WO2020238110A1 - 涡旋压缩机 - Google Patents

涡旋压缩机 Download PDF

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Publication number
WO2020238110A1
WO2020238110A1 PCT/CN2019/121967 CN2019121967W WO2020238110A1 WO 2020238110 A1 WO2020238110 A1 WO 2020238110A1 CN 2019121967 W CN2019121967 W CN 2019121967W WO 2020238110 A1 WO2020238110 A1 WO 2020238110A1
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WO
WIPO (PCT)
Prior art keywords
scroll
axial
fixed scroll
flange
end plate
Prior art date
Application number
PCT/CN2019/121967
Other languages
English (en)
French (fr)
Inventor
韩艳春
梁计
张跃
王小燕
刘利涛
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 CN201910465901.0A external-priority patent/CN112012925B/zh
Priority claimed from CN201920805084.4U external-priority patent/CN210033824U/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
Priority to US17/614,472 priority Critical patent/US11859613B2/en
Publication of WO2020238110A1 publication Critical patent/WO2020238110A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—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 both members having co-operating elements in spiral form
    • F04C18/0215—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 both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • F04C2240/00—Components
    • F04C2240/10—Stators
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/805—Fastening means, e.g. bolts

Definitions

  • the present invention relates to a scroll compressor, and more specifically, to a scroll compressor capable of preventing the failure of an axial flexible mounting mechanism.
  • Scroll compressors can be used in, for example, refrigeration systems, air conditioning systems, and heat pump systems.
  • the scroll compressor includes a compression mechanism for compressing a working fluid (eg, refrigerant), a main bearing housing for supporting the compression mechanism, a rotating shaft for driving the compression mechanism, and a motor for driving the rotating shaft to rotate.
  • the compression mechanism includes a fixed scroll and a movable scroll that moves in translation relative to the fixed scroll. Both the fixed scroll and the movable scroll include an end plate and a spiral blade extending from one side of the end plate.
  • the fixed scroll is mounted to the main bearing seat through an axial flexible mounting mechanism, so that the fixed scroll can move a certain distance axially relative to the movable scroll.
  • the axial flexible installation mechanism usually includes a bolt and a sleeve located outside the bolt. Bolts are inserted into the mounting holes of the fixed scroll to thread the fixed scroll to the main bearing housing. The sleeve is also inserted into the mounting hole of the fixed scroll and is arranged between the bolt head and the main bearing seat, so that there is a certain gap between the bolt head and the fixed scroll for the axial movement of the fixed scroll.
  • the inventor of the present application found that the bolts of the axial flexible installation mechanism are easy to loose or break. For this reason, the reasons for the fatigue damage of the bolts are deeply studied, and a solution that can improve the fatigue strength of the bolts is proposed.
  • the purpose of the present disclosure is to provide a scroll compressor that can prevent or reduce damage to the axial flexible mounting mechanism.
  • a scroll compressor includes a fixed scroll, a movable scroll, a main bearing seat and an axial flexible mounting mechanism.
  • the fixed scroll has a fixed scroll end plate and a fixed scroll blade extending from one side of the fixed scroll end plate.
  • the movable scroll has a movable scroll end plate and movable scroll blades extending from one side of the movable scroll end plate, and the movable scroll is configured to orbit relative to the fixed scroll so that the A series of compression chambers for compressing the working fluid are formed between the fixed scroll blades and the movable scroll blades.
  • the main bearing housing is fixedly mounted to the casing of the scroll compressor, and has a supporting surface for supporting the movable scroll end plate in a sliding manner.
  • the fixed scroll is fixedly connected to the connecting portion of the main bearing housing via the axial flexible mounting mechanism so that the fixed scroll can move a predetermined distance in the axial direction.
  • the fixed scroll further has a flange extending radially outward from its peripheral wall portion, the flange having a first surface facing the fixed scroll end plate and a second surface facing the movable scroll end plate And a mounting hole extending from the first surface to the second surface for receiving the axial flexible mounting mechanism, the flange having an axial direction between the first surface and the second surface
  • the geometric center position, the flange is positioned such that the axial geometric center position is located on the side of the peripheral wall portion that is close to the movable scroll end plate with respect to the axial middle position thereof.
  • the scroll compression mechanism causes the axial position of the equivalent point of action of the force applied to the axial flexible mounting mechanism to shift toward the main bearing seat relative to the axial geometric center position during normal operation.
  • the scroll compressor of the present disclosure by shifting the axial position of the equivalent point of action of the force applied to the axially flexible mounting mechanism toward the main bearing seat relative to the axial geometric center position, it is possible to reduce The small distance h, that is, reduces the arm distance D from the axial position of the equivalent point of action to the breaking position P, and therefore can significantly alleviate or prevent the bolt from breaking.
  • the outer contour of the axially flexible mounting mechanism and/or the inner contour of the mounting hole of the flange has a protruding section so that the axial position of the equivalent point of action is relative to the shaft The geometric center position is offset toward the main bearing seat.
  • the protruding section is in the form of a curved surface or in the form of a shoulder forming a step.
  • the flange includes an extension that extends from the second surface along the axial direction toward the main bearing housing over the top surface of the fixed scroll blade.
  • the connecting portion of the main bearing seat that engages with the axial flexible mounting mechanism extends across the support surface toward the flange in the axial direction.
  • the axial flexible mounting mechanism includes a bolt and a sleeve located outside the bolt; or the axial flexible mounting mechanism includes a shoulder bolt.
  • a scroll compressor is also provided.
  • the scroll compressor includes a fixed scroll, a movable scroll, a main bearing seat and an axial flexible mounting mechanism.
  • the fixed scroll has a fixed scroll end plate and a fixed scroll blade extending from one side of the fixed scroll end plate.
  • the movable scroll has a movable scroll end plate and movable scroll blades extending from one side of the movable scroll end plate, and the movable scroll is configured to orbit relative to the fixed scroll so that the A series of compression chambers for compressing the working fluid are formed between the fixed scroll blades and the movable scroll blades.
  • the main bearing housing has a supporting surface for supporting the movable scroll end plate in a sliding manner.
  • the fixed scroll is fixedly connected to the connecting portion of the main bearing housing via the axial flexible mounting mechanism so that the fixed scroll can move a predetermined distance in the axial direction.
  • the fixed scroll further has a flange extending radially outward from its peripheral wall portion, the flange having a first surface facing the fixed scroll end plate and a second surface facing the movable scroll end plate And a mounting hole extending from the first surface to the second surface for receiving the axial flexible mounting mechanism.
  • the height of the flange between the first surface and the second surface is H1, and between the axial position of the equivalent point of action of the force borne by the axial flexible mounting mechanism and the second surface Is h1, the distance between the first surface and the end surface of the connecting portion is H2, the distance between the second surface and the end surface is h2, and the axial position of the equivalent point of action is equal to
  • the flange and/or the connecting portion extend toward each other in the axial direction, so that the second surface of the flange passes over the top surface of the fixed scroll blade and/or the connecting portion The end surface crosses the support surface.
  • the distance h can be reduced, that is, the arm distance from the axial position of the equivalent point of action to the breaking position P can be reduced D, and therefore can significantly alleviate or prevent bolt breakage.
  • the axial flexible mounting mechanism includes a bolt and a sleeve located outside the bolt; or the axial flexible mounting mechanism includes a shoulder bolt.
  • the scroll compression mechanism causes the equivalent point of action axial position to face the axial geometric center position between the first surface and the second surface during normal operation.
  • the main bearing seat is offset.
  • the outer contour of the axially flexible mounting mechanism or the inner contour of the mounting hole of the flange has a protruding section such that the equivalent point of action axial position is relative to the axial geometry The center position is offset toward the main bearing seat.
  • the protruding section is in the form of a curved surface or in the form of a shoulder forming a step.
  • Fig. 1 is a perspective schematic view of a scroll compressor according to an embodiment of the present disclosure
  • Figure 2 is a schematic partial cross-sectional view of the scroll compressor of Figure 1;
  • Fig. 3 is a partial enlarged schematic diagram of the scroll compressor of Fig. 2;
  • FIG. 4 is a schematic partial cross-sectional view of a scroll compressor according to another embodiment of the present disclosure.
  • Fig. 5 is a partial enlarged schematic view of the fixed scroll of the scroll compressor of Fig. 4;
  • Fig. 6 is a schematic partial cross-sectional view of a scroll compressor according to another embodiment of the present disclosure.
  • Fig. 7 is a partial enlarged schematic view of the fixed scroll of the scroll compressor of Fig. 6;
  • Fig. 8 is a schematic partial cross-sectional view of a scroll compressor according to another embodiment of the present disclosure.
  • Fig. 9 is a partial enlarged schematic view of the main bearing seat of the scroll compressor of Fig. 8;
  • Figure 10 is a schematic diagram of the parameter size associated with the fixed scroll and the main bearing seat of the axial flexible mounting mechanism of the scroll compressor;
  • FIG. 11a to 11d are schematic diagrams of parameter sizes according to various embodiments of the present disclosure.
  • Fig. 12 is an effect graph of the scroll compressor according to the present disclosure.
  • Figure 13 is a schematic diagram illustrating the location of a bolt failure.
  • the compressor 100 includes a housing 11, a compression mechanism CM, a motor 16, a rotating shaft (also called a drive shaft or a crankshaft) 14, and a main bearing housing 15.
  • the housing 11 may include a cylindrical body 11a, a top cover 11b at the top end of the cylindrical body 11a, and a bottom cover 11c at the bottom end of the cylindrical body 11a.
  • the housing 11 forms a closed space in which the compression mechanism CM, the rotating shaft 14 of the motor 16 and the main bearing housing 15 are accommodated in the closed space.
  • a partition 11d may also be provided between the top cover 11b and the cylindrical body 11a. The partition 11d divides the enclosed space of the housing 11 into a high pressure side and a low pressure side. The high pressure side is defined by the partition 11d and the top cover 11b, and the low pressure side is defined by the partition 11d, the cylindrical body 11a and the bottom cover. Qualified by 11c.
  • the cylindrical body 11a is provided with an inlet (not shown) for introducing a working fluid with suction pressure into the housing 11.
  • the top cover 11b is provided with a discharge port 11e for discharging the working fluid with discharge pressure compressed by the compression mechanism CM to the housing 11.
  • the compression mechanism CM includes a fixed scroll 12 and a movable scroll 13 fixed to a housing 11 (specifically, a cylindrical body 11a).
  • the motor 16 is configured to rotate the rotating shaft 14, and then, the rotating shaft 14 drives the movable scroll 13 to orbit relative to the fixed scroll 12 (ie, the central axis of the movable scroll moves around the central axis of the fixed scroll, but the movable scroll The spin does not rotate around its central axis) to compress the working fluid.
  • the above-mentioned translational rotation is realized by the Oldham slip ring 17 (see FIG. 2).
  • the fixed scroll 12 may be fixed relative to the housing 11 in any suitable manner, as shown in the figure, fixedly mounted to the main bearing housing 15 by bolts, which will be described in detail later.
  • the fixed scroll 12 may include a fixed scroll end plate 122, a fixed scroll blade 124 extending from one side of the fixed scroll end plate 122, and an exhaust port 121 located approximately at the central portion of the fixed scroll end plate 122.
  • the radially outermost portion of the fixed scroll blade 124 is referred to as the peripheral wall portion 126 herein.
  • the fixed scroll 12 also has a flange 128 extending radially outward from the outer peripheral surface of the peripheral wall portion 126.
  • a mounting hole 127 is provided in the flange 128 for receiving an axial flexible mounting mechanism so as to be connected to the main bearing housing 15.
  • the movable scroll 13 may include a movable scroll end plate 132, a movable scroll blade 134 formed on one side of the movable scroll end plate 132, and a hub 131 formed on the other side of the movable scroll end plate 132.
  • the fixed scroll blades 124 and the movable scroll blades 134 can be engaged with each other, so that a series of volumes are formed between the fixed scroll blades 124 and the movable scroll blades 134 when the scroll compressor is running.
  • the moving compression chamber is gradually reduced to achieve compression of the working fluid.
  • the hub 131 is engaged with the eccentric crank pin of the rotating shaft 14 and is driven by the eccentric crank.
  • the main bearing housing 15 is suitable for supporting the movable scroll end plate 132 of the movable scroll 13.
  • the orbiting scroll end plate 132 orbits on the supporting surface 155 of the main bearing housing 15 (see FIG. 2).
  • the main bearing housing 15 may be fixed with respect to the casing 11 of the scroll compressor 100 by any suitable means.
  • a radial seal is also required between the side surface of the spiral blade 124 of the fixed scroll 12 and the side surface of the spiral blade 134 of the movable scroll 13.
  • Such a radial seal between the two is usually achieved by the centrifugal force of the movable scroll 13 during operation and the driving force provided by the rotating shaft 14.
  • the top end of the spiral blade 124 of the fixed scroll 12 and the end plate 132 of the movable scroll 13 and the top end of the spiral blade 134 of the movable scroll 13 and the fixed scroll 12 Axial sealing is required between the end plates 122.
  • the pressure in the compression chamber of the scroll compressor is too high, the fluid in the compression chamber will pass through the gap between the tip of the spiral blade 124 of the fixed scroll 12 and the end plate 132 of the movable scroll 13 and the movable scroll 13
  • the gap between the tip of the spiral blade 134 and the end plate 122 of the fixed scroll 12 leaks to the low pressure side to achieve unloading, thereby providing the scroll compressor 100 with axial flexibility.
  • the fixed scroll 12 is mounted to the main bearing housing 15 through the axial flexible mounting mechanism 18.
  • the axial flexible mounting mechanism 18 includes a bolt 181 and a sleeve 182 located radially outside of the bolt 181.
  • the bolt 181 has a rod portion 1813, a head 1811 located at one end of the rod portion 1813, and a threaded portion 1817 located at the other end of the rod portion 1813.
  • the head 1811 has an abutting surface 1812 for abutting the upper end surface 1821 (see FIG. 3) of the sleeve 182 and the upper surface (first surface) 1281 of the flange 128.
  • the threaded portion 1817 is configured to be able to be screwed into the threaded hole 151 of the main bearing housing 15.
  • the sleeve 182 is also received in the mounting hole 127 of the flange 128 of the fixed scroll 12 and is located between the head 1811 and the upper surface 153 of the main bearing housing 15, thereby defining the position of the head 1811 such that the fixed scroll 12 is It can move a predetermined distance in the axial direction.
  • Figure 13 to analyze the reasons why the bolts are easy to loose or break.
  • the force of the bolt is very complicated, and only the explanation is simplified here to understand the cause of the fracture.
  • the position P indicated by the dashed line is a position where the bolt is likely to break and fail, and is located at the upper threaded joint between the bolt 3 and the main bearing housing 2. According to the distance from the flange 128, the "upper threaded joint" is referred to herein as the proximal joint.
  • the movable scroll (not shown in FIG.
  • the blade side contact force (force) is generated due to the centripetal acceleration, and the blade side contact force passes through the sleeve 4 and transfer to bolt 3.
  • the equivalent point of action of the force F applied to the bolt 3 by the fixed scroll 1 is at a position corresponding to the axial geometric center point of the flange of the fixed scroll 1.
  • the distance between the position P and the force F is D, so that the moment M (the product of the force F and the distance D) is generated with the position P as a fulcrum.
  • the moment M makes the bolt easily break at the position P.
  • the present disclosure aims to slow down or prevent bolt breakage by reducing the distance D.
  • the movable scroll exerts force on the sleeve through the flange (lug) of the fixed scroll.
  • the flange of the fixed scroll and the sleeve are in a face-to-face contact fit, so the force applied to the sleeve can be regarded as a force distributed over a certain contact area.
  • the position of the concentrated force F is the equivalent point axial position of the force F described herein.
  • the flange 182 of the fixed scroll is located on the peripheral wall portion 126 near the lower half of the main bearing housing 15 and preferably extends radially outward from the end of the peripheral wall portion 126 (convex
  • the lower surface 1283 of the rim 182 is substantially flush with the top surface of the blade 124).
  • FIGS. 1 to 3 show an example of reducing the distance h by improving the outer contour of the sleeve 182.
  • the outer contour (outer peripheral surface) of the sleeve 182 is not a cylindrical shape with a constant diameter, but has a convex section 1828.
  • the dashed line C1 in FIG. 2 represents the axial geometric center position of the flange 128, and the dashed line C2 corresponds to the largest diameter portion 1829 of the protruding section 1828 and therefore represents the position in contact with the mounting hole 127 of the flange 182 (ie, the force F The axial position of the equivalent point of action).
  • the protruding section 1828 has a reduced diameter from the maximum diameter portion 1829 toward the upper surface (first surface) 1281 and the lower surface (second surface) 1283 of the flange 128.
  • the sleeve 182 further has a straight section 1827 with a constant diameter on the side adjacent to the main bearing housing 15. In FIG. 2, the distance from the position P to the equivalent point of action axial position C2 is obviously smaller than the distance from the position P to the axial geometric center position C1.
  • the protruding section 1828 may have a reduced diameter from the maximum diameter portion 1829 only toward the first surface 1281 of the flange 128, and have a constant diameter from the maximum diameter portion 1829 to the end adjacent to the main bearing housing 15.
  • the axial position of the equivalent point of action can be further offset downward, that is, the distance from the position P to the equivalent point of force can be further reduced.
  • the protruding section 1828 is in the form of a curved surface.
  • the protruding section 1828 may also be in the form of a shoulder forming a step.
  • the sleeve 182 and the bolt 181 are separate parts, however, it should be understood that the sleeve 182 and the bolt 181 may be a single piece, that is, a shoulder bolt.
  • the outer contour of the axial flexible mounting mechanism 18 has a protruding section and the equivalent point of action axial position C2 is lower than the axial geometric center position C1, which can alleviate or prevent the bolt 181 from breaking.
  • the sleeve 282 may have a cylindrical shape with a constant diameter. Similar to the example of FIGS. 1 to 3, the dashed line C2 corresponds to the largest diameter portion 2279 of the protruding section 2272 and therefore indicates the position of contact with the sleeve 282 (ie, the equivalent point of action axial position of the force F).
  • the protruding section 2272 has a reduced diameter from the maximum diameter portion 2279 toward the upper surface (first surface) 2281 and the lower surface (second surface) 2283 of the flange 228.
  • the mounting hole 227 further has a straight section 2271 with a constant diameter on the side adjacent to the upper surface (first surface) 2281.
  • the distance from the position P to the equivalent point of action axial position C2 is obviously smaller than the distance from the position P to the axial geometric center position C1.
  • the protruding section 2272 may have any other suitable form, as long as the equivalent point of action axial position C2 is below the axial geometric center position C1.
  • the flange 328 also has an extension portion 3285 extending downward in the axial direction from the lower surface (second surface) 3283, so that the lower end surface (third surface) 3284 of the extension portion 3285 is on the fixed scroll blade 124 Below the top surface.
  • the mounting hole 327 of the flange 328 may have a constant inner diameter
  • the sleeve 382 may also have a constant outer diameter substantially equal to the inner diameter of the mounting hole 327.
  • the dotted line C1 still represents the axial geometric center position from the upper surface (first surface) 3281 to the lower surface (second surface) 3283
  • the dotted line C2 corresponds to the position from the upper surface (first surface)
  • the axial geometric center position of the surface) 3281 to the lower end surface (third surface) 3284 and therefore represents the axial position of the equivalent point of action of the force F applied to the bolt.
  • the axial position of the equivalent point of action is offset toward the main bearing housing 15, thereby reducing the position P to the axial position of the equivalent point of action.
  • Distance that is, reduce the distance h.
  • the main bearing housing 15 has a connecting portion 452 for threaded engagement with a bolt 481.
  • the connecting portion 452 may extend toward the flange such that the upper end surface 453 of the connecting portion 452 is higher than the supporting surface 455 of the end plate 432 for supporting the movable scroll 13, and more preferably, is close to the lower surface 4283 of the flange 428.
  • the distance between the position P and the upper surface of the main bearing housing that is, the axial height of the counterbore
  • the position P is offset toward the flange 428, thereby reducing the distance h.
  • the inventor also performed finite element analysis on some parameters related to the axial flexible mounting mechanism 18, and optimizing some parameter designs can also alleviate or prevent bolt fracture.
  • FIG. 10 The components in FIG. 10 that are the same as those in FIG. 8 are denoted by the same reference numerals as in FIG. 8.
  • the height of the flange 428 between the first surface 4281 and the second surface 4283 is H1.
  • the distance between the axial position C2 of the equivalent point of action of the force applied by the flange 428 to the axial flexible mounting mechanism and the second surface 4283 is h1.
  • the distance between the first surface 4281 and the end surface 453 of the connecting portion 452 is H2.
  • the distance between the second surface 4283 and the end surface 453 is h2.
  • the inventor found through finite element analysis that the bolt fracture can be significantly relieved or prevented when the following conditions are met: 0 ⁇ h2/H1 ⁇ 0.3; 0 ⁇ h2/H2 ⁇ 0.3; 0 ⁇ h/H1 ⁇ 0.6; or 0 ⁇ h/ H2 ⁇ 0.6.
  • Figure 11a corresponds to the embodiment of Figures 1 to 3
  • Figure 11b corresponds to the embodiment of Figures 4 and 5.
  • FIG. 11c corresponds to the embodiment of FIG. 8 and FIG. 9.
  • Tests show that this parameter can significantly alleviate or prevent bolt fracture.
  • Fig. 11d corresponds to the embodiment of Figs. 6 and 7.
  • Tests show that this parameter can significantly alleviate or prevent bolt fracture.
  • the inventor also tested the torque generated at the position P at different distances h under the same force.
  • the structure of the flange, the main bearing seat and the axial flexible mounting mechanism are the same, and only the value of the distance h is changed.
  • the test results are shown in Table 1 below.

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  • 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（12）、动涡旋（13）、主轴承座（15）和轴向柔性安装机构（18）。定涡旋（12）与动涡旋（13）接合以压缩工作流体，主轴承座（15）具有用于支撑动涡旋（13）的端板（132）的支承面（155）。经由轴向柔性安装机构（18）将定涡旋（12）固定连接到主轴承座（15）的连接部使得定涡旋（12）能够沿轴向方向移动预定距离。定涡旋（12）还具有从周壁部径向向外延伸的凸缘（128），凸缘（128）在第一表面和第二表面之间具有轴向几何中心位置，凸缘（128）定位成使得轴向几何中心位置位于周壁部的相对于其轴向中间位置靠近动涡旋（13）的端板（132）的一侧。该结构可以防止或减少涡旋压缩机的轴向柔性安装机构损坏。

Description

涡旋压缩机
本申请要求于2019年5月30日同日提交中国专利局、发明名称为“涡旋压缩机”且申请号分别为201910465901.0和201920805084.4的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及一种涡旋压缩机，更具体地，涉及一种能够防止轴向柔性安装机构失效的涡旋压缩机。
背景技术
本部分的内容仅提供了与本发明相关的背景信息，其可能并不构成现有技术。
涡旋压缩机可以应用于例如制冷系统、空调系统和热泵系统中。涡旋压缩机包括用于压缩工作流体(例如制冷剂)的压缩机构、用于支承压缩机构的主轴承座、用于驱动压缩机构的旋转轴以及用于驱动旋转轴旋转的马达。压缩机构包括定涡旋和相对于定涡旋平动绕动的动涡旋。定涡旋和动涡旋均包括端板和从端板的一侧延伸的螺旋叶片。当动涡旋相对于定涡旋绕动时，定涡旋和动涡旋的螺旋叶片之间形成体积从径向外侧向径向内侧逐渐减小的一系列移动的压缩腔，由此压缩工作流体。
在涡旋压缩机正常运行时，定涡旋和动涡旋中的一者的螺旋叶片的稍端与另一者的端板之间需要达到良好密封。另一方面，例如，在涡旋压缩机的压缩腔内的压力过高时，螺旋叶片可以与端板分离以卸载高压流体，从而避免压缩机构受到损害。
为此，通过轴向柔性安装机构将定涡旋安装至主轴承座，使得定涡旋可以相对于动涡旋轴向移动一定距离。轴向柔性安装机构通常包括螺栓和位于螺栓外侧的套筒。螺栓插入定涡旋的安装孔中以将定涡旋螺纹连接至主轴承座。套筒也插入定涡旋的安装孔中并且设置在螺栓头部与主轴承座之间，使得螺栓头部与定涡旋之间存在一定间隙以供定涡旋的 轴向移动。
发明内容
本申请的发明人发现轴向柔性安装机构的螺栓容易松脱或断裂，为此深入研究螺栓疲劳损坏的原因，并提出了能够提高螺栓的抗疲劳强度的解决方案。
本公开的目的是提供一种能够防止或减少轴向柔性安装机构损坏的涡旋压缩机。
根据本公开的一个方面，提供一种涡旋压缩机。该涡旋压缩机包括定涡旋、动涡旋、主轴承座和轴向柔性安装机构。所述定涡旋具有定涡旋端板和从所述定涡旋端板的一侧延伸的定涡旋叶片。所述动涡旋具有动涡旋端板和从所述动涡旋端板的一侧延伸的动涡旋叶片，所述动涡旋构造成能够相对于所述定涡旋绕动，使得所述定涡旋叶片与所述动涡旋叶片之间形成用于压缩工作流体的一系列压缩腔。所述主轴承座固定地安装至所述涡旋压缩机的壳体，并且具有用于以滑动的方式支承所述动涡旋端板的支承表面。经由所述轴向柔性安装机构将所述定涡旋固定地连接至所述主轴承座的连接部使得所述定涡旋能够沿轴向方向移动预定距离。所述定涡旋还具有从其周壁部径向向外延伸的凸缘，所述凸缘具有面向所述定涡旋端板的第一表面、面向所述动涡旋端板的第二表面以及从所述第一表面延伸至所述第二表面的用于接收所述轴向柔性安装机构的安装孔，所述凸缘在所述第一表面和所述第二表面之间具有轴向几何中心位置，所述凸缘定位成使得所述轴向几何中心位置位于所述周壁部的相对于其轴向中间位置靠近所述动涡旋端板的一侧。所述凸缘在所述第一表面和所述第二表面之间的高度为H1，所述轴向柔性安装机构所承受的力的等效作用点轴向位置与所述第二表面之间的距离为h1，所述第一表面与所述连接部的端面之间的距离为H2，所述第二表面与所述端面之间的距离为h2，所述等效作用点轴向位置与所述端面之间的距离为h，h＝h1+h2。所述涡旋压缩机构造成在正常运行时使得施加至所述轴向柔性安装机构的力的等效作用点轴向位置相对于所述轴向几何中心位置朝向所述主轴承座偏移。
根据本公开的涡旋压缩机，通过使施加至所述轴向柔性安装机构的力 的等效作用点轴向位置相对于所述轴向几何中心位置朝向所述主轴承座偏移，可以减小距离h，即，减小从等效作用点轴向位置到达断裂位置P的力臂距离D，并因此可以显著缓解或防止螺栓断裂。
在一些示例中，所述轴向柔性安装机构的外部轮廓和/或所述凸缘的所述安装孔的内部轮廓具有凸出部段使得所述等效作用点轴向位置相对于所述轴向几何中心位置朝向所述主轴承座偏移。
在一些示例中，所述凸出部段为曲面的形式或者为形成台阶的肩部的形式。
在一些示例中，所述凸缘包括从所述第二表面沿所述轴向方向朝向所述主轴承座延伸越过所述定涡旋叶片的顶面的延伸部。
在一些示例中，所述主轴承座的与所述轴向柔性安装机构接合的连接部沿所述轴向方向朝向所述凸缘延伸越过所述支承表面。
在一些示例中，所述轴向柔性安装机构包括螺栓和位于所述螺栓外侧的套筒；或者所述轴向柔性安装机构包括带肩螺栓。
在一些示例中，0<h2/H1<0.3；0<h2/H2<0.3；0<h/H1<0.6或者0<h/H2<0.6。
根据本公开，还提供一种涡旋压缩机。该涡旋压缩机包括定涡旋、动涡旋、主轴承座和轴向柔性安装机构。所述定涡旋具有定涡旋端板和从所述定涡旋端板的一侧延伸的定涡旋叶片。所述动涡旋具有动涡旋端板和从所述动涡旋端板的一侧延伸的动涡旋叶片，所述动涡旋构造成能够相对于所述定涡旋绕动，使得所述定涡旋叶片与所述动涡旋叶片之间形成用于压缩工作流体的一系列压缩腔。所述主轴承座具有用于以滑动的方式支承所述动涡旋端板的支承表面。经由所述轴向柔性安装机构将所述定涡旋固定地连接至所述主轴承座的连接部使得所述定涡旋能够沿轴向方向移动预定距离。所述定涡旋还具有从其周壁部径向向外延伸的凸缘，所述凸缘具有面向所述定涡旋端板的第一表面、面向所述动涡旋端板的第二表面以及从所述第一表面延伸至所述第二表面的用于接收所述轴向柔性安装机构的安装孔。所述凸缘在所述第一表面和所述第二表面之间的高度为H1，所述轴 向柔性安装机构所承受的力的等效作用点轴向位置与所述第二表面之间的距离为h1，所述第一表面与所述连接部的端面之间的距离为H2，所述第二表面与所述端面之间的距离为h2，所述等效作用点轴向位置与所述端面之间的距离为h，h＝h1+h2。所述凸缘和/或所述连接部沿所述轴向方向朝向彼此延伸，使得所述凸缘的所述第二表面越过所述定涡旋叶片的顶面和/或所述连接部的所述端面越过所述支承表面。
根据本公开的涡旋压缩机，通过使凸缘和主轴承座的连接部朝向彼此延伸，可以减小距离h，即，减小从等效作用点轴向位置到达断裂位置P的力臂距离D，并因此可以显著缓解或防止螺栓断裂。
在一些示例中，0<h2/H1<0.3；0<h2/H2<0.3；0<h/H1<0.6或者0<h/H2<0.6。
在一些示例中，所述轴向柔性安装机构包括螺栓和位于所述螺栓外侧的套筒；或者所述轴向柔性安装机构包括带肩螺栓。
在一些示例中，所述涡旋压缩机构造成在正常运行时使得所述等效作用点轴向位置相对于所述第一表面与所述第二表面之间的轴向几何中心位置朝向所述主轴承座偏移。
在一些示例中，所述轴向柔性安装机构的外部轮廓或所述凸缘的所述安装孔的内部轮廓具有凸出部段使得所述等效作用点轴向位置相对于所述轴向几何中心位置朝向所述主轴承座偏移。
在一些示例中，所述凸出部段为曲面的形式或者为形成台阶的肩部的形式。
从下文的详细描述中，本发明的其它应用领域将变得更为明显。应该理解的是，这些详细描述和具体示例，虽然示出了本发明的优选实施例，但是它们旨在为了示例性说明的目的，而非试图限制本发明。
附图说明
通过以下参照附图的描述，本发明的一个或多个实施方式的特征和优点将变得更加容易理解，在附图中：
图1为根据本公开实施方式的涡旋压缩机的立体示意图；
图2为图1的涡旋压缩机的局部剖面示意图；
图3为图2的涡旋压缩机的局部放大示意图；
图4为根据本公开另一实施方式的涡旋压缩机的局部剖面示意图；
图5为图4的涡旋压缩机的定涡旋的局部放大示意图；
图6为根据本公开又一实施方式的涡旋压缩机的局部剖面示意图；
图7为图6的涡旋压缩机的定涡旋的局部放大示意图；
图8为根据本公开另一实施方式的涡旋压缩机的局部剖面示意图；
图9为图8的涡旋压缩机的主轴承座的局部放大示意图；
图10为涡旋压缩机的轴向柔性安装机构与定涡旋和主轴承座相关联的参数尺寸示意图；
图11a至图11d为根据本公开的各个实施方式的参数尺寸的示意图；
图12为根据本公开的涡旋压缩机的效果曲线图；以及
图13为说明螺栓断裂失效位置的示意图。
具体实施方式
现在将参照附图更全面地描述示例性实施方式。
提供示例性实施方式以使得本公开将是详尽的并且将向本领域技术人员更全面地传达范围。阐述了许多具体细节比如具体部件、装置和方法的示例，以提供对本公开的各实施方式的透彻理解。对本领域技术人员而言将清楚的是，不需要采用具体细节，示例性实施方式可以以许多不同的形式实施，并且也不应当理解为限制本公开的范围。在一些示例性实施方式中，不对公知的过程、公知的装置结构和公知的技术进行详细的描述。
下面参照图1来描述涡旋压缩机100的总体结构。如图所示，压缩 机100包括壳体11、压缩机构CM、马达16、旋转轴(也可以称为驱动轴或曲轴)14以及主轴承座15。
壳体11可以包括筒形本体11a、位于筒形本体11a的顶端的顶盖11b以及位于筒形本体11a的底端的底盖11c。壳体11形成封闭的空间，其中，压缩机构CM、马达16旋转轴14和主轴承座15容置在该封闭的空间中。在顶盖11b与筒形本体11a之间还可以设置有隔板11d。隔板11d将壳体11的封闭的空间分隔成高压侧和低压侧，其中，高压侧由隔板11d和顶盖11b限定而成，而低压侧由隔板11d、筒形本体11a和底盖11c限定而成。
在筒形本体11a上设置有用于将具有吸气压力的工作流体引入壳体11内的进入口(未示出)。在顶盖11b上设置有用于将经过压缩机构CM压缩的具有排出压力的工作流体排出壳体11的排出口11e。在涡旋压缩机100运行时，低压工作流体经由进入口被引入至压缩机100(在图1的示例中引入至低压侧)中，然后被吸入压缩机构CM中，在经过压缩后被排出至高压侧，最后经由排出口11e被排出涡旋压缩机100。
压缩机构CM包括固定至壳体11(具体为筒形本体11a)的定涡旋12和动涡旋13。马达16构造成使旋转轴14旋转，接着，旋转轴14驱动动涡旋13相对于定涡旋12绕动运动(即，动涡旋的中心轴线绕定涡旋的中心轴线运动，但是动涡旋不会绕其中心轴线旋转)以压缩工作流体。上述平动转动通过十字滑环17(参见图2)来实现。
定涡旋12可以以任何合适的方式相对于壳体11固定，如图示的通过螺栓固定地安装至主轴承座15，后面将详细描述。定涡旋12可以包括定涡旋端板122、从定涡旋端板122的一侧延伸的定涡旋叶片124以及大致位于定涡旋端板122的中央部分的排气口121。为便于描述，本文中将定涡旋叶片124的径向最外侧部分称为周壁部126。如图2所示，定涡旋12还具有从周壁部126的外周面径向向外延伸的凸缘128。凸缘128中设置有安装孔127，用于接收轴向柔性安装机构从而连接至主轴承座15。
动涡旋13可以包括动涡旋端板132、形成在动涡旋端板132一侧的动涡旋叶片134和形成在动涡旋端板132另一侧的毂部131。定涡旋叶片124与动涡旋叶片134能够彼此接合，使得当涡旋压缩机运行时在定 涡旋叶片124和动涡旋叶片134之间形成一系列体积在从径向外侧向径向内侧逐渐减小的移动的压缩腔，从而实现对工作流体的压缩。毂部131与旋转轴14的偏心曲柄销接合并被偏心曲柄驱动。
主轴承座15适于支承动涡旋13的动涡旋端板132。动涡旋端板132在主轴承座15的支承面155(参见图2)上绕动。主轴承座15可以通过任何合适地方式相对于涡旋压缩机100的壳体11固定。
为了实现流体的压缩，定涡旋12和动涡旋部件13之间需要有效密封。
一方面，在涡旋压缩机正常运行时，定涡旋12的螺旋叶片124的侧表面与动涡旋13的螺旋叶片134的侧表面之间也需要径向密封。二者之间的这种径向密封通常借助于动涡旋13在运转过程中的离心力以及旋转轴14提供的驱动力来实现。当不可压缩的异物(诸如固体杂质以及液态制冷剂)进入压缩腔中而卡在螺旋叶片124和134之间时，螺旋叶片124和134能够暂时沿径向彼此分开以允许异物通过，由此防止对螺旋叶片124和134造成损坏，从而为涡旋压缩机100提供了径向柔性。
另一方面，在涡旋压缩机正常运行时，定涡旋12的螺旋叶片124的顶端与动涡旋13的端板132之间以及动涡旋13的螺旋叶片134的顶端与定涡旋12的端板122之间需要轴向密封。当涡旋压缩机的压缩腔中的压力过大时，压缩腔中的流体将通过定涡旋12的螺旋叶片124的顶端与动涡旋13的端板132之间的间隙以及动涡旋13的螺旋叶片134的顶端与定涡旋12的端板122之间的间隙泄漏到低压侧以实现卸载，从而为涡旋压缩机100提供了轴向柔性。
为了提供轴向柔性，通过轴向柔性安装机构18将定涡旋12安装至主轴承座15。参见图2，轴向柔性安装机构18包括螺栓181和位于螺栓181径向外侧的套筒182。螺栓181具有杆部1813、位于杆部1813的一端的头部1811以及位于杆部1813的另一端的螺纹部1817。头部1811具有用于抵接套筒182的上端面1821(参见图3)和凸缘128的上表面(第一表面)1281的抵接表面1812。螺纹部1817构造成能够旋拧至主轴承座15的螺纹孔151中。套筒182也接收在定涡旋12的凸缘128的安装孔127中并且位于头部1811与主轴承座15的上表面153之间，由此限定头部1811的位置使得定涡旋12在轴向上能够移动预定距离。
发明人发现现有的轴向柔性安装机构的螺栓容易松脱或断裂。下面参见图13来分析螺栓容易松脱或断裂的原因。螺栓的受力很复杂，在此仅简化说明以便理解断裂原因。虚线表示的位置P为螺栓容易断裂失效的位置，并且位于螺栓3与主轴承座2之间的上螺纹接合部。根据与凸缘128的距离远近，本文中将该“上螺纹接合部”称为近端接合部。如上所述，在动涡旋(图13中未示出)相对于定涡旋1绕动时，由于向心加速度而产生了叶片侧面接触力(作用力)，该叶片侧面接触力经由套筒4而传递至螺栓3。通常认为定涡旋1施加在螺栓3的作用力F的等效作用点在对应于定涡旋1的凸缘的轴向几何中心点的位置处。位置P与力F的距离为D，这样，以位置P为支点产生了力矩M(力F与距离D的乘积)。该力矩M使得螺栓容易在位置P处断裂。本公开旨在通过减小距离D来减缓或防止螺栓断裂。在本文中为了便于描述，假定在各个实施方式中位置P与主轴承座2的上表面2a的距离(即，沉孔2b的轴向高度)不变。这样，通过减小从主轴承座2的上表面2a至力F的等效作用点的距离h，可以减缓或防止螺栓断裂。
当压缩机正常运行时，动涡旋通过定涡旋的凸缘(凸耳)对套筒施加力。通常，定涡旋的凸缘与套筒是面对面的接触配合，因此可以将施加于套筒上的力认为是一定接触面积上分布的力。当把这些分布的力的作用效果等价于一个集中力(本文中所述的力F)时，这个集中力F的位置，即为本文中所述的力F的等效点轴向位置。
为了减小距离h，使定涡旋的凸缘182位于周壁部126的靠近主轴承座15的下半部以下的位置处，优选地，从周壁部126的端部径向向外地延伸(凸缘182的下表面1283基本与叶片124的顶面齐平)。
图1至图3示出了通过改进套筒182的外部轮廓来减小距离h的一个示例。如图所示，套筒182的外部轮廓(外周表面)并不是直径恒定的筒形形状，而是具有凸出部段1828。图2中的虚线C1表示凸缘128的轴向几何中心位置，虚线C2对应于凸出部段1828的最大直径部1829并因此表示与凸缘182的安装孔127接触的位置(即，力F的等效作用点轴向位置)。凸出部段1828从最大直径部1829朝向凸缘128的上表面(第一表面)1281和下表面(第二表面)1283具有减小的直径。在图示的示例中，套筒182在邻近主轴承座15的一侧还具有直径恒定的直 线部段1827。在图2中，从位置P至等效作用点轴向位置C2的距离显然小于从位置P至轴向几何中心位置C1的距离。
应理解的是，本公开不局限于图示的具体示例。例如，凸出部段1828可以从最大直径部1829仅朝向凸缘128的第一表面1281具有减小的直径，而从最大直径部1829至邻接主轴承座15的端部具有恒定的直径。在这种情况下，等效作用点轴向位置可以进一步向下偏移，即，可以进一步减小从位置P至力的等效作用点的距离。在图示的示例中，凸出部段1828为曲面的形式，然而应理解的是，凸出部段1828也可以为形成台阶的肩部形式等。在示出的示例中，套筒182和螺栓181是分体部件，然而应理解的是，套筒182和螺栓181可以是一体件，即，带肩螺栓。
通过上述内容可知，使轴向柔性安装机构18的外部轮廓具有凸出部段并且使等效作用点轴向位置C2低于轴向几何中心位置C1，可以缓解或防止螺栓181断裂。
图4和图5示出了通过改进凸缘228的安装孔227的内部轮廓(内壁的形状)来减小距离h的一个示例。如图所示，安装孔227的内部轮廓(内壁的形状)并不是直径恒定的筒形形状，而是具有凸出部段2272。因此，套筒282可以为具有恒定直径的筒形形状。与图1至图3的示例类似，虚线C2对应于凸出部段2272的最大直径部2279并因此表示与套筒282接触的位置(即，力F的等效作用点轴向位置)。凸出部段2272从最大直径部2279朝向凸缘228的上表面(第一表面)2281和下表面(第二表面)2283具有减小的直径。在图示的示例中，安装孔227在邻近上表面(第一表面)2281的一侧还具有直径恒定的直线部段2271。在图4中，从位置P至等效作用点轴向位置C2的距离显然小于从位置P至轴向几何中心位置C1的距离。
应理解的是，本公开不局限于图示的具体示例。例如，凸出部段2272可以具有任何其他合适的形式，只要等效作用点轴向位置C2在轴向几何中心位置C1以下即可。
图6和图7示出了通过改进凸缘328的结构来减小距离h的另一个示例。如图所示，凸缘328还具有从下表面(第二表面)3283沿轴向向下延伸的延伸部3285，使得延伸部3285的下端面(第三表面)3284在定涡旋叶片124的顶面的下方。在该示例中，凸缘328的安装孔327可 以具有恒定的内径，并且套筒382也可以具有与安装孔327的内径大致相等的恒定的外径。
在图6和图7的示例中，虚线C1仍然表示从上表面(第一表面)3281至下表面(第二表面)3283的轴向几何中心位置，而虚线C2对应于从上表面(第一表面)3281至下端面(第三表面)3284的轴向几何中心位置并因此表示施加于螺栓上的力F的等效作用点轴向位置。在该示例中，通过朝向主轴承座15延长安装孔327的长度，使得等效作用点轴向位置朝向主轴承座15偏移，由此可以减小位置P至等效作用点轴向位置的距离，即，减小距离h。
图8和图9示出了通过改进主轴承座15的结构来减小距离h的另一个示例。如图所示，主轴承座15具有用于与螺栓481螺纹接合的连接部452。连接部452可以朝向凸缘延伸使得连接部452的上端面453高于用于支承动涡旋13的端板432的支承表面455，更优选地，靠近凸缘428的下表面4283。如上所述，本文中为了便于描述，假定在各个实施方式中位置P与主轴承座的上表面的距离(即，沉孔的轴向高度)不变。因此，在图8和图9的示例中，通过使连接部452朝向凸缘428延伸，使得位置P朝向凸缘428偏移，由此减小了距离h。
发明人还对与轴向柔性安装机构18相关的一些参数进行了有限元分析，通过优化一些参数设计也可以缓解或防止螺栓断裂。下面参见图10来了解与缓解或防止螺栓断裂有关的参数。图10中与图8相同的部件使用与图8中相同的附图标记来表示。
如图10所示，凸缘428在第一表面4281和第二表面4283之间的高度为H1。凸缘428施加于轴向柔性安装机构的力的等效作用点轴向位置C2与第二表面4283之间的距离为h1。第一表面4281与连接部452的端面453之间的距离为H2。第二表面4283与端面453之间的距离为h2。等效作用点轴向位置C2与端面453之间的距离为h，h＝h1+h2。
发明人经过有限元分析发现当满足下述条件时可以显著缓解或防止螺栓断裂：0<h2/H1<0.3；0<h2/H2<0.3；0<h/H1<0.6；或者0<h/H2<0.6。
发明人还针对上述各种实施方式在这些参数范围内进行了测试。图11a对应于图1至图3的实施方式，图11b对应于图4和图5的实施方式。在 图11a和图11b的示例中，h1/H1＝0.25，并且h＝14.5，测试表明该参数能够显著缓解或防止螺栓断裂。
图11c对应于图8和图9的实施方式。在图11c的示例中，h2/H2＝0.06，h/H2＝0.36，并且h＝9.3，测试表明该参数能够显著缓解或防止螺栓断裂。图11d对应于图6和图7的实施方式。在图11d的示例中，h2/H2＝0.10，h/H2＝0.55，并且h＝14.3，测试表明该参数能够显著缓解或防止螺栓断裂。
发明人还对相同作用力下不同的距离h在位置P处产生的力矩进行了测试。在该测试中，凸缘、主轴承座和轴向柔性安装机构的结构相同，仅仅改变距离h的值。测试结果如下面的表1。
表1
作用力F(N) 距离h(mm) 位置P处的力矩(Nmm)
3000 8.2 2803
3000 10.2 3229
3000 12.2 3665
3000 14.2 4105
3000 16.2 4546
3000 18.2 4975
3000 20.2 5418
3000 22.2 5851
3000 24.2 6289
根据表1绘制了曲线图，参见图12。图12更直观地示出距离h越小，位置P处的力矩越小。因此，通过减小距离h，可以显著缓解或防止螺栓断裂。
虽然已经参照示例性实施方式对本发明进行了描述，但是应当理解，本发明并不局限于文中详细描述和示出的具体实施方式，在不偏离权利要求书所限定的范围的情况下，本领域技术人员可以对示例性实施方式做出各种改变。还应理解的是，在技术方案不矛盾的情况下，各个实施方式的特征可以相互结合或者可以省去。

Claims (19)

  1. 一种涡旋压缩机，包括：
    定涡旋，所述定涡旋具有定涡旋端板和从所述定涡旋端板的一侧延伸的定涡旋叶片；
    动涡旋，所述动涡旋具有动涡旋端板和从所述动涡旋端板的一侧延伸的动涡旋叶片，所述动涡旋构造成能够相对于所述定涡旋绕动，使得所述定涡旋叶片与所述动涡旋叶片之间形成用于压缩工作流体的一系列压缩腔；
    主轴承座，所述主轴承座固定地安装至所述涡旋压缩机的壳体，并且具有用于以滑动的方式支承所述动涡旋端板的支承表面；以及
    轴向柔性安装机构，经由所述轴向柔性安装机构将所述定涡旋固定地连接至所述主轴承座的连接部使得所述定涡旋能够沿轴向方向移动预定距离，
    其中，所述定涡旋还具有从其周壁部径向向外延伸的凸缘，所述凸缘具有面向所述定涡旋端板的第一表面、面向所述动涡旋端板的第二表面以及从所述第一表面延伸至所述第二表面的用于接收所述轴向柔性安装机构的安装孔，所述凸缘在所述第一表面和所述第二表面之间具有轴向几何中心位置，所述凸缘定位成使得所述轴向几何中心位置位于所述周壁部的相对于其轴向中间位置靠近所述动涡旋端板的一侧，
    所述凸缘在所述第一表面和所述第二表面之间的高度为H1，所述轴向柔性安装机构所承受的力的等效作用点轴向位置与所述第二表面之间的距离为h1，所述第一表面与所述连接部的端面之间的距离为H2，所述第二表面与所述端面之间的距离为h2，所述等效作用点轴向位置与所述端面之间的距离为h，h＝h1+h2，
    所述涡旋压缩机构造成在正常运行时使得所述等效作用点轴向位置相对于所述轴向几何中心位置朝向所述主轴承座偏移。
  2. 根据权利要求1所述的涡旋压缩机，其中，所述轴向柔性安装机构 的外部轮廓和/或所述凸缘的所述安装孔的内部轮廓具有凸出部段使得所述等效作用点轴向位置相对于所述轴向几何中心位置朝向所述主轴承座偏移。
  3. 根据权利要求2所述的涡旋压缩机，其中，所述凸出部段为曲面的形式或者为形成台阶的肩部的形式。
  4. 根据权利要求1所述的涡旋压缩机，其中，所述凸缘包括从所述第二表面沿所述轴向方向朝向所述主轴承座延伸越过所述定涡旋叶片的顶面的延伸部。
  5. 根据权利要求1所述的涡旋压缩机，其中，所述主轴承座的与所述轴向柔性安装机构接合的连接部沿所述轴向方向朝向所述凸缘延伸越过所述支承表面。
  6. 根据权利要求1至5中的任一项所述的涡旋压缩机，其中，所述轴向柔性安装机构包括螺栓和位于所述螺栓外侧的套筒；或者
    所述轴向柔性安装机构包括带肩螺栓。
  7. 根据权利要求1至5中的任一项所述的涡旋压缩机，其中，0<h2/H1<0.3。
  8. 根据权利要求1至5中的任一项所述的涡旋压缩机，其中，0<h2/H2<0.3。
  9. 根据权利要求1至5中的任一项所述的涡旋压缩机，其中，0<h/H1<0.6。
  10. 根据权利要求1至5中的任一项所述的涡旋压缩机，其中，0<h/H2<0.6。
  11. 一种涡旋压缩机，其中，包括：
    定涡旋，所述定涡旋具有定涡旋端板和从所述定涡旋端板的一侧延伸的定涡旋叶片；
    动涡旋，所述动涡旋具有动涡旋端板和从所述动涡旋端板的一侧延伸的动涡旋叶片，所述动涡旋构造成能够相对于所述定涡旋绕动，使得所述定涡旋叶片与所述动涡旋叶片之间形成用于压缩工作流体的一系列压缩腔；
    主轴承座，所述主轴承座具有用于以滑动的方式支承所述动涡旋端板的支承表面；以及
    轴向柔性安装机构，经由所述轴向柔性安装机构将所述定涡旋固定地连接至所述主轴承座的连接部使得所述定涡旋能够沿轴向方向移动预定距离，
    其中，所述定涡旋还具有从其周壁部径向向外延伸的凸缘，所述凸缘具有面向所述定涡旋端板的第一表面、面向所述动涡旋端板的第二表面以及从所述第一表面延伸至所述第二表面的用于接收所述轴向柔性安装机构的安装孔，
    所述凸缘在所述第一表面和所述第二表面之间的高度为H1，所述轴向柔性安装机构所承受的力的等效作用点轴向位置与所述第二表面之间的距离为h1，所述第一表面与所述连接部的端面之间的距离为H2，所述第二表面与所述端面之间的距离为h2，所述等效作用点轴向位置与所述端面之间的距离为h，h＝h1+h2，
    所述凸缘和/或所述连接部沿所述轴向方向朝向彼此延伸，使得所述凸缘的所述第二表面越过所述定涡旋叶片的顶面和/或所述连接部的所述端面越过所述支承表面。
  12. 根据权利要求11所述的涡旋压缩机，其中，0<h2/H1<0.3。
  13. 根据权利要求11所述的涡旋压缩机，其中，0<h2/H2<0.3。
  14. 根据权利要求11所述的涡旋压缩机，其中，0<h/H1<0.6。
  15. 根据权利要求11所述的涡旋压缩机，其中，0<h/H2<0.6。
  16. 根据权利要求11至15中任一项所述的涡旋压缩机，其中，所述轴向柔性安装机构包括螺栓和位于所述螺栓外侧的套筒；或者
    所述轴向柔性安装机构包括带肩螺栓。
  17. 根据权利要求11至15中任一项所述的涡旋压缩机，其中，所述涡旋压缩机构造成在正常运行时使得所述等效作用点轴向位置相对于所述第一表面与所述第二表面之间的轴向几何中心位置朝向所述主轴承座偏移。
  18. 根据权利要求17所述的涡旋压缩机，其中，所述轴向柔性安装机构的外部轮廓或所述凸缘的所述安装孔的内部轮廓具有凸出部段使得所述等效作用点轴向位置相对于所述轴向几何中心位置朝向所述主轴承座偏移。
  19. 根据权利要求18所述的涡旋压缩机，其中，所述凸出部段为曲面的形式或者为形成台阶的肩部的形式。
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