range of movement of the Oldham ring 60.
  • the moving distance of the Oldham slip ring 60 increases,
  • the outer diameter of the inner peripheral wall 412 needs to be small enough to avoid interference with the movement of the Oldham slip ring 60 in the first direction. Therefore, the area of the thrust surface 411 of the bearing seat component is reduced to provide space for the movement of the Oldham slip ring 60. But the reduced area increases the possibility of wear.
  • the bearing housing member 42 has a generally annular base 421, an outer peripheral wall 422 extending upward from the outer periphery of the base 421 along the longitudinal axis of the turbo compressor, and an inner peripheral wall 423 extending upward in a generally cylindrical shape at the center of the base 421.
  • An Oldham slip ring groove 425 for guiding the Oldham slip ring to move in the first direction is provided at the opposite side edges of the base 421.
  • the outer circumferential wall 422 includes a first outer circumferential wall and a second outer circumferential wall, and the first outer circumferential wall and the second outer circumferential wall are spaced apart in the circumferential direction to form an opening 424 to provide space for the movement of the Oldham ring 60.
  • the outer peripheral wall 422 includes more than two outer peripheral walls.
  • the first outer peripheral wall and the second outer peripheral wall are symmetrically arranged with respect to the central axis of the substantially annular base.
  • the inner peripheral wall 423 includes a first inner peripheral wall and a second inner peripheral wall, and the first inner peripheral wall and the second outer peripheral wall of the inner peripheral wall 423 are axially spaced to form an opening, thereby Provide space for the movement of the cross slip ring.
  • the first inner peripheral wall and the second inner peripheral wall are arranged symmetrically with respect to the central axis of the substantially annular base.
  • the outer peripheral wall 422 is provided with an opening 427 at a position corresponding to the Oldham slip ring groove 425 of the base 421, and the opening 427 also provides space for the Oldham slip ring to move.
  • the inner peripheral wall 423 has a central hole 429 of the bearing seat member for receiving the hub 222 of the movable scroll 22.
  • the thrust member 43 may also be provided with an outer peripheral wall and/or an inner peripheral wall extending in the axial direction toward the bearing seat member 42.
  • the Oldham slip ring 60 is provided between the bearing seat part 42 and the thrust piece 43.
  • the Oldham slip ring 60 is supported by the base 421 of the bearing housing member 42.
  • the Oldham slip ring 60 is provided with a pair of Oldham slip ring first keys 601 extending downward along the longitudinal axis of the scroll compressor at opposite side edges.
  • the Oldham slip ring first key 601 is accommodated in the Oldham slip ring groove 425 of the base 421, so that the Oldham slip ring 60 can slide along the first direction on the line of the pair of Oldham slip ring first keys 601.
  • the other two sides of the Oldham slip ring 60 are provided with a pair of Oldham slip ring second keys 602 extending upward along the longitudinal axis of the scroll compressor.
  • the second key 602 of the Oldham slip ring is mounted to the orbiting scroll chute 224 of the movable scroll 22, so that the orbiting scroll 22 can be moved along the first line of the second key 602 of the pair of Oldham ring. Slide in two directions. The above-mentioned first direction is substantially orthogonal to the second direction.
  • the Oldham slip ring 60 moves in translation between the bearing seat part 42 and the thrust piece 43.
  • the thrust member 43 is a plate having a substantially circular ring shape.
  • the generally annular plate may also serve as the base of the thrust member 43.
  • the base of the thrust member 43 may also be provided with an Oldham slip ring groove for guiding the Oldham slip ring 60 to move in the first direction.
  • the thrust member 43 is provided with four notches 433 on the radially outer peripheral portion, and the notches 433 are configured to provide space for movement of the part of the Oldham ring 60 that cooperates with the movable scroll 22 and/or the fixed scroll 21.
  • the four notches 433 are arranged at equal intervals in the circumferential direction.
  • the thrust member 43 is provided with other numbers of notches 433 on the radially outer circumference.
  • the thrust member 43 may be provided with a notch on the radially inner circumference, so as to provide space for the movement of the part of the Oldham ring 60 that cooperates with the movable scroll 22 and/or the fixed scroll 21.
  • the bearing seat member support surface 426 located on the top of the inner peripheral wall 423 is engaged with the thrust member support surface 432 of the thrust member 43 to support the thrust member 43.
  • the thrust piece thrust surface 431 of the thrust piece 43 is engaged with the movable scroll thrust surface 221 of the movable scroll 22 to support the movable scroll 22.
  • the thrust piece 43 has a thrust piece central hole 435.
  • the central hole 435 of the thrust member corresponds to the central hole 429 of the bearing seat member, and is used for receiving the hub 222 of the movable scroll 22.
  • the outer diameter of the thrust member 43 is larger than the outer diameter of the inner peripheral wall 423.
  • the radially outer peripheral portion 434 of the thrust member 43 is in radial contact with the radially inner peripheral portion 428 of the outer peripheral wall 422 of the bearing housing member 42 so that the thrust member 43 is positioned in the radial direction.
  • the radial abutment between the radially outer circumferential portion of the inner circumferential wall 423 of the bearing seat member 42 and the radially inner circumferential portion of the thrust piece central hole 435 of the thrust piece 43 may be used for radial positioning.
  • the thrust member 43 is supported by the outer peripheral wall 422 of the bearing housing member 42.
  • the thrust member 43 has an outer peripheral wall extending toward the bearing housing member 42
  • a space between the radially inner peripheral portion of the outer peripheral wall of the thrust member 43 and the radially outer peripheral portion of the bearing housing member 42 may be used. ⁇ radial abutment for radial positioning.
  • the thrust member 43 has an inner peripheral wall extending toward the bearing housing member 42
  • the radial outer peripheral portion of the inner peripheral wall of the thrust member 43 and the diameter of the center hole of the bearing housing member 42 may be used. The radial positioning is performed by abutting between the inner peripheral parts in the radial direction.
  • Those skilled in the art can also envisage using other methods of radial abutment between the outer circumferential wall/inner circumferential wall and the corresponding radial outer circumferential portion/radially inner circumferential portion to radially position the thrust member.
  • the radially inner peripheral portion 428 of the outer peripheral wall 422 is cylindrical, and the radially outer peripheral portion 434 of the thrust member 43 also has a corresponding cylindrical profile. The abutting in the radial direction can only perform radial positioning.
  • the outer peripheral wall 422 at least partially has a non-cylindrical inner surface
  • the radially outer peripheral portion 434 at least partially has a non-cylindrical shape corresponding to the inner surface of the outer peripheral wall 422 (for example, Oval, regular polygon, irregular shape, shape with radial protrusions and radial recesses, etc.) contours, so that both radial positioning and circumferential positioning can be performed.
  • the thrust member 43 and the bearing seat member 42 have other forms of outer peripheral wall and radially outer peripheral portion and/or inner peripheral wall and radially inner peripheral portion as described above, radial positioning and Circumferential positioning.
  • the bearing seat member 42 and the thrust member 43 include a radial circumferential portion that is form-fitted with each other to restrict the movement of the thrust member 43 in the radial direction and in the circumferential direction relative to the bearing seat member 42, wherein the radial circumference
  • the portion includes, for example, the inner surface and the radially outer circumferential portion of the outer circumferential wall of the bearing housing member 42 and/or the thrust member 43 and/or the inner circumferential wall and the radially inner circumferential portion.
  • a positioning pin 45 is provided between the bearing seat part 42 and the thrust piece 43.
  • the positioning pin 45 is matched with the positioning pin hole 44 provided on the bearing seat member supporting surface 426 of the inner peripheral wall 423 and the corresponding positioning pin hole (not shown) provided on the thrust member supporting surface 432 of the thrust member 43 , Thereby positioning the thrust member 43 in the circumferential direction.
  • the positioning pin holes are not necessarily provided on the bearing seat component supporting surface 426 and the thrust component supporting surface 432, but only the positioning pin can be used to locate the bearing seat component and the thrust component.
  • the scroll compressor 100 utilizes the radially inner circumferential portion 428 of the outer circumferential wall 422 of the bearing housing member 42 to cooperate with the radially outer circumferential portion 434 of the thrust member 43 to be positioned in the radial direction.
  • the positioning pin 45 between the seat member 42 and the thrust member 43 is positioned in the circumferential direction, thereby avoiding the movable scroll member 22, the bearing seat member 42, the thrust member 43, and the cross slip ring during the operation of the scroll compressor.
  • the possible collision between 60 and other components avoids the resulting failures and noise problems such as component damage, thereby improving the reliability and service life of the components.
  • the Oldham slip ring 60 translates between the bearing housing member 42 and the thrust piece 43.
  • the translational space of the Oldham slip ring 60 becomes larger, since the notch 433 of the thrust member 43 allows the Oldham slip ring 60 to move a greater distance, the outer diameter of other parts of the thrust member 43 does not have to be affected by the Oldham slip ring 60. limits. In this way, the contact area between the thrust member 43 and the movable scroll member 22 does not need to be reduced, but may increase, thereby reducing the risk of wear.
  • the bearing seat member 42 and the thrust piece 43 can also be positioned in other ways.
  • FIGS. 8 and 9 The bearing seat member, the thrust member, and the Oldham slip ring of the scroll compressor according to the second embodiment of the present disclosure are shown in FIGS. 8 and 9.
  • two positioning pins 45 are provided between the bearing housing member 42 and the thrust piece 43.
  • Two locating pins 45 and two locating pin holes 44 (FIG. 8) provided on the bearing seat member supporting surface 426 of the inner peripheral wall 423 and corresponding locating pin holes provided on the thrust member supporting surface 432 of the thrust member 43 46 (FIG. 9) cooperate to position the thrust member 43 in the radial direction and in the circumferential direction.
  • the bearing seat member 42 and the thrust member 43 may also be positioned in other ways.
  • FIGS. 10 and 11 The bearing housing component, thrust piece and Oldham slip ring according to the third embodiment of the present disclosure are shown in FIGS. 10 and 11.
  • no positioning pin is provided between the bearing housing member 42 and the thrust piece 43.
  • an axial key 47 is provided on the thrust member supporting surface 432 of the thrust member 43, and a corresponding axial recessed portion 48 is provided on the bearing seat member supporting surface 426 of the inner peripheral wall 423. The axial key portion 47 and the axial recessed portion 48 cooperate to position the thrust member 43 in the circumferential direction.
  • FIGS. 12 and 13 The bearing housing component, the thrust piece and the Oldham slip ring according to the fourth embodiment of the present disclosure are shown in FIGS. 12 and 13.
  • the bearing seat member supporting surface 426 of the inner peripheral wall 423 is provided with an axial key portion 47
  • the thrust member supporting surface 432 of the thrust member 43 is provided with a corresponding axial recessed portion 48.
  • the axial key portion 47 and the axial recessed portion 48 cooperate to position the thrust member 43 in the circumferential direction.
  • the axial key portion 47 and the axial recessed portion 48 can also be provided at other positions on the bearing seat member 42 and the thrust member 43, as long as they can Just position the thrust piece 43.
  • interference fit and key fit may be used to position the bearing seat component and the thrust piece.

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

Abstract

一种涡旋压缩机包括：壳体；压缩机构，压缩机构包括定涡旋件和动涡旋件；轴承座部件（42），轴承座部件（42）固定地安装至涡旋压缩机的壳体；止推件（43），止推件（43）由轴承座部件（42）支承，并且止推件（43）的上表面支承动涡旋件的背板的下表面。涡旋压缩机还具有：定位结构，定位结构构造成用于限制止推件（43）相对于轴承座部件（42）在径向上和/或在周向上的移动。

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05月10日提交国家知识产权局的申请号为201920670984.2、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。
涡旋压缩机一般包括壳体和容置在壳体内的由定涡旋件和动涡旋件构成的压缩机构。定涡旋件固定于涡旋压缩机的壳体。动涡旋件能够相对于定涡旋件绕动以形成用于压缩工作流体的一系列压缩腔。动涡旋件相对于定涡旋件的绕动引起压缩腔容积的变化，从而对压缩腔内的工作流体进行压缩。压缩机构由固定地安装至壳体的主轴承座支承。特别是，其中，动涡旋件由主轴承座支承。
在现有技术的涡旋压缩机中，已知存在分体式止推轴承的设计。在该设计中，在主轴承座与动涡旋件之间设置有止推件。特别地，止推件为止推板。止推件由主轴座支承，与动涡旋件相接触。该分体式止推轴承的止推件与主轴承座之间缺乏定位，容易造成零部件碰撞损坏等故障及噪音问题。
因此，需要对止推件进行定位，减少涡旋压缩机内各部件的碰撞，从而提高各部件的可靠性和使用寿命。
发明内容
本公开的提供一种涡旋压缩机，涡旋压缩机包括：壳体；压缩机构，压缩机构包括定涡旋件和动涡旋件；轴承座部件，轴承座部件固定地安装至涡旋压缩机的壳体；止推件，止推件由轴承座部件支承，并且止推件的上表面支承动涡旋件的背板的下表面。涡旋压缩机具有：定位结构，定位结构构造成用于限 制止推件相对于轴承座部件在径向上和/或在周向上的移动。
在一个实施方式中，轴承座部件和止推件均具有大体圆环状的基部，轴承座部件和止推件中的一者设置有从其基部的径向外侧沿轴向朝向轴承座部件和止推件中的另一者延伸的外周壁和/或从其基部的径向内侧沿轴向朝向轴承座部件和止推件中的另一者延伸的内周壁，轴承座部件和止推件中的另一者具有能够与外周壁径向抵接的径向外周部和/或能够与内周壁径向抵接的径向内周部，其中，定位结构包括：外周壁和径向外周部；以及/或者内周壁和径向内周部。
在一个实施方式中，外周壁和/或内周壁呈圆筒状。
在一个实施方式中，定位结构还包括：一个定位销以及相应地设置在止推件和轴承座部件两者上的用于接收定位销的一个定位孔；或者设置在止推件和轴承座部件中的一者上的一个轴向键部以及设置在止推件和轴承座部件中的另一者上的与轴向键部配合的一个轴向凹入部。
在一个实施方式中，定位结构包括：至少两个定位销以及设置在止推件和轴承座部件中每一者上的用于接收定位销的至少两个定位孔；或者设置在止推件和轴承座部件中的一者上的至少两个轴向键部和/或轴向凹入部以及设置在止推件和轴承座部件中的另一者上的与轴向键部和/或轴向凹入部配合的至少两个轴向凹入部和/或轴向键部；或者轴承座部件和止推件的彼此形状配合以限制止推件相对于轴承座部件在径向上以及在周向上的移动的径向周部。
在一个实施方式中，外周壁包括第一外周壁和第二外周壁，第一外周壁与第二外周壁关于大体圆环状的基部的中心轴线对称地布置；并且/或者内周壁包括第一内周壁和第二内周壁，第一内周壁和第二内周壁关于大体圆环状的基部的中心轴线对称地布置。
在一个实施方式中，涡旋压缩机构造成适于在轴承座部件与止推件之间容置涡旋压缩机的十字滑环。
在一个实施方式中，外周壁和/或内周壁设置有为十字滑环的运动提供空间的开口。
在一个实施方式中，轴承座部件的基部或止推件的基部中设置有用于引导十字滑环沿第一方向运动的十字滑环槽。
在一个实施方式中，止推件的径向外周部或径向内周部上设置有凹口，凹 口构造成为十字滑环的与动涡旋件和/或定涡旋件配合的部分的运动提供空间。
附图说明
以下将参照附图仅以示例方式描述本公开的实施方式，在附图中，相同的特征或部件采用相同的附图标记来表示且附图不一定按比例绘制，并且在附图中：
图1是根据现有技术的涡轮压缩机的正视截面图；
图2是根据现有技术的涡旋压缩机的局部截面图，示出了组装在一起的动涡旋件、十字滑环和轴承座部件；
图3是根据现有技术的涡旋压缩机的动涡旋件、十字滑环和轴承座部件在组装在一起时的俯视立体图；
图4是根据现有技术的涡旋压缩机的动涡旋件的仰视立体图；
图5是根据现有技术的涡旋压缩机的十字滑环和轴承座部件在组装在一起时的俯视立体图；
图6是根据本公开的第一实施方式的涡旋压缩机的轴承座部件、止推件与十字滑环在组装状态下的俯视立体图；
图7是根据本公开的第一实施方式的涡旋压缩机的轴承座部件、止推件与十字滑环的分解立体图；
图8是根据本公开的第二实施方式的涡旋压缩机的轴承座部件、止推件与十字滑环的分解立体图；
图9是根据本公开的第二实施方式的涡旋压缩机的止推件的仰视立体图；
图10是根据本公开的第三实施方式的涡旋压缩机的轴承座部件、止推件与十字滑环的分解立体图；
图11是根据本公开的第三实施方式的涡旋压缩机的止推件的仰视立体图；
图12是根据本公开的第四实施方式的涡旋压缩机的轴承座部件、止推件与十字滑环的分解立体图；
图13是根据本公开的第四实施方式的涡旋压缩机的止推件的仰视立体图。
具体实施方式
下文的描述本质上仅是示例性的而并非意图限制本公开、应用及用途。应当理解，在所有这些附图中，相似的附图标记指示相同的或相似的零件及特征。各个附图仅示意性地表示了本公开的实施方式的构思和原理，并不一定示出了本公开各个实施方式的具体尺寸及其比例，在特定的附图或图中的特定部分可能采用夸张的方式来图示本公开各个实施方式的相关细节或结构。
图1示出了根据现有技术的涡旋压缩机100。涡旋压缩机100包括壳体10以及容置在壳体10内的压缩机构20、用于驱动压缩机构20运动的驱动机构30等。压缩机构20包括定涡旋件21和动涡旋件22。动涡旋件22能够相对于定涡旋件21绕动以形成用于压缩工作流体的一系列压缩腔。压缩机构20被支承在主轴承座50上。主轴承座50可以通过任何合适的方式相对于壳体10固定。定涡旋件21可以以任何合适的方式相对于壳体10固定，例如通过螺栓相对于主轴承座50固定。驱动机构30例如包括马达，马达包括定子31和转子32。转子32设置在定子31内，并且能够相对于定子31旋转。驱动机构30经由旋转轴33驱动压缩机构20。旋转轴33设置在转子32内，随转子32一起旋转。旋转轴33经由主轴承由主轴承座50支承，并且形成有偏心曲柄销34。偏心曲柄销34配合在动涡旋件22的毂部222中以驱动动涡旋件22运动。
如图2所示，在现有技术的涡旋压缩机中，在动涡旋件22与主轴承座50之间设置有轴承座部件41和十字滑环60。轴承座部件41与主轴承座50单独地形成并且固定地连接在一起。替代性地，轴承座部件41与主轴承座50一体地形成。轴承座部件41为定涡旋件21和动涡旋件22提供轴向支承。
如图3所示，在组装状态下，动涡旋件22座置在轴承座部件41上。如图4和图5所示，轴承座部件41具有圆筒状的内周壁412和大体圆环状的基部413。在内周壁412的中央形成有大体呈圆筒状的中央孔414。中央孔414可供动涡旋件22的毂部222穿过，并且在动涡旋件22运动时允许毂部222在中央孔414中运动。
在轴承座部件41与动涡旋件22之间设置有十字滑环60。十字滑环60大体呈环状框架。在十字滑环60的相对两侧设有沿涡旋压缩机纵向轴线方向向上延伸的一对十字滑环第一键601。十字滑环第一键601安装至涡轮压缩机的 十字滑环槽(未示出)，而十字滑环60能够沿着在该一对十字滑环第一键601的连线上的第一方向滑动。在十字滑环60的另外两侧设有沿涡旋压缩机纵向轴线方向向上延伸的一对十字滑环第二键602。十字滑环第二键602安装至动涡旋件22的动涡旋件滑槽224，而能够使动涡旋件22沿着在该一对十字滑环第二键602的连线上的第二方向滑动。上述第一方向与第二方向大体正交。由此，通过十字滑环60实现动涡旋件22相对于定涡旋件21进行平动运动。本领域技术人员可以理解，十字滑环不一定设有凸起的键，也可以在与上述键相应的位置处设置有成对的引导面，用于引导十字滑环的运动。
轴承座部件41的位于内周壁412顶部的轴承座部件止推面411支承位于动涡旋件22下侧的动涡旋件止推面221，其中，动涡旋件止推面221作为动涡旋件22的背板223的下表面。在动涡旋件22旋转过程中，轴承座部件止推面411与动涡旋件止推面221之间产生端面摩擦。轴承座部件止推面411的面积受到十字滑环60的运动范围的限制。例如，在涡旋压缩机100的壳体10尺寸不变的情况下，当动涡旋件22相对于定涡旋件21以更大绕动半径运动时，十字滑环60的运动距离增加，内周壁412的外径需要足够小以避免干涉十字滑环60的沿第一方向的运动。因此轴承座部件止推面411的面积减小以便为十字滑环60的运动提供空间。但是减小的面积增大了磨损的可能性。
图6和图7示出根据本公开的第一实施方式的涡旋压缩机的轴承座部件42、止推件43与十字滑环60。轴承座部件42与主轴承座50单独地形成并且固定地连接在一起。替代性地，轴承座部件42与主轴承座50一体地形成。轴承座部件42具有大体圆环状的基部421、从基部421的外周沿涡轮压缩机纵向轴线向上延伸的外周壁422和在基部421中央处大体呈圆筒状向上延伸的内周壁423。在基部421的相对两侧边缘处设置有用于引导十字滑环沿第一方向运动的十字滑环槽425。外周壁422包括第一外周壁和第二外周壁，第一外周壁与第二外周壁在周向上间隔开而形成开口424，以便为十字滑环60的运动提供空间。替代性地，外周壁422包括多于两个的外周壁。优选地，第一外周壁与第二外周壁关于大体圆环状的基部的中心轴线对称地布置。替代性地，本领域普通技术人员可以设想，内周壁423包括第一内周壁和第二内周壁，内周壁423的第一内周壁与第二外周壁在轴向上间隔开而形成开口，从而为十字滑环的运动提供空间。优选地，第一内周壁和第二内周壁关于大体圆环状的基部 的中心轴线对称地布置。外周壁422在与基部421的十字滑环槽425对应的位置处设置有开口427，开口427也为十字滑环的运动提供空间。内周壁423具有轴承座部件中央孔429，用以容置动涡旋件22的毂部222。
附加地或者替代性地，本领域技术人员可以理解，在止推件43上也可以设置沿着轴向方向朝向轴承座部件42延伸的外周壁和/或内周壁。
十字滑环60设置在轴承座部件42和止推件43之间。十字滑环60由轴承座部件42的基部421支承。十字滑环60在相对两侧边缘处设置有沿涡旋压缩机纵向轴线向下延伸的一对十字滑环第一键601。十字滑环第一键601容置在基部421的十字滑环槽425中，使十字滑环60能够沿着在该一对十字滑环第一键601的连线上的第一方向滑动。在十字滑环60的另外两侧设有沿涡旋压缩机纵向轴线方向向上延伸的一对十字滑环第二键602。十字滑环第二键602安装至动涡旋件22的动涡旋件滑槽224，而能够使动涡旋件22沿着在该一对十字滑环第二键602的连线上的第二方向滑动。上述第一方向与第二方向大体正交。十字滑环60在轴承座部件42与止推件43之间平动。
在本实施方式中，止推件43为大体呈圆环状的板。该大体呈圆环状的板也可以作为止推件43的基部。本领域普通技术人员可以设想，在止推件43的基部中也可以设置有用于引导十字滑环60沿第一方向运动的十字滑环槽。止推件43在径向外周部上设置有四个凹口433，凹口433构造成为十字滑环60的与动涡旋件22和/或定涡旋件21配合的部分的运动提供空间。优选地，四个凹口433沿圆周方向等间距地布置。四个凹口433中，位于相对位置的两个凹口433用于容置十字滑环第二键602。替代性地，止推件43在径向外周部上设置有其他数目的凹口433。替代性地，止推件43可以在径向内周部上设置有凹口，从而为十字滑环60的与动涡旋件22和/或定涡旋件21配合的部分的运动提供空间。
位于内周壁423顶部的轴承座部件支承面426与止推件43的止推件支承面432相接合以对止推件43进行支承。止推件43的止推件止推面431与动涡旋件22的动涡旋件止推面221相接合以对动涡旋件22进行支承。止推件43具有止推件中央孔435。止推件中央孔435与轴承座部件中央孔429相对应，用以容置动涡旋件22的毂部222。止推件43的外径大于内周壁423的外径。
止推件43的径向外周部434与轴承座部件42的外周壁422的径向内周部 428径向抵接，从而使止推件43在径向上定位。替代性地，可以利用轴承座部件42的内周壁423的径向外周部与止推件43的止推件中央孔435的径向内周部之间的径向抵接来进行径向定位。此时，止推件43由轴承座部件42的外周壁422支承。替代性地，在止推件43具有朝向轴承座部件42延伸的外周壁的情况下，可以利用止推件43的外周壁的径向内周部与轴承座部件42的径向外周部之间的径向抵接来进行径向定位。替代性地，在止推件43具有朝向轴承座部件42延伸的内周壁的情况下，可以利用止推件43的内周壁的径向外周部与轴承座部件42的轴承座部件中央孔的径向内周部之间的径向抵接来进行径向定位。本领域技术人员还可以设想利用外周壁/内周壁与相应的径向外周部/径向内周部之间的径向抵接的其他方式对止推件进行径向定位。
此外，在图6和图7所示的实施方式中，外周壁422的径向内周部428呈圆筒形，止推件43的径向外周部434也具有相应的圆筒形轮廓，两者在径向上抵接只能进行径向定位。但是本领域技术人员可以设想，使外周壁422至少部分地具有非圆筒形的内表面，而径向外周部434至少部分地具有与外周壁422的该内表面相应的非圆筒形(例如椭圆形、正多边形、不规则形状、带有径向凸部和径向凹部的形状等)轮廓，从而既能进行径向定位，也能进行周向定位。替代性地，在止推件43和轴承座部件42具有如上所述的其他形式的外周壁和径向外周部以及/或者内周壁和径向内周部时，也可以如此进行径向定位以及周向定位。也就是说，轴承座部件42和止推件43包括彼此形状配合以限制止推件43相对于轴承座部件42在径向上以及在周向上的移动的径向周部，其中，该径向周部例如包括轴承座部件42和/或止推件43的外周壁的内表面和径向外周部以及/或者内周壁和径向内周部等。
在轴承座部件42和止推件43之间设置有一个定位销45。定位销45与设置在内周壁423的轴承座部件支承面426上的定位销孔44和设置在止推件43的止推件支承面432上的对应的定位销孔(未示出)相配合，从而使止推件43在周向上定位。本领域技术人员可以理解，定位销孔不一定设置在轴承座部件支承面426和止推件支承面432上，而是只要能利用定位销对轴承座部件和止推件进行定位即可。
根据本实施方式，涡旋压缩机100利用轴承座部件42的外周壁422的径向内周部428与止推件43的径向外周部434相配合而在径向上定位，还利用 设在轴承座部件42与止推件43之间的定位销45在周向上定位，从而避免了在涡旋压缩机工作过程中，动涡旋件22、轴承座部件42、止推件43、十字滑环60等部件之间可能的碰撞，避免了由此带来的零部件损坏等故障及噪音问题，从而提高了部件的可靠性和使用寿命。
另外，根据本实施方式，十字滑环60在轴承座部件42与止推件43之间平动。当十字滑环60的平动空间变大时，由于止推件43的凹口433允许十字滑环60移动更大距离，因此，止推件43的其他部分的外径不必受到十字滑环60的限制。这样，止推件43与动涡旋件22之间的接触面积不必减小，反而可能增加，从而降低了磨损的风险。
轴承座部件42与止推件43之间也可以利用其它方式定位。
图8和图9中示出的根据本公开的第二实施方式的涡旋压缩机的轴承座部件、止推件和十字滑环。在本实施方式中，在轴承座部件42和止推件43之间设置有两个定位销45。两个定位销45与设在内周壁423的轴承座部件支承面426上的两个定位销孔44(图8)和设在止推件43的止推件支承面432的对应的定位销孔46(图9)相配合，从而使止推件43在径向上以及在周向上定位。
除了定位销，轴承座部件42和止推件43之间也可以通过其它方式进行定位。
图10和图11中示出的根据本公开的第三实施方式的轴承座部件、止推件和十字滑环。在本实施方式中，在轴承座部件42和止推件43之间并未设置定位销。替代性地，在止推件43的止推件支承面432上设有轴向键部47，在内周壁423的轴承座部件支承面426上设有对应的轴向凹入部48。轴向键部47和轴向凹入部48相配合，从而使止推件43在周向上定位。
图12和图13中示出的根据本公开的第四实施方式的轴承座部件、止推件和十字滑环。在本实施方式中，在内周壁423的轴承座部件支承面426上设有轴向键部47，在止推件43的止推件支承面432上设有对应的轴向凹入部48。轴向键部47和轴向凹入部48相配合，从而使止推件43在周向上定位。
替代性地，本领域技术人员可以理解，在上述两个实施方式中，轴向键部47和轴向凹入部48也可以设置在轴承座部件42和止推件43上的其他位置，只要能够对止推件43进行定位即可。
替代性地，本领域技术人员可以设想，可以利用过盈配合、键配合对轴承座部件与止推件进行定位。
在此，已详细描述了本公开的示例性实施方式，但是应该理解的是，本公开并不局限于上文详细描述和示出的具体实施方式。在不偏离本公开的主旨和范围的情况下，本领域的技术人员能够对本公开进行各种变型和变体。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 (10)

  1. 一种涡旋压缩机，所述涡旋压缩机包括：
    壳体；
    压缩机构，所述压缩机构包括定涡旋件和动涡旋件；
    轴承座部件，所述轴承座部件固定地安装至所述涡旋压缩机的所述壳体
    止推件，所述止推件由所述轴承座部件支承，并且所述止推件的上表面支承所述动涡旋件的背板的下表面；
    其特征在于，所述涡旋压缩机具有：
    定位结构，所述定位结构构造成用于限制所述止推件相对于所述轴承座部件在径向上和/或在周向上的移动。
  2. 根据权利要求1所述的涡旋压缩机，其中，所述轴承座部件和所述止推件均具有大体圆环状的基部，所述轴承座部件和所述止推件中的一者设置有从其基部的径向外侧沿轴向朝向所述轴承座部件和所述止推件中的另一者延伸的外周壁和/或从其基部的径向内侧沿轴向朝向所述轴承座部件和所述止推件中的另一者延伸的内周壁，
    所述轴承座部件和所述止推件中的另一者具有能够与所述外周壁径向抵接的径向外周部和/或能够与所述内周壁径向抵接的径向内周部，
    其中，所述定位结构包括：
    所述外周壁和所述径向外周部；以及/或者
    所述内周壁和所述径向内周部。
  3. 根据权利要求2所述的涡旋压缩机，其中，所述外周壁和/或所述内周壁呈圆筒状。
  4. 根据权利要求3所述的涡旋压缩机，其中，所述定位结构还包括：
    一个定位销以及相应地设置在所述止推件和所述轴承座部件两者上的用于接收所述定位销的一个定位孔；或者
    设置在所述止推件和所述轴承座部件中的一者上的一个轴向键部以及设 置在所述止推件和所述轴承座部件中的另一者上的与所述轴向键部配合的一个轴向凹入部。
  5. 根据权利要求1所述的涡旋压缩机，其中，所述定位结构包括：
    至少两个定位销以及设置在所述止推件和所述轴承座部件中每一者上的用于接收所述定位销的至少两个定位孔；或者
    设置在所述止推件和所述轴承座部件中的一者上的至少两个轴向键部和/或轴向凹入部以及设置在所述止推件和所述轴承座部件中的另一者上的与所述轴向键部和/或轴向凹入部配合的至少两个轴向凹入部和/或轴向键部；或者
    所述轴承座部件和所述止推件的彼此形状配合以限制所述止推件相对于所述轴承座部件在径向上以及在周向上的移动的径向周部。
  6. 根据权利要求2所述的涡旋压缩机，其中，所述外周壁包括第一外周壁和第二外周壁，所述第一外周壁与所述第二外周壁关于所述大体圆环状的基部的中心轴线对称地布置；并且/或者
    所述内周壁包括第一内周壁和第二内周壁，所述第一内周壁和第二内周壁关于所述大体圆环状的基部的中心轴线对称地布置。
  7. 根据权利要求2所述的涡旋压缩机，其中，所述涡旋压缩机构造成适于在所述轴承座部件与所述止推件之间容置所述涡旋压缩机的十字滑环。
  8. 根据权利要求7所述的涡旋压缩机，其中，所述外周壁和/或所述内周壁设置有为所述十字滑环的运动提供空间的开口。
  9. 根据权利要求7所述的涡旋压缩机，其中，所述轴承座部件的基部或所述止推件的基部中设置有用于引导所述十字滑环沿第一方向运动的十字滑环槽。
  10. 根据权利要求7所述的涡旋压缩机，其中，所述止推件的径向外周部或径向内周部上设置有凹口，所述凹口构造成为所述十字滑环的与所述动涡旋 件和/或所述定涡旋件配合的部分的运动提供空间。
PCT/CN2019/116600 2019-05-10 2019-11-08 涡旋压缩机 WO2020228272A1 (zh)

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